Ring gears – internal combustion engine

Abstract

An internal combustion engine wherein cold air or water spray is introduced into the combustion chamber to mix with the excess hot air, to cause further expansion, and hence generate more power and maximum thermal-mechanical performance, while reducing fuel consumption and emissions is disclosed. Said engine comprises of a hollow rotor (1) featuring internal closed curve epicyclic gears (2), driven by a planetary gear train, rotatable outer casing (10) encompassing the rotor, wherein a combustion chamber is formed in the space between the inside of the casing and the top surface of the rotor, and roller frame with rollers (14) configured to roll through respective path / groove provided on the inside of the side covers.

Description

RING GEARS - INTERNAL COMBUSTION ENGINETECHNICAL FIELD

[0001] The present invention, in general, relates to rotary engines. Particularly, the invention relates to an internal combustion engine, wherein cold air or water spray is introduced into the combustion chamber after achieving desired rpm, to mix with the excess hot air, therein causing expansion, and hence generating more power and maximum thermalmechanical performance, alongside lower emissions.BACKGROUND ART

[0002] Rotary engine is a form of internal combustion engine widely used in aviation engineering and automobiles. It has certain advantages over other reciprocating internal combustion engines such as fewer moving parts, better reliability, less manufacturing cost, and less vibration. Among the rotary engines developed across the world, the Wankel engine is the most popular and widely used for industrial applications. However, the Wankel engine suffers from certain problems such as excessive exhaust emission, leakage at the side seals, excessive wear, and high fuel consumption.

[0003] Different types of rotary engines are known in the state-of-the-art literature. For example, US Pat No. 3918415 teaches a rotary internal combustion engine comprising of an elliptical cylinder, four pistonelements operatively associated with each other to form a rotor in the shape of a regular quadrangle having angles which form a rhombus with sides of substantially equal length, said elliptical cylinder being concentric with a rotating shaft disposed in the centre of said regular quadrangle, the sides of said piston elements and the sides of the elliptical cylinder defining a plurality of chambers there between which extend between the respective vertices of the angles forming the regular quadrangle, and rod means for securing the centre portion of the piston elements to the rotating shaft.

[0004] CN104405447A teaches a multi-angle rotor fluid mechanism, including a triangular rotor. The triangle rotor is arranged in a double arc cylindrical cavity, and a fluid entrance and a fluid exit are arranged on the double arc cylindrical cavity and the end sealing bodies of the double arc cylindrical cavity. However, the central spur gear is designed to be stationary, wherein the circular ring gear is configured to eccentrically rotate around said central spur gear. It further means implies the centre shaft is eccentric, which causes vibration when the engine is in operation.

[0005] Further, WO9932781A1 teaches an internal combustion engine includes a fuel system having the capability of injecting a fuel and air mixture, or air alone, for providing a secondary air charge directly into the combustion chamber after combustion of a primary air and fuel charge has begun. US Pat No. 7513222B2 discloses a combustion-steam enginewherein injection of water into the combustion chamber is performed during the fuel combustion cycle, wherein said process is controlled based on sensor input, such as temperature, extinguishment and pollution level input.

[0006] WO2017179032A1 discloses a method of direct air injection for internal combustion engines wherein as one aspect, once the air-fuel mixture is ignited inside the cylinder, fresh air is injected before the flame extinguishes, in order to keep it burning for a longer period of time to achieve the total combustion of the hydrocarbons obtaining the maximum thermal-mechanical performance. US2004177837A1 teaches a cold air super-charged internal combustion engine, working cycle and method, wherein during compression process, dense, cooled supercharging air charge is injected, adding density and turbulence above that of conventional engines with low "effective" compression ratio for this portion of air charge also.

[0007] From the foregoing, it becomes apparent that there is a need for an internal combustion engine that is capable of achieving improved fuel consumption, cleaner emissions, and delivers high thermal, volumetric, and mechanical efficiency.

[0008] The present invention discloses an internal combustion engine wherein cold air or water spray is introduced into the combustion chamber to mix with the excess hot air, therein causing further expansion, andhence generating more power and maximum thermal-mechanical performance, alongside lower emissions.SUMMARY OF THE INVENTION

[0009] It is therefore the primary objective of the present invention to provide an internal combustion engine wherein cold air or water spray is introduced into the combustion chamber after achieving desired rpm, to mix with the excess hot air, therein causing further expansion, and hence generating maximum power and efficiency, alongside lower emissions.

[0010] It is another object of the invention to provide an internal combustion engine built with less number of constituent parts.

[0011] It is yet another object of the invention to provide an internal combustion engine that generates maximum continuous rotation [275° to 4850°] to the casing and output shaft due to the work generated by the combustion stroke.

[0012] It is a further object of the invention to improve the power delivery of an internal combustion engine.

[0013] It is yet another object of the invention to provide an internal combustion engine that produces less wear and tear during operation as the casing and rotor rotates in the same direction.

[0014] It is a further object of the invention to keep the temperature of gas exhaust to less than 100° and thereby improve the internal combustion engine’s efficiency.

[0015] It is yet another object of the invention to reduce the fuel consumption of the internal combustion engine.

[0016] It is a further object of the invention to achieve long-term combustion process by increasing the rotation of the casing with augmented combustion pressure.

[0017] It is yet another object of the invention to provide an internal combustion engine that produce very less vibration and minimal wear and tear.

[0018] It is a further object of the invention to provide an internal combustion engine that has high thermal, volumetric, and mechanical as well as fuel efficiency.

[0019] It is yet another object of the invention to provide an internal combustion engine that has applications in automotive sector, electric generation, and compressed air systems [CAS].

[0020] Accordingly, the present invention proposes an internal combustion engine, characterized in that: post initiation of the combustion stroke, cool air or water spray isintroduced into the combustion chamber to mix with the residual hot gases present in the chamber, wherein said residual hot gases cause the expansion of said injected cold air or generation of steam, which in turn generates additional power output, lower emissions and improved fuel efficiency, said engine comprising of:• hollow rotor featuring internal epicyclic gear, wherein a planetary gear is so disposed to mesh with said internal teeth of the rotor, wherein said planetary gear is configured to mesh with a second planetary gear positioned between said first planetary gear and a third planetary gear, wherein said second planetary gear meshes with said third planetary gear to form a gear train, wherein the third planetary gear is further configured to mesh with a static spur gear fixed at the centre;• two further planetary gears positioned in-line the gear train, but at the opposite side of the static spur gear, wherein the outermost gear is positioned to mesh with the epicyclic gear of the rotor, whereas the inner planetary gear is configured to mesh with the outer gear;• rotatable outer casing encompassing the rotor, wherein a combustion chamber is formed in the space between the inside of the casing and the top surface of the rotor, wherein circular covers are fixed to either side of said casingrespectively to constitute an air-tight closed chamber;• recess provided along the edges of the rotor on both sides, adjacent to the epicyclic gears, to accommodate roller frames, wherein at the centre of the respective edges of said roller frames are provided with a depression to receive a roller; and• rollers fixed at 60° wherein said rollers are configured to roll through respective path / groove provided on the inside of the side covers, wherein said movement of the rollers in the groove helps the rotor to maintain its rotation along a desired eccentric path that keeps it stable.DESCRIPTION OF ACCOMPANYING FIGURES

[0021] FIG.1 shows the schematic diagram of the internal combustion engine.

[0022] FIG.2 illustrates the X-Y coordinates of the closed curve epicyclic gear shape.

[0023] FIG.3 depicts the exploded view.

[0024] FIG.4 shows the X-Y coordinates of the casing geometry.

[0025] FIG.5 illustrates the shape of the groove.DETAILED DESCRIPTION OF EMBODIMENTS

[0026] The preferred embodiments of the present invention will now be explained with reference to the accompanying drawings. It should be understood however that the disclosed embodiments are merely exemplary of the invention, which may be embodied in various forms. The following description and drawings are not to be construed as limiting the invention and numerous specific details are described to provide a thorough understanding of the present invention, as the basis for the claims and as a basis for teaching one skilled in the art how to make and / or use the invention. However, in certain instances, well-known or conventional details are not described in order not to unnecessarily obscure the present invention in detail.

[0027] The preferred embodiment of the present invention discloses an internal combustion engine wherein cold air or water spray is introduced into the combustion chamber to mix with the excess hot air, to cause further expansion, and hence generate more power and maximum thermal-mechanical performance, while reducing fuel consumption and emissions. Specifically, after combustion at about 275° (or 250°) rotation of the casing, cold air is injected into the combustion chamber, wherein said cold air mixes with the excess hot air present, causing expansion, therein creating more power and efficiency, and more rotations of the shaft, while reducing emissions.

[0028] Referring to FIG.1, the internal combustion engine comprises of a hollow rotor (1 ) featuring an internal closed curve epicyclic gear (2), wherein a planetary gear (3) is so disposed to mesh with said internal teeth of the rotor, wherein said planetary gear is configured to mesh with a second planetary gear (4) positioned between said first planetary gear and a third planetary gear (5), wherein said second planetary gear meshes with said third planetary gear to form a gear train, wherein the third planetary gear is further configured to mesh with a static spur gear (6) fixed at the centre. The X-Y coordinates of the closed curve epicyclic gear shape (19), as shown in FIG.2, is enclosed in Annexure 1. As an aspect of the present invention, the angle at the geometric centre of the closed curve epicyclic gear in the X-Y direction is between 40° - 59°.

[0029] The distance to the closed curve epicyclic gear along the X and Y axes from the geometrical centre of said curve is different. Further, the distance from the static central spur gear to the point of meshing of planetary gears on the closed curve epicyclic gear along the horizontal axis on the rotor is equal. Referring to FIG.1, two further planetary gears (7) are positioned in-line the gear train, but at the opposite side of the static spur gear, wherein the outermost gear is positioned to mesh with the closed curve epicyclic gear of the rotor, whereas the inner planetary gear is configured to mesh with the outer gear. As the area near the comers of the closed curve epicyclic gear is less, owing to less number of teeth, the velocity of the planetary gears decrease. Hence, maintaining a similargear train on the other side of the spur gear would result in the rotor being jammed owing to the difference in angular velocities on either sides of said spur gear. FIG.3 shows the exploded view of the system.

[0030] The planetary gears are configured to turn on their respective axes, wherein the gear shaft (8) of the planetary gears is fixed to the rotor side covers on both sides by means of respective bearings. The centre static spur gear is mounted on a shaft (9), wherein one end of said shaft is disposed such that it extends out to the output side through an opening provided on one side of the rotatable casing (10), wherein said shaft is rotatable by means of bearings. The planetary gear shafts are fixed on the side covers of the rotor by means of bearings.

[0031] When the rotor turns, the static spur gear causes the rotor to trace an eccentric path. Specifically, the outermost planetary spur gears of the gear train simultaneously mesh with the closed curve epicyclic gear of the rotor, and the innermost spur gear of the gear train meshes with the static central spur gear, wherein as the rotor turns, it follows an eccentric path around the centre spur gear. As the rotor rotates, the distance from the static central spur gear to the point of meshing of planetary gears on the closed curve epicyclic gear on the rotor remains equal.

[0032] As illustrated in FIG.1, the rotor is encompassed inside the outer rotatable casing (10), wherein a combustion chamber is formed in thespace between the inside of said casing and the top surface of the rotor. The X-Y coordinates of the casing geometry, as shown in FIG.4, is enclosed in Annexure 2. The top surface of the rotor, on the three sides, features a recess (11), which enhances the volume of said combustion chamber. The comers of the rotor are at 60°. Circular side covers are fixed to either side of said casing respectively to constitute an air-tight closed chamber. The distance from the geometric centre along the x-axis to the outer edge or periphery of the casing is 18% lesser than the distance from the geometric centre along the y-axis. That is, the ratio of distances along the minor and major axes should fall between 0.82 and 1 for the smooth rotation of the casing and rotor.

[0033] Further, along the edges of the rotor, adjacent to the closed curve epicyclic gears, is provided a recess to accommodate a roller frame (13), wherein at the centre of the respective edges of said frame is provided with a depression to receive a roller. The rollers (14) are fixed in triangle formation at 60°. A complementing roller frame with roller arrangement is provided on the opposite side of the rotor as well. As the rotor rotates, said rollers are configured to roll through respective path / groove (15) provided on the inside of the side covers, wherein said movement of the rollers in the groove helps the rotor to maintain its rotation along a desired eccentric path that keeps it stable. The shape of the groove (18) may vary with the overall size of the rotor. FIG.5 illustrates the shape of the grooves. The X- Y coordinates of the shape of the groove or the roller path geometry, asshown in FIG.5, is enclosed in Annexure 3. Corner seals at 60° of rotor, and side seals are provided to prevent any kind of gas leakage from the combustion chamber during the combustion process. The thickness of the rotor is same in all directions, which helps to keep the overall weight of the rotor less. Said design also aids in cooling the rotor during operation, and helps to easily apply lubrication, whenever required.

[0034] According to the preferred embodiment of the present invention, the outer casing encompassing the rotor is provided, wherein the casing as a whole is configured to rotate along with the rotor, but at different angular velocities. When the rotor and the casing rotates, the corners of the rotor remains in constant contact with the inside of said casing. By varying the gear ratio between the spur gears and the epicyclic rotor gear, said relative angular velocity may be varied, and is included within the scope of the present invention. Inlet and exhaust ports (16, 17) are provided on the casing for the intake and exhaust of gases respectively. The casing further features a provision for installing one or more spark plugs to aid the combustion of the fuel in the combustion chamber. In one embodiment, the engine features one spark plug. The engine is mounted on a stand (24), encompassed inside stationary front and back covers (21 , 22).Working

[0035] The internal combustion engine is started using self-motor, wherein the gear mounted on said motor shaft is meshed with a starting gear (20) mounted on the periphery of the rotatable outer casing, causing said casing to rotate. The rotation of the casing induces rotation on the planetary gears, which in turn causes the rotor to rotate as the planetary gear train transfers the rotational torque to the closed curve epicyclic gears of the rotor. In the preferred embodiment of the present invention, the closed curve epicyclic gears of the rotor features 360 teeth, and the static central spur gear has 10 teeth, wherein the planetary gear features 60 teeth. As a result, when the casing rotates 12 times or turns by 4320°, the rotor turns by 120°. A closed curve increases the number of teeth on the epicyclic gear and decreases the number of teeth on the stationary gear, which results in reduced fuel consumption. The gear ratio may be varied as per requirement, and is included within the scope of the present invention.

[0036] The relative angular velocities between the rotor and casing creates vacuum, which causes air to be sucked into the suction chamber through the inlet. Further, the casing rotates another 12 times, wherein the rotor turns by 120° to constitute the compression stroke, wherein fuel is injected through fuel injection port (12) into the rotor cavity at the end of said compression stroke, wherein the compressed fuel is combusted by asparkplug as the rotor turns by another 10°. The next 120° rotation of the rotor consists of the combustion stroke, wherein the casing rotates by a further 4320°. As the casing rotates by 520° by the work done by said combustion of fuel, cool air or water spray is introduced into the combustion chamber through an injection port (23) to mix with the residual hot gases present in the chamber post combustion, wherein said residual hot gases cause the expansion of said injected cold air or generation of steam, which in turn generates additional power output to cause the casing to rotate by 4320°. Specifically, as the pressure drops inside combustion chamber, cool air or water spray is introduced into said chamber to coincide with said pressure drop to mix with the residual hot gases present in the chamber post combustion.

[0037] In one embodiment, water spray is injected at the beginning of the combustion stroke. The pressure of the injected cool air may be varied as per requirement. Said injection of cool air or water spray into the combustion chamber reduces the temperature of exhaust gases below 100°C. The angle in which cold air or water spray is injected as well as the volume of air introduced depends upon the cubic capacity of the engine as well as the calorific value of fuel. Exhaust stroke follows, completing the cycle. The additional work produced improves the thermal-mechanical performance of the engine, therein reducing the fuel consumption and producing lower emissions.

[0038] In another embodiment, small type engine having 270° suction, 270° suction compression, 270° expansion, and 270° exhaust is defined by varying the gear ratio, wherein the the closed curve epicyclic gear has 45 teeth, whereas the stationary central spur gear features 20 teeth. In yet another embodiment, a small-medium engine, wherein 720° suction, 720° suction compression, 720° expansion, and 720° exhaust is defined, by varying the gear ratio, wherein the closed curve epicyclic gear has 180 teeth, whereas the stationary central spur gear features 30 teeth. A further embodiment details a medium type engine with 1080° suction, 1080° suction compression, 1080° expansion, and 1080° exhaust may be designed, wherein the closed curve epicyclic gear of the rotor has 180 teeth, whereas the stationary central spur gear features 20 teeth. Yet another embodiment discloses a medium-large engine having 2180° suction, 2180° compression, 2180° expansion, and 2180° exhaust, wherein the closed curve epicyclic gear has 240 teeth, whereas the stationary central spur gear features 10 teeth.

Claims

1. CLAIMS1 . An internal combustion engine, characterized by: less number of constituent parts, wherein post initiation of the combustion stroke, cool air or water spray is introduced into the combustion chamber to mix with the residual hot gases present in the chamber, wherein said residual hot gases cause the expansion of said injected cold air or generation of steam, which in turn generates additional power output, lower emissions, and lower fuel consumption, said engine comprising of:• hollow rotor (1 ) featuring internal closed curve epicyclic gears (2), wherein a planetary gear (3) is so disposed to mesh with said internal teeth of the rotor, wherein said planetary gear is configured to mesh with a second planetary gear (4) positioned between said first planetary gear and a third planetary gear, wherein said second planetary gear meshes with said third planetary gear (5) to form a gear train, wherein the third planetary gear is further configured to mesh with a static spur gear fixed at the centre;• two further planetary gears positioned in-line the gear train, but at the opposite side of the static spur gear (6), wherein the outermost gear is positioned to mesh with the epicyclic gear of the rotor, whereas the inner planetary gear isconfigured to mesh with the outer gear;• rotatable outer casing (10) encompassing the rotor, wherein a combustion chamber is formed in the space between the inside of the casing and the top surface of the rotor, wherein circular covers are fixed to either side of said casing respectively to constitute an air-tight closed chamber;• recess provided along the edges of the rotor on both sides, adjacent to the closed curve epicyclic gears, to accommodate respective roller frames (13), wherein at the centre of the respective edges of said roller frames are provided with a depression to receive a roller; and• rollers (14) fixed in triangle formation at 60° wherein said rollers are configured to roll through respective path / groove (15) provided on the inside of the side covers, wherein said movement of the rollers in the groove helps the rotor to maintain its rotation along a desired eccentric path that keeps it stable.

2. The internal combustion engine as claimed in claim 1 , wherein the further two planetary gears positioned in-line the gear train, but at the opposite side of the static spur gear, is meant to balance the difference in angular velocities on either side of said spur gear.

3. The internal combustion engine as claimed in claim 1 , wherein the the gear shaft (8) of the planetary gears are fixed to the rotor side covers on both sides by means of respective bearings.

4. The internal combustion engine as claimed in claim 1 , wherein the centre static spur gear is mounted on a shaft (9), wherein one end of said shaft extends out to the output side through an opening provided on one side of the outer casing, wherein said shaft is rotatable by means of bearings.

5. The internal combustion engine as claimed in claim 1 , wherein the top surface of the rotor, on the three sides, features a recess, to enhance the volume of the combustion chamber, wherein the comers of the rotor are at 60°.

6. The internal combustion engine as claimed in claim 1 , wherein the distance from the static central spur gear to the point of meshing of planetary gears on the closed curve epicyclic gears on the rotor is equal.

7. The internal combustion engine as claimed in claim 1 , wherein the thickness of the rotor is same in all directions, wherein the closed curve epicyclic gears of the rotor features 360 teeth, and the static central spur gear has ten teeth, wherein the planetary gear features60 teeth.

8. The internal combustion engine as claimed in claim 1 , wherein the distance to the closed curve epicyclic gear along the X and Y axes from the geometrical centre of said curve are different.

9. The internal combustion engine as claimed in claim 1 , wherein the distance from the geometric centre along the x-axis to the outer edge or periphery of the casing is 18% lesser than the distance from the geometric centre along the y-axis.

10. The internal combustion engine as claimed in claim 1 , wherein the casing is configured to rotate along with the rotor, but at different angular velocities, wherein the comers of the rotor remains in constant contact with the inside of said casing.

11. The internal combustion engine as claimed in claim 1 , wherein the angle at the geometric centre of the closed curve epicyclic gear in the X-Y direction is between 40° - 59°.

12. The internal combustion engine as claimed in claim 1 , wherein, for 270° suction, 270° suction compression, 270° expansion, and 270° exhaust, the gear ratio is varied, wherein the closed curve epicyclic gears of the rotor features 45 teeth, and the static central spur gear has 20 teeth.

13. The internal combustion engine as claimed in claim 1 , wherein, for720° suction, 720° suction compression, 720° expansion, and 720°exhaust, the gear ratio is varied, wherein the closed curve epicyclic gears of the rotor features 180 teeth, and the static central spur gear has 30 teeth.

14. The internal combustion engine as claimed in claim 1 , wherein, for 1080° suction, 1080° suction compression, 1080° expansion, and 1080° exhaust, the gear ratio is varied, wherein the closed curve epicyclic gears of the rotor features 180 teeth, and the static central spur gear has 10 teeth.

15. The internal combustion engine as claimed in claim 1 , wherein, for 2180° suction, 2180° suction compression, 2180° expansion, and 2180° exhaust, the gear ratio is varied, wherein the closed curve epicyclic gears of the rotor features 240 teeth, and the static central spur gear has 10 teeth.

16. A method of operation of the internal combustion engine to achieve long-term combustion process by increasing the rotation of the casing with augmented combustion pressure, said method comprising the steps of:• starting the internal combustion engine using a self-motor, wherein the gear mounted on the motor shaft is meshed with a starting gear (20) mounted on the periphery of the outer casing, causing said casing to rotate;• causing the planetary gears to rotate by the rotation of thecasing, wherein it causes the rotor to rotate as the planetary gear train transfers the rotational torque to the closed curve epicyclic gears of the rotor;• causing air to be sucked into the suction chamber through the inlet owing to the vacuum created by the relative angular velocities between the rotor and casing, wherein as the casing rotates 12 times or turns by 4320°, the rotor turns by 120°;• performing the compression stroke, wherein as the casing rotates further 12 times, the rotor turns by 120°, wherein fuel is injected into the rotor cavity at the end of said compression stroke, wherein the compressed fuel is combusted by the sparkplug as the rotor turns by another 10°;• performing the combustion stroke, wherein the rotor wherein the casing rotates by a further 4320°, and rotor by 120°, wherein as the casing rotates by 520° by the work done by said combustion of fuel, cool air or water spray is introduced into the combustion chamber through injection port (23) to mix with the residual hot gases present in the chamber post combustion, wherein said residual hot gases cause the expansion of said injected cold air or generation of steam, which in turn generates additional power output to cause the casing to rotate by 4320°; andperforming the exhaust stroke, wherein the temperature of exhaust gases is below 100°C.

17. The method as claimed in claim 16, wherein the water spray is injected at the beginning of the combustion stroke.

18. The method as claimed in claim 16, wherein cool air or water spray is introduced into the combustion chamber to mix with the residual hot gases present in the chamber post combustion to coincide with pressure drop inside said combustion chamber.

19. The method as claimed in claim 16, wherein the angle in which cold air or water spray is injected as well as the volume of air introduced depends upon the cubic capacity of the engine as well as the calorific value of fuel.

Images