IL43857A

IL43857A - Internal combustion engine

Info

Publication number: IL43857A
Application number: IL43857A
Authority: IL
Original assignee: Green E
Priority date: 1973-09-25
Filing date: 1973-12-19
Publication date: 1977-05-31
Also published as: IL49841A; ES421671A1; IT1006139B; SE397564B; JPS5059608A; BR7309917D0; GB1447289A; CH592805A5; AU6387173A; JPS5213566B2; IL49841A0; DE2365830C3; FR2250383A5; NL162174B; DE2365830A1; GB1447290A; DE2363077A1; IE40312L; CA992462A; JPS52104609A

Abstract

1447289 Linkwork E H GREEN and E H GREEN Jnr 20 Dec 1973 [25 Sept 1973] 59235/73 Heading F2K [Also in Division F1] In an oscillating-vane I.C. engine (see Division F1) each vane 1 is mounted for oscillation on a two-piece shaft 2 having at its free end a radial arm 6 pivoted to one end of a connecting rod 1 which is eccentrically mounted on a disc 9. As the vane 1 oscillates the disc 9 is rotated to drive the main shaft 22 via gear wheels 12, 21. The two piece shaft 2 is interconnected by a tongue and slot 4, 5 which allows for slight misalignment of the two shaft portions due to thermal expansion of the combustion chambers of the engine relative to the gear casing. [GB1447289A]

Description

INTERNAL COMBUSTION ENGINE > r &p- -SBWARD H. GREEH-a?t<-t-BSW¾R&- ^^ INTERNAL COMBUSTION ENGINE ABSTRACT OF THE DISCLOSURE An internal combustion engine comprising a translation case or gear case, a combustion chamber and a rotary valve.

The rotary valve is adjacent to and on one side of the combustion chamber. The combustion chamber contains a rectangula piston plate. The piston plate is hinged at one end to a shaft and adapted for oscillatory movement in the combustion chamber. The walls of the combustion chamber are formed by the inner wall of a first circular disc, the inner wall of a second circular disc, the inner wall surfaces of the engine block, and the surface of the piston plate. The rectangular piston plate is integral with or fixedly connected to the shaft, which shaft is fixedly connected to a first linking means.

The piston plate, shaft and first linking means are movably connected to a second linking means, a throw and a drive gear.

The fixed relationship between the piston plate, shaft and first linking means and their movable relationship to the second linking means, throw and drive gear are such that during the combustion-power cycle, when a compressed fuel-air mixture is burned in the combustion chamber the piston plate is high unburned or partially burned hydrocarbons in their exhausts which add to the problems of air pollution.

A second type of rotary engine which utilizes oscillating piston plates similar to the type described herein have generally been ineffective in ^hang ing . the oscillatory motion of the piston plate to useful rotary motion.

One of the principal problems encountered with engines of this type was how to design for the lateral ahd radial expansion of the hot combustion chamber portion of the engine relative to the cooler gear and mechanical motion translation portion of the engine.

It is an object of this, invention to provide an internal combustion engine which is relatively simple, compact, inexpensive, easy to manufacture and capable of generating a high power output for its weighc and size.

Another object of the invention is to provide an engine which has a new and efficient means of translating the oscillatory motion of the rectangular piston plate to rotary motion of the main gear and main shaft.

A further object of the invention is to provide an engine of the type described herein which is capable of having the oscillatory motion of the pi on plate, in sequence, accomplish the functions of exhaust, intake, compression and combustion-power.

Another object of the: present invention is to provide s o r * .

Another object of the present invention is to ^, provide for the lateral and radial hea expansion of the combustion chamber portion of the engine relative to the cooler gear and mechanical motion translation portion of the engine* Another object of the invention is to provide an internal combustion engine which is easy to maintain* The invention relates to an internal combustion engine comprising an engine block containing at least one combustion chamber and a translation gear case, means which oscillate back and forth in said combustldn chamber* a shaft fixedly connected to said oscillating means and a main shaft carried by said engine block* characterized in that the translation gear case is spaced away from the combustion chamber and is disposed adjacent only a single side of the combustion chamber, and heat expansion means provide radial and lateral heat expansion of portions of the engine block and combustion chamber relative to portions of the translation gear case, means in the translation gear case operably connecting the oscillating means and shaft to the main shaft', whereby during the combustion power cycle the oscillator^ motion of said oscillating means is transmitted and converted to ratoray motion of the main shaft* - 3a - cooler gear and mechanical motion translation portion of the engine.

Another object of t e invention is to provide an --Internal combustion engine -flrtch- is eas^r .o ma -t -ir . 11 A brief description of the figures of the drawings is given below.

Figure 1 is a cross-section of a preferred embodiment taken along a vertical line enerally through the central axis. For purposes of clarity the drive' gear and main-gear are shown in elevation.

Figure 2 is an isom tric drawing of the rectangular piston plate and the related fixed and moving parts.

Figure 3 is an isometric drawing of the connecting links, throw, drive gear, main gear and main shaft.

Figure 4 is a vertical section taken generally along line A-A of Figure 1 looking in the direction indicated by the arrows showing the relationship between the connecting links, throw, drive gear, main gear and main shaft.

Figure 5 is an enlarged schematic view of the arrangement of the rectangular piston plate, the first and second linking means," the throw, drive gear and a portion of the arrows showing four combustion chambers arranged for e$0|l firing in the various cycles of exhaust, fuel intake, compression and combustion-power.

Figure 7 is a vertical section of another embodiment of the invention showing the same view of the engine as shown in Figure 6 in which embodiment the engine is arranged for single firing in each combustion chamber.

Figure 8 is a vertical section taken generally along line C-C of Figure 1 looking in the direction indicated by the arrows showing a view of surface 46a of the translation case 46.

Figure 9 is a vertical section taken generally along line D-D of Figure 1 looking in the direction indicated by the arrows showing a view of surface 27a of the first circular disc 27.

Figure 10 ie a detailed cross-section of Figures 8 and 9 taken generally along lines E and F respectively.

Figure 11 is a vertical section taken through the center line of shaft 2.

Figure 12 is an isomotric drawing showing a partially expanded view of the engine block and first and second circular discs 27 and 28 respectively.

Figure 13 is a three dimensional expanded view showing the second circular disc 28, rotary valve 33 and end plate 38.

Figure 14 is an end viow taken generally along line G-G of Figure 1 looking in the direction indicated by the arrows showing fuel inlet means 42 and xhaust means 40.

DESCRIPTION OF THE I VENTION This invention relates to a new and useful ■ improvement in internal combustion engine;;. The invention particularly relates to an internal combustion engine which is compact and simple in design and yet capable of developing a large amount of power relative to its overall size and weight.

The invention more particularly relates to a novel four cycle internal combustion engine comprising oscillating piston plates. The oscillatory motion of the piston plates caused by the combustion of a compressed fuel-air mixture in the combustion chamber is effectively and efficiently translated or changed into useful rotary motion. The engine block of the engine of the present invention has one or more combustion chambers. Each chamber can be arranged to cooperate with the rectangular piston plate for single or dual firing.

A preferred embodiment of the engine of the present invention comprises a four-cycle engine. An illustration of this embodiment is an engine having four combustion chambers spaced 90° apart. Each cl.

An ignition roeunr. for the combos* i on cha:n r\i i provided in the outer port on of the onujne block. in the dual firing embodiment , coir.j .st o.n clumbers are formed on each side of the rcctnrnular i .«·. ι.··>η pi ate. The chamber? arc-formed by the piston plate surfaces, the engine block and the first and second circular discs.

The rotary valve contains an exhaust groove and an inlet groove. The second circular disc has four ports spaced 90° apart, which communicate with the four combustion chambers The ports in turn function aa both exhaust ports and inlet por During each 360° rotation of the rotary valve, the rotary valve exhaust groove ¾nd inlet qroove come into contact with the ports in the second circular disc and through the ports the exhaust groove and inlet groove communicate with the combustion chambers.

Each rectangular iston plate in each chamber oscillates twice in each, direc: r "_n for one revolution of the rotary valve. In the dual firm.,* embodiment the rotation of the rotary valve exhaust groove a d inlet groove passed the ports in the second circul ir dv .;..· is coordina ed wi h the oscillation .of the rectangular -· i ··: on plat ■■"■:-· r.ueh tha two combust on c ambe at ' .. s.\nu in t n ,·. throu h, the The operation of the engine briefly described is as follows. After completion of th combustion power cycle the piston plates oscillate back towards a port which has just been opened by the exheiust groove of the rotary valve such that the spent combustion gases are expelled through the open port and the exhaust groove. The opened port closes at the end of the exhaust cycle and then opens to permit fuel-air mixture to enter through the open port and the inlet groove in the rotary valve during the intake cycle which follows. During the fuel intake cycle, the rectangular piston plates move away from the open port to draw the fuel-air mixture through the port and into the combustion chambers. After the fuel intake cycle, the port is closed by the rotary valve. The plates then oscillate towards the now closed port to compress the fuel air mixture. At the proper time the compressed mixture will be ignited by ignition means which starts the combustion-power cycle causing the piston plates to oscillate away from the closed port. After completion of the combustion power cycle, the po t is again opened by the exhaust groove in the rotary valve and the pis tor, plates oscil late towards the opened port to exhaust the combustion gases through the port and the exhaust groove. The four cycles then begin again.

A more detailed descr p ion of the operation of the engine is given with reference to Figu e;-- a t ·α 13 of the firing embodiment of the invention.

The combustion chambers A as shown in Figure 6 have just completed the exhaust cycle. In carrying out the exhaust cycle, exhaust groove 35 in rotary valve 33 rotated counterclockwise first in communication with port 29, channels 29 (a,b) and combustion chambers A and then passed and out of communication with port 29 and combustion chambers A and channels 29 (a,b). During the counter-clockwise rotation of rotary valve 33, port 29 which was closed was opened by exhaust groove 35, was closed, was opened again by inlet groove 34 and then closed again.

Prior to the exhaust cycle, combustion chambers A had previously undergone a combustion-power cycle. At the end of the combustion-power cycle, the piston plates were on the opposite side of the combustion chambers A, i.e. away from port 29. As the piston plates 1 commenced their oscillating motion towards port 29, the left hand or leading edge of the exhaust groove 35 first came into contact with port 29 and channels 29 (a, b). While the piston plates oscillate towards port 29 and during the time the exhaust groove 35 is in communication with port 29, the combustion gases are expelled through port 29 and channels 29 (a,b) and exhaust groove 35.

In the position shown in the drawing, combustion - f V the port 29 is below the engine block in the second circular disc 28. The exhaust groove 35 and the fuel intake groove 34 are in rotary valve 33 which is belo the second circular disc 28.

During the time the combustion chambers A are going through the exhaust cycle, combustion chambers B are going through the fuel intake cycle. During the fuel intake cycle, a fuel-air mixture in vapor phase is fed through fuel inlet port 42 in end plate 38, through inlet groove 34 in rotary valve 33, through port 30 in second circular disc 28 and into combustion chambers B.

Combustion chambers B as shown in Figure 6 of the drawings have completed the intake cycle. The rotary valve 33 and fuel inlet groove 34 rotate counter-clockwise and groove 34 comes into communication with and opens port 30 in the second circular disc 28. When the leading edge of intake groove 34 first comes into contact with port 30 and channels 30 (a,b) , the rectangular piston plates 1 are at a position adjacent to port 30. As the fuel inlet groove 34 continues its movement in a counter-clockwise direction and groove 34 comes more fully into communication with port 30, the piston plates 1 oscillate away from port 30 to the position shown in the drawing. When the piston plates 1 have reached this point, the fuel inlet groove 34 has rotnted passed and out of communica position and the two adjacent combustion chambers B are in the completed fuel intake position, the exhaust groove 35 and the fuel inlet groove 34 are not in communication with either combustion chambers A or combustion chambers B.

The combustion chambers C in the immediately preceding cycle had completed the fuel intake cycle as the fuel inlet groove 34 passed in a counter-clockwise direction first in communication with port 31 and channels 31 (a,b), to open port 31, and then out of communication with port 31 and channels 31 (a,b), to close port 31. During the time the fuel inlet groove 34 rotated 90° in a counter-clockwise direction to the position shown in Figure 6, the rectangular piston plates in combustion chambers C oscillated from a position away from port 31 to a position adjacent port 31, to compress the fuel-air mixture in chambers C. In the position shown, the rectangular piston plates have just completed the compression cycle in combustion chambers C and the compressed fuel mixtures within the next instant will be ignited by the ignition means 36. On ignition of the compressed fuel mixture in combustion chambers C and with the continued counter-clockwise rotation of the rotary valve 33, the rectangular piston plates in chambers B will oscillate towards port 30 which is closed and compress the fuel mixture in combustion chambers B, while the piston plates in chambers D will oscillate toward port 32 and will exhaust The combustion chambers D have in the position shown . just completed the combustion-power cycle. Visualize in the immediately proceeding cycle, while the chambers D were in the full compression cycle, the leading or left hand edge of the exhaust groove 35 was just approaching port 29 but was not yet in communication with port 29, During the combustion-power cycle of combustion chambers D, the rectangular piston plates oscillated away from port 32 while the exhaust groove 35 came into communication with port 29 and channels 29 (a,b) allowing the combustion gases in combustion chambers A to be expelled through port 29 and exhaust groove 35.

As shown in the drawing, port 32 is closed and combustion chambers D are isolated from exhaust groove 35. The rotary valve 33 rotates in a counter-clockwise direction and the exhaust groove 35 comes into contact with port 32 and opens port 32. Through the open port 32, and channels 32 (a, b), combustion chambers D communicate with exhaust groove 35 and the exhaust cycle of combustion chambers D is carried out.

It can be seen from the above that each 90° counter-clockwise rotation of the rotary valve 33 is coordinated with the oscillatory movement of the rectangular piston plates in the combustion chambers 16.

The exhaust groove 35 and the fuel inlet groove 34 in the rotary valve 33, the p rts 29, 30, 31, and 32 in the is no ' communication between the exhaust groove or the inlet groove and any of the chambers 16.

In operation of the engine any two adjacent piston plates oscillate away from each other or towards each other. Visualize the two rectangular piston plates 1 oscillating towards port 29, while the two opposite rectangular piston plates 1 oscillate towards port 31. As each of the four piston plates reach the end of their travel, they reverse themselves and then travel in the opposite direction. This oscillatory motion occurs twice for each piston plate per 360° revolution of the rotary valve 33. The four engine cycles of exhaust, intake, compression and combustion-power take place continuously for each of the combustion chambers, two chambers at a time (dual embodiment) , once per 360° revolution of the rotary valve 33, The operation of the engine provides a balanced almost continuous smooth power output by providing one or two power cycles for each of the combustion chambers per revolution of rotary valve 33 and of the main shaft of the engine.

The engine of the present invention provides substantial advantages in engineering, manufacturing and design improvements over conventional engines of comparable size including: more horsepower per weight of engine, more mileage per gallon, fewer total parts, fewer moving parts, and compact per cc of displacement and horsepower, simplicity of manufacture, assembly and maintenance, and high degree of reliability and useful life, Another advantage that the engine performs all the functions of an internal combustion engine without the use of conventional intake and exhaust valves and all the complex mechanism normally required for the timing and operation of such valves.

Another advantage of the construction of the engine is that it provides a simplified means of ignition. Once started the engine can have automatic self-ignition. For example, after the engine ha bean started and is in operation automatic ignition can be obtained by diesel engine type firing.

A further advantage of the present invention is that the means for lubricating and. cooling the engine operates as a sealed unit. The lubricating oil is not exposed to the atmosphere and can thus not volatilize. The lubricating oil is not directly exposed to the combustion chambers and thus is not subjected to oxydative degradation. Both of these features act to minimize air pollution that may result from operation of the engine, A specific advantage of the present invention as and drive shaft, whereas the conventional engine provides o ly one power stroke per two complete revolutions of the drive shaft. The engine of the present invention is thus capable of producing about two to rour times the power of a conventional engine of the same number of chambers and displacement.

Other advantages of the present invention will become obvious to those skilLed in the art by the following description of the accompanying figures of the drawings.

In the description that follows, like reference numerals indicate like parte.

Figure 1 is an expanded side view taken through a vertical section along the central axis of the engine. Figure 1 shows the overall construction of the engine including the translation case or gear case 46, the engine block 26 and combustion chambers 16, the piston plate 1 and shaft 2, linking means 6 and 7, drive gear 12, main gear 21, main shaft 22 and the rotary valve 33.

In the operation qf the engine a fuel air mixture is fed through inlet 42 and the combustion products expelled through exhaust outlet 40.

Looking from left to right at the drawing, bolts 60 fixedly connect end disc 49 to translation case 46. End disc 49 has integral therewith cylindrical hub 56 through which main shaft 22 passes. Suitable oil sealing means, not shown, are provided between end disc 49 and the translation case 46. Shaft 58 and bolts 59. Flange 57 may be made as part of main shaft 22 or may be made separately and welded or otherwise fixedly attached to shaft 22. Shaft 22 passes through engine block 26, rotary valve 33 and end plate 38. A first circular disc 27 and a second circular disc 28 are fixedly connected to engine block 26 by suitable bolts, not shown.

Shaft 2 which is integral with the piston plate 1 is supported by end plate 49, translation case 46, first circular disc 27, engine block 26 and second circular disc 28. , The end plate 38 is fixedly connected to the second circular disc 28 by bolts 77 and is integral with cylindrical hub 43. The lower portion of the second circular disc 28 and end plate 38 have attached thereto legs 78 for securing the combustion chambers and rotary valve portion of the engine to a suitable base 86, e.g., an engine mount. The portions of the engine indicated as 89 in cooperation with suitable bolt means secure the translation or gear case portion of the engine to base 86.

The rotary valve 33 is positioned between the second circular disc 28 and the end plate 38. The main shaft 22 is connected to the rotary valve 33 by four connecting pins 79 and rotates with the rotary valve and relative to the second circular disc 28 and end plate 38. The pins 79 are free chambers 16. Annular oil space 24 provides lubrication and annular air space 25 provides heat insulation and protection for the main shaft 22 from the heat of the combustion chambers 16. End plate 38 on the right end of main shaft 22 has passing therethrough fuel inlet port 42 and outlet port 40. Oil seal 80 prevents leakage of oil from around the main shaft 22.

The rotary valve 33 cooperates with the second circular disc 28 and the end plate 38 to provide inlet means for the fuel and air mixture to the combustion chambers and an exhaust means for the combustion products by at the proper time and in the proper sequence opening and closing ports 32, 31, 30 and 29.

The walls of combustion chamber 16 are formed by the inner wall surface 27a of the f rs circular disc 27, the inn^er wall surface 28a of the second circular disc 28, the surfaces of the engine block 26 and the surfaces of piston plate 1.

The rectangular piston plate 1 is integrally connected and hinged to shaft 2, which shaft is in turn fixedly connected to a first linking means 6w The piston plate 1, shaft 2 and first linking means 6 are movably connected to a second linking means 7, throw 9 and drive gear 12 whereby the oscillatory motion of the piston plate is changed into a rotary motion of the drive gear 12. The drive gear 12 is movably connected to shaft 13 by bearing means 55. $haft 13 is fixedly connected The rectangular piston plates 1 oscillate with shaft 2 in combustion chambers 16. Shaft 2 is supported by bearing means 45 in translation case 46 and is sealed by oil seal means 47. Bearing means 45 forms a thrust face 53 which seats in a recess formed in translation case 46. Shaft 2 is also supported by bearing 48 which seats in a recess formed in end disc 49. Thrust bearing raceways 61 and thrust bearing 62, thrust bearing raceways 63 and thrust bearing 64 and thrust bearing raceways 65 arid thrust bearing 66 provide support and bearing means for main shaft 22 and main shaft 22 rotates on the bearings. A socket for raceway 61 is formed in the hub 56 portion of end disc 49; a socket for raceway 63 is formed in translation case 46, and a socket for raceway 65 is formed in the hub 43 portion of end plate 38. A small shoulder 69 formed on main shaft 22 locates washer 67 for cooperation with thrust bearing 62. Flange 57 positions thrust bearing 64, Thrust bearing 62 and washer 67 in cooperation wit!) thrust bearing 64 and flange 57 prevent lateral movement f shaft 22 in translation case 46.

The inside of the translation case 46 is filled with oil to cool and lubricate thct moving parts. The oil is supplied through oil inlet port 75 and passes through and around the moving parts including link 6, link 7, throw 9, drive gear 12 and main gear 21 and leaves the translation case through oil outlet port 76, The cooling and lubricating oil Figures 2 and 3 - There are two parts, part 3a and 3b to shaft 2. Shaft 2 is fixedly connected to link 6 by key 51. There are two legs to link 6. Shaft 19 passes through the two legs and through link 7, operably connecting link 6 to link 7. Shaft 19 is fixedly connected to link 6 by pin 54. Bearing means 17 provides a movable connecting eans between shaft 19 and link 7. Shaft 14 is integral with throw 9 and extends through link 7. Link 7 is movably connected by bearing means 18 to shaft 14. Throw 9 is fixedly connected to drive gear 12, by hexagonal portion 15 of gear 12 which is inserted in the recess in the surface of throw 9. Shaft 13 extends through throw 9 and drive gear 12 and is fixedly connected to the translation case 46.

Shaft 13 is movably connected to throw 9 and gear 12 by suitable bearing means 55.

The fixed relationship of rectangular piston plate 1, shaft 2 and connecting link 6 and the movable relationship of these parts with link 7, throw 9 and gear 12 causes the oscillatory motion of the rectangular piston plate back and forth in the combustion chamber 16 to be translated or changed into rotary motion of drive gear 12. Drive gear 12, see Figure 5, rotates in a clockwise direction. The drive gear 12 drives against main gear 21 and causos the main gear 21 and main shaft rotates away from the viewer. With reference to the rotary valve means 33, shown in Figure 13, the rotation is counterclockwise.

Piston plate 1 can have recesses on its side edges and outer edge in which recesses sealing and bearing means 20 can be placed. The sealing and bearing means can be pressed outwardly by suitable spring means not shown.

Figures 4 and 5 - Figure 4 is a cross-section taken generally along line A-A of Figure 1 looking in the direction indicated by the arrows showing the relationship between the connecting links 6 and 7, throw 9, drive gear 12, main gear .21 and shaft 22. The outer surface 46b of the translation case 46 can be seen in the background.

The translation c¾¾e 46 supports shaft 13, throw 9 and gear 12. Shaft 13 is fixedly connected to the translation case. Gear 12 and throw 9 rotate around shaft 13 on bearing means 55 in a clockwise direction, causing rotation of main gear 21 and shaft 22 in a counter-clockwise direction.

Figure 5 is a slightly enlarged detailed view of the arrangement of the rectangular piston plate 1, shaft 2, linking means 6, linking means 7, throw 9, shaft 14 and drive gear 12. The relationship of shaft 19, pin 54 and bearing means 17 to linking means 6 and 7, and the relationship of bearing means 18 to linking means 7, shaft 14 and throw 9 are also shown.

Figure 6 - Figure 6 is a vertical section taken generally along line B-B of Figure 1 looking in the direction indicated by the arrows showing four chambers 16 arranged for dual firing- in the various cycles of exhaust (position A), fuel intake (position B) , compress on (position C) and combustion-power (position D) . (See discussion of engine operation above.) This figure shows the inner wall surfaces 26a of engine block 26, the surfaces of the piston plate 1 and the inner wall surface 28a of the second circular disc 28 which form walls of the combustion chambers. The drawing also shows in cross-section a view of the rectangular piston plate 1, shaft 2, insulating metal heat shield 23, and annular oil lubricating space 24, heating insulating space 25 and main shaft 22.

The ignition means 3 # the piston plate 1 and the channels 29 (a, b), 30 (a, b) , 31 (a, b) and 32(a b) are in the engine block 26. The second circular disc 28 is under engine block 26 and piston plate 1. The openings 37 are in the second circular disc 28. The ports 29, 30, 31 and 32 are also in the second circular disc 28.

The ports 29, 30, 31 and 32 communicate with the chambers 16, and the ignition means 36 through the channel means 29 (a, b), 30 (a, b), 31 (a, b) and 32 (a, b), respectively. The ignition 36 means is located in about the center of chamber 16 The rotary valve 33 is under the second circular disc 28 and contains the exhauwt groove 35 and inlet groove 34. The exhaust groove 35 and the fuel inlet groove 34 are about the same size and shape and a c radially about the same distance from the center axis of the engine.

The exhaust groove 35 extends into the surface of rotary valve 33 but does not extend through rotary valve 33. Exhaust groove 35b is radially offset from groove 35. Exhaust groove 35b extends into the surface of the rotary valve on the side opposite groove 35, but dpes not extend through rotary valve 33. Grooves 35 and 35b communicate with each other through connecting channel 35a, The inlet groove 34 extends completely through the rotary valve 33.

Figure 7 - Figure 7 ^.s a vertical section of another embodiment of the invention growing essentially the same view of the engine as shown in Figure 6. The engine, however, is arranged for single firing in each combustion chamber instead of dual firing. The operatipn of the engine except for the single firing is otherwise similar to that described above for the dual firing embodiment, The principal difference in structure is that the channels, 29a, 30a, 31a and 32a have been omitted. This prevents communication between chambers 16, on the side of the piston plates from which the channels have been omitted, with ignition means 3o, ports 29, 30, 31 and 32 movement of the piston plates in the side of the combustion chamber that does not fiie-., by allowing gas to vent in and out of the non-firing portion of the chamber. The vent 74 also provides a means for enting and collecting any blow-by gases from the combustion chambers 16. The collected gases, to reduce air pollution, can bo recycled to the fuel intake means and burned.

Figure 8 - Figure 8 is a vertical section taken generally along the line OC of Figure 1 looking in the direction indicated by the arrows and showing a view of surface 46a of translation case 46. The main shaft 22 passes through circular opening 70. The shaft 2 passes through opening 71. Annular space 24 is filled with oil and provides lubrication for shaft 22. Expansion and support members 72 are bolted into the surface 46a of translation case 46. These expansion members have a tight sliding fit and cooperate with the expansion members 81 (Fig. 9) and allow longitudinal expansion and radial expansion of the hot engine block 26 portion of the engine relative to the cooler translation case 46 portion of the engine.

Figure 9 - Figure 9 is a vertical section taken generally along line D-D of Figure 1 looking in the direction indicated by the arrows showing a view and surface 27b of the Expansion and support members 81 are bolted into the surface 27b of the first circular disc 27. The expansion members have a tight sliding fit and cooperate with the expansion members 72 (Fig..8) and allow longitudinal expansion and radial expansion of the hot engine block 26 portion of the engine relative to the cooler translation case 46 portion of the engine.

Figure 10 - Figure 10 is a detailed view of Figures 8 and 9 taken generall along line E and F, respectively. From this figure of the drawings, the longitudinal and radial heat expansion means can be more easily seen and understood.

Figure 11 is a detailed view of the connecting means and expansion means provided for shaft 2. Shaft 2 can, in order to allow for heat expansion, be made in two parts, 3a and 3b. A two piece grease coupling 47a is provided for retention of lubrication of the end portions 3a and 3b. The coupling is spring loaded to allow lateral and radial heat expansion of the tongue 4 and groove 5 end portions. Shaft 2 has packing and oil seal gland 47 which sits in the wall of translation case 46. Seal 47 prevents seepage of oil from the interior of the translation case into the engine expansion space 52.

Figure 12 is an isometric drawing showing a partially expanded view of the engine block 26 and the first disc 27 respectively, can readily be seen. The first circular disc 27 is bolted or otherwise fixedly connected to one side of the engine block 26 and second circular disc 28 is bolted or other-wise fixedly connected to the opposite side of the engine block. The chambers 16 are tightly sealed between the first and second circular discs by gasket means not shown.

The engine block 26 has four chambers 16. The chambers 16 are generally triangular in shape and are spaced 90° apart. The apex of the triangle is away from the central axis of the engine. The angla^ at the apex of the triangle can be 30 to 180° and preferaply 60 to 80°. The base of the triangle is curved to form the outer circumference of a circle having its center at the center of shaft 2.

Figure 13 is a three dimensional expanded view showing the second circular disc 28, rotary valve 33, and end plate 38. In this drawing the means for providing communication between ports 29, 30, 31 and 32 and exhaust groove 35, connecting channel 35a, groove 35b, exhaust ring 39 and exhaust port 40 and. the means for providing cQipmunication between ports 29, 30, 31 and 32 and fuel inlet groove 34, fuel inlet ring 41 and inlet port 42 can be seen.

The rotation counter-clockw se of rotary valve 33, brings exhaust groove 35 and inlet groove 34, in turn in contact with each of the ports 32, 31 30 and 29, whereby the combustion The exhaust groove 35 and the inlet groove 34 are dimensioned such that when centered between, for example, ports 32 and 29, and ports 29 and 30, respectively, neither is in contact or communica ion with any of the ports or chambers 16.

Exhaust groove 35 s about the same size and shape as fuel inlet groove 34 and is spaced 90° from groove 34.

Groove 35 and groove 34 are about the same radial distance from the central axis of the rotary valve 33. Groove 35 does not go all the way through rotary valve 33. Groove 35 can have a depth about 2/3 the thickness of rotary valve 33.

Groove 35b is on the side of rotary valve 33 which is opposite groove 35 and is radially offset from groove 35. Groove 35b can have a depth of about 2/3 the thickness of the rotary valve 33. Grooves 35 and 35b are connected by connecting passage 35a. Connecting passage 35a can be parallel to the plane of rotary valve 33 and can have a thickness of about 2/3 the thickness of rotary valve 33 such that it overlaps both groove 35 and groove 35b providing communication between the two grooves. The exhaust groove 35b is always in communication with annular exhaust ring 39 and exhaust port 40 in end plate 38. Annular exhaust ring 39 does not extend all the way through end plate 38 and is of sufficient depth and width to exhaust groove 35b, annular exhaust ring 39 and exhaust port 40 to the exterior of the engine. Vhen the exhaust groove 35 is not in contact with port 29, or any of the other ports 30, 31 or 32, exhaust gases cannot leave the chambers 16.

Inlet groove 34 extends through rotary valve 33 and is always in communication with annular fuel intake ring 41, and through fuel inlet port 42 is in communication with the fuel source. The annular ring 41 does not extend through the wall of end plate 38 and is of sufficient depth and width to provide adequate cross-sectional area to supply fuel to the engine. When the inlet groove 34 is in contact with port 29, fuel mixture will pass into the chamber 16. When inlet groove 34 is not in communication with port 29 or one of the other ports 30, 31 or 32, fuel will not pass into any of the chambers 16.

The rotary valve 33 fits into the end plate 38. The rotary valve 33 and the end plate 38 are closely dimensioned to provide a rotatable but tight sealing fit such that there is no communication between exhaust groove 35b and inlet groove 34 or between annular exhaust ring 39 and annular inlet ring 41 Similarly the rotary valve 33 and the second circular disc 28 have a rotatable tight sealing fit such that except when groove 35 or groove 34 are in contact with one of the ports 29, 30 31 or 32, there is no communication between either of the grooves and any of the chambers 16. Rotary valve 33 Figure 14 - Figure 14 is an end view taken generally along line G-G of Figure 1 looking in the direction indicated by the arrows showing a view of end plate 38, exhaust port 40 and fuel inlet port 42. Legs 78 carry and support the engine and are secured to engine mount 8b by bolts 85. Figure 14 of the drawing also shows a conventional type of commutator ignition ring means which can be used for timing a spark coil to control ignition. Metal conductors 91 are carried on shaft 22 and are separated by insulators 92. Roller 93 is spring biased by spring conductor 94 to intermittently contact conductor 91. Line 95 is electrically connected to conductor 94 and to a suitable spark coil means.

In the embodiment of e engine described above in Figures 1 to 14 of the drawings, the rectangular piston plate can be very closely dimensioned with respect to the inner wall surface 27a of first circular (-jisc 27, the inner wall surface 28a of the second circular di$p 28 and the inner wall surfaces 26b of the engine block 26 such that the engine can be operated without separate gas seal or bearing means at the sides and/ or outer edge of the piston p ate 1. The sizing of the rec-tangular piston plate with respect to the inner wall surfaces of the combustion chamber is very closely controlled. The clearance between each side edge and the outer edge of the piston plate and surface of the combustion chamber is closely power cycles can be* carried out without substantial loss of gas pressure into or out of the combustion chamber. In order to improve the operation of the engine, the edges of the piston plate and/or the said inner wall surfaces of the combustion chamber can be suitably treated by Known means to improve the gas seal and contact between the surfaces.

The rotary engines of the present invention can be built throughout the same horsepower and displacement range as conventional lawn mower, ιβο¾βχκ ^¾ί<χ¾, automobile, truck, marine and aircraft engines with the important difference that the engines of this invention will approximately thirty to sixty percent lighter in weight and one third to one fourth the size for the same displacement and horeepower. Engines having one or two combustion chambers are particularly useful for lawn mowers, motorcycles and small cars. Engines having two or four or more combustion chambers are particularly useful for automobiles and trucks and for boats Depending on the size, power output and the particular use for the engine, the power cap be taken off through the main shaft, a suitable clutch plate, automatic transmission, chain, pulley and/or gear means. Ignition can be provided by a convention spark or glow plug and coil or by a conventional diesel t e firin . The firin of the engine is in sequence, designed to operate on a wide range of fuels from low octane to high octane gasoline, diesel fuel, kerosene, alcohol, and liquified gases such ae propane, butane, natural gas, etc.

Where a medium octane fuel is uyed, it can be mixed with air in a carburetor and throttled to the intake manifold. Alternatively, the fuel and air can be fed to the engine by fuel injection means using conventional automotive equipment.

The engine is both lubricated and cooled by means of oil. The oil fills the interior portion of the translation case. Because of the rotary motion of the gears and the motion of the moving parts, the oil wi¾J. be forced outwardly to cool and lubricate the engine parts in the translation case. The warm oil is cycled to an air or water cooled radiator means or other suitable heat exchange means and cooled prior to returning to the engine. The combustion chambers are preferably air cooled but can be suitably jacketed and water cooled. The various engine parts such as the translation case, engine block, first and second circular discs and end plates can be bolted, welded and/or otherwise fastened together. The engine parts are easily made by forging, casting and machining. The engine parts can be made of cast or forged iron, steel or aluminum.

The engine can easily be assembled by moderately skilled labor. Repair and maintenance of the engine is equally simple.

It is to be understood that the form of the invention from the spirit of the invention such that the scope thereof should be limited only to the ecope of the appended claims .

Claims

ED-2A Foreign Divisional Application U3857 3 March 1976

1. An internal combustion engine comprising an engine block (26) containing at least one combustion chamber (16), translation gear means (46), and rotary "valve means (33), means (1) which oscillate back and forth in said combustion chamber (16), a shaft (2) fixedly connected to said oscillating means (1) , and a main shaft (22) carried by the engine block (26) characterized in that the translation gear means (46) being disposed adjacent only a side of the combustion chamber (16) and the -rotary valve 'means (33) being disposed adjacent only a single side of the combustion chamber (16) and opposite the side on which the translation gear means (46) is disposed, the main shaft (22) being connected to the rotary valve means (33) , the gear means operably connecting the oscillating means shaft "(2) to the main shaft (22) , whereby during the combustion power cycle, the oscillatory motion of the oscillating means (1) is transmitted and converted to rotary motion of the main shaft (22) and rotary valve means (33) . . 2 , An engine according to claim 1, characterized in that the coinbustion chamber (16) has an inlet and an outlet mdans-(29), and the rotary valve means (33) has an inlet (34) and outlet (35), the combustion chamber inlet and outlet means (29) being operably associated with the rotary valve inlet (34) and outlet (33) such that during oscillatory notion of the oscillating means (1) and rotary motion of the rotary valve means (33), the combustion chamber inlet and outlet means (29) is brought into communication

2. Appln. 43857/3

3. An engine according to claim 1 or claim 2 « characterized in that the oscillating means is a piston * Plate (1).

4. : · ;'·. 4. An engine according to claim 3, characterized in that the translation gear means (46) includes, a firs linking means .(6) fixedly connected to the piston plate shaft a second linking means (7) operably connected to the first l nking means (6); a" crank throw (9); a drive gear (12); and a main gear (21), the main gear (21) being connected to the main shaft (22), said crank throw (9) and drive gear (12) being operably connected to the second linking means (7) , whereby the oscillatory motion of the piston plate (1) is transmitted, during the combustion power cycle, through the piston plate shaft (2) and first (6) and second linking means (7) and crank throw (9) and is converted to rotary motion of the drive gear (12) which drives the main gear (21) causing the main gear (21) , the main shaft (22) and the rotary Valve ".(33) "to rotate. .

5. An engine according to claim 1 or claim 4 characterized in that the oscillatory means comprises piston plate (1) which oscillates back and forth in the combustion chamber (16); a shaft (2) fixedly connected to one end of the piston plate' (l)-and operably connected to a main shaft (21) carried by the engine block (26) ; and heat expansion members (72, 81) providing racial and lateral heat expanion of portions of the engine block (26) and combustion chamber (16) relative to portions of the gear case (46) .

6. An engine according to claim 1, 4 or 5 characterized in that it has at least two combustion chambers. ' ... ,

7. "' 7. An engine according to claim 1 or claim 6 Characterized in tha the combustion chamber (16) has an '.-· '".*■·...· ·· · '. . · " » .·· "inlet and outlet" means (29a) on One side only of the os- .·;¾._.' ··■;. ·- . · · : ■ 'cillating means (1) and is adapted for single firing.

8. An engine according to claim 1 or claim 6 . characterized in that the combustion chamber (16) has an "inlet" and outlet means (29a, 32b) on each side of the os- cillating means (1) and is adapted for dual firing.

9. An engine according to claim 1, 4 or 5, characterized in that the combustion chamber has a port (29) which is in operable relationship with the rotary valve (33) , one side of the rotary valve (33) has, dis- . laced substantially the same radial distance as the port (29), a first exhaust groove (35), and a fuel inlet groove (34) , the opposite side of the rotary valve (33) has a ■second exhaust groove (35b) which is radially displaced outwardly from the first exhaust groove (35) and the inlet groove (34) , and rotation of the rotary valve (33) brings the exhaust groove (35) and the inlet groove (34) in turn into communication with the port (29) and combustion chamber (16) .

10. An engine according to claim 9 characterized in that the rotary valve has a connecting passage (35a) cont and s cond 5b

11. An engine according to claims 1, 4, 5, 6 or t 9, characterized in that the engine has at one end an end -plate (38) which has an annular exhaust ring (39) and an annular fuel inlet ring (41), the exhaust and fuel rings being respectively communicated with the rotary valve means · (33) . :'■ ·'-

12. !^ 'V . r .:- . -.12. An engine according to claims 1, 4, 5, 6 or 9, 'characterized in that the engine has at one end an end plate (38) which has an annular exhaust ring (39) and an annular fuel inlet^ ring. (41) , the rotary valve (3.3) having an exhaust groove (35) and an inlet groove (34), the exhaust groove (35) being in communication with the exhaust r-ing (39) and the inlet groove (34) being in communication with the inlet ring (41) .

13. An engine according to claims 1* 4, 5, 6 or 9 characterized in that there are at least four combustion chambers (16) . ' : : l . An engine according to claims 1, 4* 6 or' * i ' * characterized in that the engine block (26) is fixedly con- .-- ". ·.'""- - "*· * ''. · nect'ed to first (27) and second (28) circular discs and translation 9ear case (46) has a wall (46a) adjacent to the first circular disc (27), the inner wall surfaces (27a, 28a) of the first (27) and second (28) circular discs forming walls of the combustion chamber (16) , the outer wall (27b) of the first circular disc (27) and the adjacent wall (46a) of the translation gear case (46) containing cooperating means (72, 81) to allow for radial and longitudinal heat ex ansio of ortions of the en ine bl 2 and combustion