KR20060074021A - Non-crank piston engine - Google Patents

Abstract

The present invention relates to an internal combustion engine. In current internal combustion engines, crank piston engines are the mainstream. Although the piston is a reciprocating structure, the gas is easy to seal. However, the crank piston engine has a defect that the piston is in close contact with the cylinder wall because the piston must reciprocate by the crank and the cylinder wall wears elliptically. In addition, the conventional piston engine has at least two or more poppet valves are used, which has the disadvantage that the cylinder head becomes complicated.

The present invention is configured to solve this problem. In the present invention, a cam device is formed by a cam device having an eight-shaped groove formed in a disk larger than the diameter of the piston, and the piston is reciprocated. The cylinders are radially arranged around the disk cam. In more detail, a cam follower roller is inserted into an eight-shaped groove formed on a slope, and a piston rod is directly connected to the follower. Therefore, when the disc rotates, the cam follower reciprocates along the groove of the disc, so that the piston reciprocates. Thus, when the piston reciprocates by the cam, unlike the reciprocation by the crank, the piston does not apply force to the cylinder wall surface, thereby preventing the cylinder wall surface from being worn in an elliptical shape, and the frictional resistance is also greatly reduced.

In addition, the present invention improves the intake and exhaust device more concisely by adding a check valve mainly used in the piping system to the intake and exhaust device. In the present invention, a check valve is used as an auxiliary valve in a part for controlling the intake and exhaust air, and a poppet valve (or rotary valve) that is conventionally used is provided in the sealing field. It is configured to reduce to / 2.

Internal combustion engine, crank piston engine

Description

Internal combustion engine {Non-Crank Piston Engine}

1 is a three-dimensional view showing the main part of the present invention,

2 and 3 is a detailed view of the cam follower in the present invention,

4, 5 and 6 is a summary diagram showing an overview of the present invention;

7 is an external view of a spiral bevel gear and a helical gear,

8 is a diagram for explaining the operation of the cam follower of the present invention;

9 is a graph for explaining the stroke of the present invention;

10 and 11 is a summary for explaining the intake and exhaust device of the present invention,

12 is a detailed view showing a check valve of the present invention,

13 is a detailed view showing the exhaust fan of the present invention,

14 is a detailed view showing an intake and exhaust rotary valve of the present invention;

15 is a rotor outline view of a rotary valve of the present invention;

16 is a schematic diagram of a cam device for explaining the present invention.

<Simple description of symbols for main parts of the drawings>

10: Power Cam

11: Groove grooved on the power cam

11a: Peak slope of cam slope

11b: point at which the radius of curvature changes in the slope of the cam

12: piston

13: Piston Rod

14: Lock Nut to Secure Piston Rod to Cam Follower

15: Guide Plate of Cam Follower

16: Guide slot of cam follower

17: Power Cam Shaft

18: cylinder

19: Cylinder Head

20: Cam Follower

21: Cam Follower Guide Bearing

22: Roller Main Axis of Cam Follower

23: Roller Axis Base Plate of Cam Follower

23a: base plate center hole of the cam follower

23b: Roller Axis of Cam Follower

24: Cam Follower Roller

25: Roller Upper-Plate of Cam Follower

26: Cam Follower Main Axis Bushing Bearing

26a: Stress Absorbing Curved-Surface

26b: spindle bushing bearing hub (fitting into hole 23a)

30: Check Valve Body

31: check valve for intake control

32: check valve for exhaust control

33: Disk Seat of Check Valve

34: Swing Disk

35: Component for fixing the disc of the check valve (oil-free bearing material)

36: Pin for Fixing Disc of Check Valve

37: oil-free bushing bearing portion to which the pin is fitted

40: Exhaust Fan

41: Flange in which the exhaust fan is mounted to the exhaust port

42: Exhaust Fan and Inertia Wheel (Flywheel)

43: Wings that set the shaft of the exhaust fan

44: exhaust fan shaft

45: Journal fitted in hub bearing of exhaust fan

46: square hole for fixing the axial blades of the exhaust fan

50: Intake / Exhaust Rotary Valve

51: Rotary Valve Body

52: Ball

52a: Ball Valve Lower Seat

52b: Upper Valve Seat

53: Valve Stem

54: Valve Bonnet

55: Bonnet Setting Screw

56/58: Rotary Valve Inlet / Outlet

57: Rotary Valve Fluid Passage

59 / 59a / 59b: Valve Oil Passageways

61: Intake Port

62: exhaust port

63: Poppet Valve for Sealing

64: Combustion Chamber

TDC: Top Dead Center of Piston

BDC: Bottom Dead Center of the Piston

The present invention relates to a means for the reciprocating motion of a piston and an intake and exhaust device in an internal combustion engine. In the conventional crank piston engine, the piston is reciprocated by the crank, so that the piston exerts a force on the cylinder wall, and thus the cylinder wall is worn in an oval shape. In addition, the conventional engine has a defect that the cylinder head is complicated by having at least one intake valve and one exhaust valve.

On the other hand, the cam device in the mechanical device is used when converting the rotational motion to linear motion. In addition, check valves commonly used in piping systems are used to prevent backflow of fluid.

The present invention is configured to reciprocate the piston by the disc cam using the operating principle of the cam device. In more detail, an eight-way cam groove is formed on the disk, or a circular groove is eccentric with respect to the axis of the disk, and the groove of the cam follower is formed in the groove. A roller is fitted, and a piston rod is connected to the follower so that the piston reciprocates when the disc rotates. In the present invention, the cylinders are arranged radially about the cam thus configured. In addition, the present invention has a simpler configuration of the cylinder head by adding a check valve to the intake and exhaust device, a piston engine that eliminates the above-mentioned defects of the conventional engine.

In a crank piston engine, the piston is controlled by the crank and must move in motion corresponding to the curve whose peak point is higher than the sine curve in mathematics. Therefore, a power stroke generating power and an exhaust stroke exhausting combustion gas are constant. However, in the present invention, the piston reciprocates by the groove slope of the cam, so that the expansion stroke can be made longer or shorter than the exhaust stroke information. That is, the piston may be operated more slowly in the expansion process than in the exhaust process. In other words, more power can be obtained from high-pressure combustion gases. The reason for this is as follows.

The definition of an object's temperature is thermodynamically defined as the average velocity of the molecules in the object. That is, the temperature is defined by the formula <Mean molecular kinetic energy of the object> = 3/2 k T, 1/2 mv ² _rms = 3/2 kT, k T = 1/3 mv ² rms where k is Boltzmann's constant (1.3805 * 10 ^-23 J / K), T is the absolute temperature, m is the mass of the molecule, v _rms is the mean square velocity of the molecule (Root-Mean-Square = 1 / N ∑v ² ). Even with a system of identical molecules, not all particles move at the same speed. Some particles move fast and some move very slowly. However, their average speed (rms) follows the formula above.

When fuel (hydrocarbon) is supplied to the cylinder and burned, carbon dioxide (CO ₂ ) and water vapor (H ₂ O) are generated. When combustion has just occurred, the temperature of the combustion gases is high, above about 2000 ° C. (2273 ° K). At this temperature, the mean kinetic velocity of carbon dioxide gas with molecular weight 44 and mass 44 / (6.022x10 ²³ ) g is (k T 3 / m) ^1/2 = (1.3805 x 2273 x 3 x 6.022 / 44 x 1000) ^{1 / 2} = 1135 m / s (where 6.022x10 ²³ is Avogadro's number) and the combustion gas temperature at the completion of the expansion process is about 300 ° C, so the average velocity is calculated to be 573 m / s. The fluctuations in the momentum mv appear as a force that pushes the piston as the combustion gas moving at random at such an average movement speed hits and bounces off the piston wall. If the piston retracts faster than the combustion gas, no power is produced because the combustion gas does not affect the piston wall. In other words, the slower the piston moves (the higher the relative speed), the more power is produced from the combustion gases. However, on the other hand, the heat energy escapes out through the cylinder wall in proportion to the time the combustion gas stays in the cylinder. Therefore, the longer the expansion process (the slower the piston speed), the greater the heat loss. Therefore, an appropriate piston reverse speed can be calculated which maximizes the engine's thermal efficiency. The present invention is a structure that can set the time curve of the expansion process and compression process to maximize the thermal efficiency by setting the curve of the cam appropriately.

The present invention is configured to reduce the poppet valve, which is an existing intake and exhaust valve, by adding two check valves to the intake and exhaust device to 1/2, and add an exhaust fan to discharge the combustion gas more quickly. In a conventional engine, there is a problem that the exhaust valve is overheated. In the present invention, however, one poppet valve performs both sealing functions of the intake valve and the exhaust valve, so that the valve is automatically cooled by the intake air. In the present invention, a ball valve type rotary valve may be used instead of the poppet valve for sealing the gas.

In machinery, cams are generally used to convert circular motions into linear motions. In a piston engine, it is also possible to convert the reciprocating motion of the piston to a cam device, one of which comes to mind easily, as shown in Fig. 16, which forms a groove in the cylinder and reciprocates along the groove. You can think of connecting the piston to). Another means is to form an eight-shaped cam groove (Cam Groove) formed in the inertia wheel of the disk as shown in Fig. 1, the roller is fitted into the groove to the reciprocating follower You can think of connecting. The present invention is configured so that the piston reciprocates by a disk cam device.

1 is a three-dimensional view showing the main part of the present invention. As shown, the disk 10, which also serves as an inertia wheel (Flywheel), has an eight-shaped groove (Cam Groove) having a slope. This disc will hereinafter be referred to as a power cam. The rollers 24 of the cam follower shown in FIGS. 2 and 3 are fitted into the eight-shaped grooves 11 formed in the power cam. The cam follower 20 is equipped with a guide bearing, which is fitted into a guide slot 16 formed in the guide plate 15. Accordingly, when the power cam 10 rotates, the cam follower 20 reciprocates only in both directions. In the present invention, the groove 11 of the power cam is not an eight-shaped curved shape, but an inclined groove having an ellipse (similar to the cam curve of the cylinder head valve) that is eccentric with respect to the power camshaft. It may be.

3 shows each part of the cam follower in three dimensions. One side of the body of the cam follower 20 is provided with the guide bearing 21, and the other side is provided with a roller main axis journal. As mentioned above, four rollers 24 are rolled on the curved surface of the eight-shaped groove 11 of the power cam. The four rollers shown in FIG. Plate) to the four roller shafts 23b fixed to the plate, and the hubs 26b and hub of the main shaft bushing bearing 26 (bulging) are inserted into the central large hole 23a. ), And fixed by covering a peanut-shaped roller shaft support plate (Upper Plate), and then mounted on the cam follower main shaft 22 journal, the shape shown in FIG.

As shown in FIG. 1, the follower 20 is directly connected with a piston rod 13 and fixed with a lock nut 14. Accordingly, when the power cam 10 rotates, the roller 24 of the cam follower 20 moves along the groove 11 inclined in an eight shape, so that the piston 12 reciprocates. do. In other words, when the piston 12 reciprocates, the power cam rotates. Thus, in the present invention, the piston reciprocates by the power cam without reciprocating by the crank. Therefore, the piston does not exert a force on the cylinder wall, thereby eliminating the defect that the cylinder wears elliptically, and also greatly reduces the frictional resistance generated between the piston and the cylinder wall.

Figure 4 is a summary diagram showing the outline of the present invention when the present invention is a four-cylinder engine, Figure 5 is a summary diagram illustrating the operation of the present invention. 6 is a summary diagram illustrating a case where eight cylinders are arranged in the present invention. As such, although the present invention is not shown, six cylinders 18 or ten cylinders may be arranged radially. In the present invention, as shown in FIG. 5, when any piston advances the power stroke, the piston 12 facing the piston takes an intake stroke, and the adjacent piston compresses the compression stroke. The piston facing each other performs the exhaust stroke. That is, the pistons facing each other always reciprocate in a direction close to or far from each other. Therefore, in the present invention, the power cam is symmetrical, the moment of inertia is completely balanced, and the opposite piston 12 always reciprocates in opposite directions, unlike the crank piston engine. You will have a circular motion. In addition, the present invention also has the advantage that it can be cooled by air cooling because all of the outer wall of the cylinder is exposed to the outside.

FIG. 7 shows the appearance of a spiral bevel gear and a helical screw gear that are commonly used when gearing two axes orthogonal to each other in a mechanical device. By such gears, the cylinder head 19 intake and exhaust valve of the present invention can be easily driven. Therefore, the driving device and means of the intake and exhaust valves of the cylinder head are already known in the art and do not belong to the scope of the present invention, and thus description thereof will be omitted.

FIG. 8 is a diagram showing a state in which the roller 24 of the follower 20 passes through the peak point 11a of the curved surface on the groove 11 of the power cam 10. It is at the beginning of an expansion stroke or when a compression stroke or exhaust stroke is completed. Among these, when the piston is located at the start of the expansion stroke, that is, when the fuel is exploded and burned in the combustion chamber after the compression process is completed, the pressure inside the cylinder is about 65 kgf / cm ^{2 at} a high pressure. Thus, the piston receives a very large force corresponding thereto, so that the two inner rollers 24 of the follower 20 located on the top 11a of the power cam must withstand this force, and any damage to the curved surface of the cam ) Should not be given.

In the present invention, in order to solve this problem, the shape of the main shaft bushing bearing 26 in the roller device is made in a bulging form. The stress-absorbing curved surface 26a located inside thereof and the curved surface near the top of the cam have the same radius of curvature R as shown. That is, when the roller is located near the top 11a, both curved surfaces 11a and 26a abut. Therefore, although a very large force is applied to the roller device rolling near the top, the roller device can be lowered from the top by sliding on the oil film of the curved surface 11a of the cam without damaging the curved surface of the cam by the stress absorbing curved surface 26a. When the roller device is halfway down the top of the cam (when the camshaft rotates the angle θ and drops by the distance H), the combustion gas in the cylinder expands considerably and the pressure is greatly reduced. Therefore, the force applied to the piston is also weakened, and thus the force applied to the roller device is also reduced. Therefore, even if the radius of curvature R is increased to be larger than or equal to the center of the cam (11b, the point where the radius of curvature changes) (that is, the stress absorbing curved surface 26a does not contact the curved surface of the cam and only the rollers 24 The surface of the cam is not damaged even if it touches the surface. In the present invention, the larger the radius of curvature of the top 11a in the cam curve, the lower the state of contact with both the stress absorbing curved surface 26a and the curved surface of the cam. In other words, the radius of curvature of the normal can be increased so that the stress-absorbing curved surface 26a is in contact with the curved surface of the cam all the way down to the middle of the normal.

 In the crank engine, when the crankshaft rotates once, the piston reciprocates once, and in the present invention (when the groove of the cam becomes eight-shaped), the piston reciprocates once when the camshaft 17 rotates 1/2. . FIG. 9 is a graph of the rotational angle of the X-axis with reference to the crankshaft for convenience, showing (for example) both the motion of the piston and the piston movement in the present invention in a conventional crank piston engine. In a crank engine, the piston is controlled by the crank, so that the expansion stroke and the compression stroke behave in the same direction only. However, in the present invention, the cam curve can be appropriately set so that the efficiency of the engine can be optimal. That is, as shown, it is possible to increase the expansion process and reduce the compression process. The piston of the present invention does not operate only on the curve of the graph shown. This is an example. In other words, the expansion process may be set smaller than the compression row information.

10 is a summary view showing an intake and exhaust device of the present invention. In the combustion chamber of the conventional cylinder head, there must be at least one intake and exhaust valve each. However, in the present invention, the intake and exhaust check valves 31 and 32 shown in detail in FIG. 12 are installed in the inlet 61 and the exhaust port 62, respectively, and one poppet valve is used. The poppet valve 63 has the same structure as a conventional intake valve, and its main role is to seal the gas. The main purpose of the check valve is not to seal the gas but to control the flow of the intake and exhaust air. As shown in Fig. 12, the check valve has a disk 34 made of a very thin stainless steel plate, fitted with a half-moon shaped part 35 made of a non-lubricated bushing bearing material, and fixed with a pin 36 as shown in the cross section. It becomes the structure that becomes.

In conventional piston engines, the exhaust valve opens (before bottom dead center) before the piston completes the expansion stroke, and then the intake valve opens again just before the piston reaches top dead center, and then closes the exhaust valve. Next, the intake valve closes when the piston passes the bottom dead center. However, in the present invention, the poppet valve 63 is opened just before the piston 12 reaches the bottom dead center in the expansion process as in a conventional engine, but is still open even when the piston reaches the top dead center. This is because intake and exhaust control is automatically performed by the check valve. When the piston 12 passes through the top dead center and retracts, the piston inhales air. At this time, the check valve 32 of the exhaust port 62 is closed and the check valve 31 of the inlet port 61 is opened. (18) is sucked into. Next, the poppet valve 63 is closed when the intake valve is closed in the existing engine. In a conventional engine, the exhaust valve is made of a special material because it must withstand high temperatures. However, since the poppet valve of the present invention is cooled by air which is always sucked, the same material as that of the conventional intake valve is sufficient.

In the present invention, even if the mass of the check valve is very small, the question remains whether the combustion gas can be sufficiently discharged from the cylinder and new air can be sucked by the operation of one poppet valve when the engine is operated at high speed. . This problem is solved as follows. The exhaust fan 40 shown in FIG. 13 is attached to the exhaust port 62 in this invention. The exhaust fan is equipped with a flywheel, and the journal 45 of the T-shaped shaft 44 is inserted into the hub bearing of the fan, and the wing 43 portion of the shaft 44 is formed in the cylinder. It is configured to fit in the square hole 46. This exhaust fan 40 is mounted to the exhaust port 62 in front of the exhaust manifold flange of the engine.

When the exhaust valve is opened in a conventional engine, the combustion gas is discharged at almost sonic speed. The same is true in the present invention. When the combustion gas is discharged at this speed, the exhaust fan of the exhaust port rotates at a high speed. When the piston approaches near top dead center, the speed of the piston is drastically lowered, and the piston can no longer push the combustion gas. However, combustion gases with considerable pressure still remain in the upper combustion chamber of the cylinder. On the other hand, the exhaust fan still maintains the rotational speed when the piston discharges the combustion gas at high speed due to the inertia of the inertia wheel 42. Therefore, the exhaust fan continuously discharges the combustion gas with the energy (rotational power) accumulated in the inertia wheel. Then, when the piston descends past the top dead center, the exhaust valve automatically closes the check valve according to the pressure difference, As it opens, air is sucked into the cylinder.

FIG. 11 is a summary diagram of the intake and exhaust device of the present invention showing the case where the rotary ball valve shown in detail in FIGS. 14 and 15 is used instead of the above-described poppet valve. Normally, the ball valve opens twice when the stem is rotated once. However, the ball valve shown in FIG. 14 is opened once when the stem 53 rotates once. This is because the fluid passage 57 is drilled obliquely with respect to the stem in the ball. The valve body (51) has a flange for mounting it on the upper part, the inside is empty like a cylinder, and the lower part is closed in a hemispherical shape. The side is half open, and the half of the hemisphere that is blocked below is half open. The lower ball seat 52a, which has a side half of the hemisphere drilled in the valve body, is placed on the inner bottom, and the weir ball 52 is inserted. The next half is open in the form of a cone, and the lining of the valve bonnet 54 lining 52b with the ball seat material is fitted and tightened with the bonnet fixing screw 55, as shown in the cross-sectional view. The opening 56 in the shape of a cone in the bonnet determines when the valve opens and closes. That is, reducing the open area 56 reduces the time that the valve is open and increases the time that it is closed. The bonnet has an oblique passage 59a (Lube Oil Passageway) obliquely downward from the top of the stem 53. The ball 52 also has an oblique passage 59b downward from the stem.

Rotating the stem 53 of such a rotary valve opens and closes once per revolution. When the ball valve is closed, it has a characteristic of sealing the fluid by high pressure like a poppet valve.If it is supplied through the oil passages 59, 59a and 59b described above, it operates as a rotary valve that seals the gas in the cylinder well without large frictional resistance. do. In the present invention, such a rotary valve 50 may be installed in place of the conventional poppet valve in the cylinder head as shown in FIG. This rotary valve is the same as when the poppet valve 63 is opened and closed as described above. In this rotary valve, combustion gas and air are exhausted and sucked through the intake and exhaust ports 56 and 58 of the valve and the hole 57 drilled in the ball. Therefore, the valve is always cooled by fresh air, which is freshly inhaled. In this rotary valve, when the hole drilled in the ball is oblique and the ball rotates, the air is sucked in while changing the direction of travel. For example, it is similar to the airflow when shooting an air gun while shaking a hand. Therefore, when the present invention is a gasoline engine, the intake air is sucked in forming a swirl, and as a result, the gasoline particles become finer particles and mix well with the air. This is very helpful for the complete combustion of fuel.

FIG. 15 shows another ball shape and the shape of a cylindrical plug that can be used instead of the ball. Here, the holes drilled in the balls and plugs are bent down. The reason that the shape of the plug is made thinner toward the valve stem, unlike the general plug valve, is that the gas is automatically sealed by the pressure of the combustion chamber. A rotary valve consisting of such a ball and plug has intake air directed down the center of the valve. If the present invention is a diesel engine, such a valve is suitable, which is easier to manufacture.

The present invention has the effect of cooling by air cooling as the engine is driven quietly and the cylinder is radially arranged as the piston reciprocates with a disc shaped cam device.

Claims (4)

In an internal combustion engine composed of a piston, a cam groove is formed on the disk 10, and the top of the groove is formed by the roller 24 of the follower 20 fitted into the groove. A rod of piston is connected to a cam device consisting of a follower 20 with a spindle bushing bearing 26 having a stress absorbing curved surface 26a coinciding with a curve 11a in the vicinity, and a plurality of cylinders ( An internal combustion engine, characterized in that 18) is arranged radially about the cam. In an internal combustion engine composed of a piston, check valves 31 and 32 are provided at the inlet port 61 and the exhaust port 62, respectively, and the poppet valve 63 has a sealing function of the intake valve and the exhaust valve in a conventional engine. And an intake / exhaust device configured to be closed at a time when the intake valve is closed in the conventional engine after the poppet valve is opened at the time when the exhaust valve is opened in the conventional engine. An internal combustion engine composed of a piston, characterized in that an exhaust fan is provided with an inertia wheel (42) and a mounting flange (41), which assists the exhaust port (62) to exhaust the combustion gas. 3. The rotary valve of claim 2, wherein the valve stem 53 opens and closes only once in one rotation instead of the poppet valve 63, and the ball 52 or the plug has a lubricating oil passage 59b. Internal combustion engine characterized by.

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