EP0086190A1 - Rotary engine valve with improved seals and lubrication system - Google Patents
Rotary engine valve with improved seals and lubrication systemInfo
- Publication number
- EP0086190A1 EP0086190A1 EP19810902358 EP81902358A EP0086190A1 EP 0086190 A1 EP0086190 A1 EP 0086190A1 EP 19810902358 EP19810902358 EP 19810902358 EP 81902358 A EP81902358 A EP 81902358A EP 0086190 A1 EP0086190 A1 EP 0086190A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- cylinder
- head
- rod
- set forth
- Prior art date
- Legal status (The legal status 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 status listed.)
- Withdrawn
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.
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.Rod type valve (36) for an internal combustion engine of the type having a block (14) in which is arranged a cylinder and a piston (22) reciprocating in the cylinder, where the chamber is covered by a cylinder head ( 18), and an improved valve in the form of a rod (36) journalled in the cylinder head, a part of the rod spanning a part of the cylinder above the piston, and the rod has a diametrical passage (90, 92) having a section which, in the direction of the center line of the rod, is at least as large as the radius of the cylinder and whose circumference is a distance substantially equal to 1/16 of the circumference of the rod, and where means seals (501) are provided between the rod and the engine, and a crankshaft (30) connected to the piston is connected to the rod (36) to rotate it simultaneously with the crankshaft by a force transmission means (38) such than a strap or whatever.
Description
Description
ROTARY ENGINE VALVE WITH IMPROVED SEALS AND LUBRICATION SYSTEM
Technical Field
This invention relates to an improved valve mean for an internal combustion engine.
Background of the Invention:
In the past there have been numerous types of valving arrangements for internal combustion engines. 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. Because of the rotary movement and because of the elimination of valve springs, 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.
Objects of the Invention:
It is an object of this invention to provide a device of the type described hereinafter which is simple and inexpensive to manufacture, highly useful in operation, efficient, and calculated to reduce pollution.
In accordance with these and other objects which will become apparent hereinafter, the instant inven-
O PI
tion will now be described with reference to the accompanying drawings in which:
Description of the Drawings:
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; and
Figure 9 is an end view of the spring shown in Figure 8.
Description of the Preferred Embodiment: '
Referring to Figure 1, there is shown 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. Within the block, 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 gear 38 on the end of a shaft 36 supported in spanning relation of the side of the upper end zone of the cylinders and being supported such as by bearings 42 and 44 captivated between the upper portion 40 of the head 18 and the block. With res-
10 pect to Figure 2, 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. As is clearly shown-in Figure 2 in the preferred 5 embodiment, 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. c On the opposite side of the cylinder there is also an opening in the head as at 81 and a tunnel 83 is defined in the head and a shaft 37 is rotatable therein in a manner similar to that referred to above in connection with 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. Through the central portion of the head 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
OMPI
"Ϋ.
into the chamber 103 in a manner which will now be described.
Referring to the shaft 36, 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. As the shaft rotates, however, this passageway will be closed; and at that time a spark will be ignited as at 50 which will cause an explo¬ sion driving the piston 22 downwardly and, on its uptake stroke, the hole 92 in the shaft 37 will have rotated into alignment with the hole 302 in the hood 303 which is bolted as at 305 to the upper end of the head and the upwardly moving piston will cause the gases to exhaust through the opening 81 and diametri¬ cal passageway 92 through the shaft 37 to exit through the hole 301. Referring now to Figure 3, it is seen that the passageways 90 and 92 of the cylinder 20 are elongated, that is, each has a substantial axially extending mouth to mate with the diametrical size of the cylinder.
Referring further to Figure 3, and particularly to the opening designated by the numeral 401 for convenience, it is seen that 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. This is true with respect to each of the diametrical passageways through the shafts comprising the rotary valves. Seal means are pro¬ vided on each of the shafts. These seal means are of two types: As shown in Figure 2, circumferential
OMPI
"
slots which extend in the chord direction are pro¬ vided; and in each there is received a 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. It is noted that the oil distribution means 902 shown in Figure 2 is utilized 5 to distribute oil along the length of the shaft. In the preferred embodiment longitudinally extending passageways are provided in the groove for lubrication between the exterior surface of the shaft
'
and the interior surface of the tunnel through the head, as indicated by the numeral 902, which are suitably fed as by oil lines 903, 904.
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.
Claims
1. For an internal combustion engine of the type having a block defining at least one cylinder of a predetermined radius and including a head spanning the cylinder and a piston reciprocable with respect to the head in the cylinder, an improved valve means in the head comprising a smooth shaft journaled in the head and having a shaft portion spanning a port¬ ion of the cylinder and said shaft having a diametri¬ cal passageway of a cross sectional area extending parallel to the centerline of the shaft which is at least as great as the predetermined radius of the cylinder and circumferentially is of a distance substantially equal to one-sixteenth of the circum¬ ference of the shaft and seal means in the shaft carried rotatingly with the shaft and longitudinally extending, circumferentially spaced recesses extend¬ ing dep-thwise at an angle with respect to the radius, which is common with respect to all of said recesses in said shaft and said seal means comprising a seal member longitudinally extending and arranged in each recess in said shaft, and a crank shaft connected to the piston and including force transmission means interconnecting the crank shaft, the shaft comprising said improved valve means.
2. The device as set forth in claim .1 wherein a pair of said shafts are provided in combination with an internal combustion engine.
3. The device as set forth in claim 1 wherein longitudinally extending slots are provided depthwise in said shaft and seal means are arranged in said recesses.
4. The device as set forth in claim 1 wherein said diametrical hole is of a cross sectional area
4
VI circumferentially equal to 1/16 of the circumference of the shaft.
5. The device as set forth in claim 1 wherein a spring means is provided in each recess to urge the seal means yieldingly outwardly beyond the shaft circumferentially into engagement with the head.
OMPI IPO
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| PCT/US1981/001099 WO1983000722A1 (en) | 1981-08-17 | 1981-08-17 | Rotary engine valve with improved seals and lubrication system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| EP0086190A1 true EP0086190A1 (en) | 1983-08-24 |
Family
ID=22161371
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP19810902358 Withdrawn EP0086190A1 (en) | 1981-08-17 | 1981-08-17 | Rotary engine valve with improved seals and lubrication system |
Country Status (2)
| Country | Link |
|---|---|
| EP (1) | EP0086190A1 (en) |
| WO (1) | WO1983000722A1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2076063B1 (en) * | 1992-04-24 | 1997-05-16 | Santiago Antonio Serralvo | IMPROVEMENTS INTRODUCED IN EXPLOSION MOTORS. |
| US5579730A (en) * | 1996-02-09 | 1996-12-03 | Trotter; Richard C. | Rotary valve head assembly and related drive system for internal combustion engines |
| SE512935C2 (en) | 1998-08-13 | 2000-06-05 | Dafab Ab | Valve device for an internal combustion engine |
| ES2242549B2 (en) * | 2005-04-14 | 2009-09-16 | Antonio Ferreres Lopez | ROTARY DISTRIBUTION VALVE FOR THERMAL ENGINES FOUR HYDROGEN PROPULSION TIMES. |
| ITPA20100018A1 (en) * | 2010-04-20 | 2011-10-21 | Vincenzo Adamo | FLUTE DISTRIBUTION SYSTEM. |
Family Cites Families (7)
| 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 (en) * | 1926-09-22 | 1928-02-20 | Four-stroke valveless engine with rotary distributor | |
| 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 (en) * | 1951-05-19 | 1953-09-15 | Rotary timing for four-stroke internal combustion engine | |
| CH354622A (en) * | 1957-11-22 | 1961-05-31 | Mottet Armand | Internal combustion piston engine |
-
1981
- 1981-08-17 EP EP19810902358 patent/EP0086190A1/en not_active Withdrawn
- 1981-08-17 WO PCT/US1981/001099 patent/WO1983000722A1/en unknown
Non-Patent Citations (1)
| Title |
|---|
| See references of WO8300722A1 * |
Also Published As
| Publication number | Publication date |
|---|---|
| WO1983000722A1 (en) | 1983-03-03 |
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Legal Events
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| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
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| AK | Designated contracting states |
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| 18D | Application deemed to be withdrawn |
Effective date: 19831018 |