KR101197307B1 - Crankless engine - Google Patents

Abstract

Embodiment of the present invention relates to a crankless engine, it is possible to reduce the weight and size of the engine without the crank, the connecting rod, the timing chain (belt), and to reduce the vibration of the engine by placing two pistons facing each other From the moment of the explosion stroke of the engine, it is characterized by converting the linear movement of the piston directly into the rotational movement.

Description

Crankless engine {CRANKLESS ENGINE}

The present invention relates to a crankless engine, and more particularly, it is possible to reduce the weight and size of the engine without a crank and connecting rod, and to arrange two pistons facing each other to offset the vibration of the engine, A crankless engine that can significantly improve efficiency.

In general, the engine is a device that converts thermal energy into mechanical work, and is used as a power source for transportation and industrial machinery. In order for the engine to convert thermal energy into mechanical work, a working material is needed. That is, in a gasoline engine, a fuel gas mixed with gasoline and air and a combustion gas generated when the fuel gas is burned are used as working materials. In the diesel engine, a fuel gas mixed with diesel oil and air and a combustion gas generated when the fuel gas is combusted are used as working materials. In addition, steam and steam use water and steam as working materials.

On the other hand, the reciprocating piston engine is formed of a cylinder and a piston, and recently has been widely used in automobiles, compressors, generators, ships, and the like. This reciprocating piston engine is an internal combustion engine that converts the explosion energy of fuel gas into mechanical work of the piston and the crank. That is, the reciprocating piston engine can convert the linear reciprocating motion of the piston into the rotational motion of the crank using the crank and the connecting rod.

However, the conventional reciprocating piston engine has a limitation in reducing the weight of the engine because the weight of the crank and the connecting rod is very heavy, and the outer shape of the crank and the connecting rod is also very large, there is a limit in reducing the appearance of the engine. Therefore, the conventional reciprocating piston engine is very difficult to improve the efficiency and performance of the engine due to the heavy weight and large appearance. In addition, the reciprocating piston engine has a disadvantage that it is difficult to secure the installation space.

In addition, in the conventional reciprocating piston engine, due to the connection structure of the crank, the connecting rod and the piston, it is almost impossible to design and change various performance factors of the engine. For example, the maximum compression pressure, the maximum compression time, the fuel explosion time, the position of the top dead center and the bottom dead center of the piston, the moving speed of the piston, and the like. Therefore, the conventional reciprocating piston engine is a very limited situation that can improve the efficiency and performance of the engine.

In addition, the conventional reciprocating piston engine also has a limitation in changing the opening and closing time, opening and closing time of the intake valve and exhaust valve. Recent reciprocating piston engines adjust some of the operation timings of the intake valve and the exhaust valve according to the driving environment, but the range of adjustment is very narrow. Therefore, there is a limit in optimizing the intake performance and exhaust performance of the reciprocating piston engine according to the driving environment.

In particular, in recent years, the need for an engine with excellent efficiency and performance is increasing due to various reasons such as energy depletion, fuel cost increase, environmental pollution, and various regulations and agreements.

Embodiment of the present invention provides a crankless engine that can significantly reduce the weight and size of the engine, and improve the efficiency and performance of the engine by omitting the crank and the connecting rod.

In addition, an embodiment of the present invention is to provide a crankless engine that can improve the vibration performance of the engine by offsetting the vibration generated when the engine is driven by operating the two pistons facing each other and the two pistons in the opposite direction to provide.

In addition, the embodiment of the present invention adjusts the maximum compression time, maximum compression pressure, opening and closing time and opening time of the valve, the top dead center and bottom dead center height of the piston, and simply adjust the feed speed of the piston, etc., the efficiency and performance of the engine It provides a crankless engine with a guide hole designed to convert linear motion into rotational force from the moment of explosion to maximize the pressure.

According to an embodiment of the present invention, a cylinder having an intake and exhaust portion in which an intake valve and an exhaust valve are disposed is formed in the middle, a first piston provided to reciprocate on one side of the cylinder, and the intake and exhaust portion facing the first piston. A second piston provided on the other side of the cylinder so as to be reciprocated so as to be disposed so as to be reciprocally moved, and an operating space provided between the cylinder and the first piston and the second piston is formed to a minimum size A fuel explosion device for exploding fuel in the working space, and disposed in parallel with the cylinder and rotated by a moving force of the first piston and the second piston during reciprocating movement of the first piston and the second piston; It provides a crankless engine comprising a rotating drum.

That is, the first piston and the second piston are disposed to face each other inside the single cylinder with respect to the intake and exhaust portion, and are simultaneously moved toward the intake or exhaust portion or simultaneously in the opposite directions away from the intake and exhaust portion. . As described above, the crankless engine may be formed to have a structure in which explosion vibrations generated by the first piston and the second piston cancel each other. Thus, the vibration design of the crankless engine can be omitted, and adverse effects of the system due to the vibration of the crankless engine can also be prevented.

In addition, the crankless engine is formed of a structure for directly converting the linear kinetic energy of the first piston and the second piston into the rotational kinetic energy of the rotary drum. Therefore, the crank and the connecting rod used in the conventional reciprocating piston engine can be omitted in the crankless engine.

Guide protrusions protruding toward the rotating drum may be formed in the first piston and the second piston. One side and the other side of the cylinder may be formed with a guide hole through which the guide protrusion is movable. One side and the other side of the rotary drum may be formed with a guide groove portion is inserted into the end of the guide protrusion to be movable so as to convert the movement force of the first piston and the second piston to the rotational force of the rotary drum. Accordingly, the first piston and the second piston may be directly connected to the rotating drum by the guide protrusion and the guide groove.

The first piston and the second piston may be formed in a shape such that the guide hole is not exposed in the working space when the first piston and the second piston move. That is, the closed state of the working space can be always maintained by the cylinder, the first piston, and the second piston when the crankless engine is driven.

The guide protrusion may be formed on the outer circumference of the piston to be spaced apart at any angle along the circumferential direction. A plurality of guide holes may be formed at positions opposite to the guide protrusions. However, only one of the guide protrusions may be inserted into the guide groove of the rotating drum.

The guide hole may be formed to have a length equal to the thickness of the guide protrusion along the moving direction of the first piston and the second piston so as to guide the movement of the first piston and the second piston. Therefore, the guide protrusions and the guide hole portions not only perform the function of guiding movement of the first piston and the second piston, but also stably support the first piston and the second piston in the cylinder. Function can also be performed.

The guide groove may include at least one of a sine wave or a modified sinusoidal wave in a circumferential direction on an outer circumference of the rotating drum such that the guide protrusion rotates the rotating drum when the first piston and the second piston reciprocate. It may be formed in a closed curve shape. The modified sinusoidal wave is a waveform in which a part of the sinusoidal wave is deformed so that the piston converts the linear motion force into the rotational force from the moment of explosion. Therefore, when the first piston and the second piston is reciprocated along the cylinder, the moving force of the guide protrusion can be applied to the inclined side of the guide groove portion, the force of the force acting on the side of the guide groove portion The rotating drum may be rotated in one direction by the component force. In particular, when the guide groove is formed in a sine wave, the first piston and the second piston can be moved in the same pattern as the conventional reciprocating piston engine.

The end of the guide protrusion may be moved along a single one-cycle guide groove in one cycle operation of the crankless engine. The guide groove may be formed in a shape in which a plurality of one cycle guide grooves are connected to the outer circumference of the rotating drum along the circumferential direction. Thus, the crankless engine performs a plurality of operating cycles in one rotation of the rotating drum. That is, by adjusting the shape of the guide groove, it is possible to change the rotational speed of the rotating drum rotated per cycle of the crankless engine.

Unlike the above, the guide groove may be formed so that the rotating drum is rotated more than once in one cycle of operation of the crankless engine. However, if the rotating drum is rotated more than once in one cycle of operation of the crankless engine, the diameter of the rotating drum may be very small and the rotational speed of the rotating drum may be too fast.

The inflection portions of the guide groove portion may be formed with a larger curvature in a narrower range than the inflection portion of the sinusoidal wave so that the moving directions of the first piston and the second piston are quickly converted. The inflection portion for changing the direction of movement of the first piston and the second piston is a convex up and down in the closed curve of the sinusoidal wave or the modified sinusoidal wave, and corresponds to the top dead center and the bottom dead center of the first piston and the second piston.

Here, since the inflection portions of the sinusoidal wave are formed in a very gentle curved shape with a small curvature, the first piston and the second piston can be moved at a very slow speed in a section in which the moving direction is changed, and as a result, the first piston The time at which the direction of movement of the piston and the second piston is changed can also be increased. Therefore, the frequency of the reciprocating movement of the first piston and the second piston per unit time is reduced, thereby reducing the use efficiency.

On the other hand, in the present embodiment, since the curved portions of the guide grooves are formed to have a sharp curvature with a large curvature, the first piston and the second piston have a very high speed in the section of changing the moving direction (upper / lower dead center section). The movement time of the first piston and the second piston can be shortened as a result. Therefore, the frequency of the reciprocating movement of the first piston and the second piston per unit time is relatively increased, thereby improving the use efficiency of the piston, and also shortening one cycle period of the crankless engine.

If the crankless engine is a four-stroke, one-cycle engine, the bent portions of the guide grooves are formed at different positions to maximize the operating space at the suction stroke and to minimize the operating space at the exhaust stroke. Can be. That is, the position of the inflection portion corresponding to the bottom dead center of the suction stroke among the inflection portions of the guide groove portion may be disposed farther from the intake and exhaust portion, and the position of the inflection portion corresponding to the top dead center of the exhaust stroke among the inflection portions of the guide groove portion. May be disposed closer to the intake and exhaust section.

Therefore, since the working space is increased to the maximum in the suction stroke, the suction amount of fuel or air can be increased to improve the suction efficiency. The increase in the intake can increase the maximum compression pressure in the compression stroke, so the engine efficiency can be increased. In addition, since the working space is reduced to a minimum in the exhaust stroke, the residual amount of exhaust gas can be reduced to improve the exhaust efficiency.

The guide groove portion may be formed such that an angle formed between a tangent of a surface contacting the guide protrusion and a moving direction of the guide protrusion at an operating time of the fuel explosion device forms 0 degrees to 50 degrees. Of course, the angle formed between the tangent of the surface in contact with the guide protrusion and the direction of movement of the guide protrusion may be formed at 50 degrees to 90 degrees according to the design conditions and circumstances of the engine. However, if the angle formed between the direction of movement of the guide protrusion and the tangent of the guide groove is formed to be close to 90 degrees, there is a possibility that the guide groove portion interferes with the movement of the guide protrusion. On the other hand, if the angle formed between the direction of movement of the guide protrusion and the tangent of the guide groove is formed to be close to 0 degrees, the guide protrusion may be smoothly moved along the guide groove at a high speed during operation of the fuel explosion device. Can be.

The intake and exhaust unit may be formed in a hollow shape. The inside of the intake and exhaust unit may be formed in a cross-sectional area smaller than the cross-sectional area of the cylinder. As such, an unnecessary increase in the working space can be prevented, and the maximum compression pressure by the first piston and the second piston can also be increased.

The fuel explosion device may include a fuel injection mechanism for injecting fuel gas into the working space when the size of the working space is minimum. Here, when the size of the working space is minimum, air in the working space may be compressed to a temperature for spontaneous ignition of the fuel gas. Unlike the above, the fuel explosion apparatus may include a fuel ignition mechanism for igniting fuel gas in the working space when the size of the working space is minimum. Here, when the size of the working space is minimum, fuel gas and air in the working space may be compressed to a pressure for completely burning the fuel gas.

The rotating drum may be formed in a hollow shape. Inside the rotary drum may be provided with a shift output unit for outputting to the outside after shifting the rotational force of the rotary drum. That is, the speed change output unit is a speed change mechanism for accelerating or decelerating the rotational force of the rotary drum at a desired speed and outputting it to the outside of the rotary drum. For example, the transmission output unit may be formed of a planetary gear set for reducing the rotational force of the rotary drum. However, the shift output unit is not limited to the planetary gear set, and a shift mechanism having various structures capable of accelerating and decelerating the rotational force of the rotating drum may be used.

In addition, the rotary drum may be formed to be adjustable in the axial direction to change the position of the guide groove. When the length of the rotating drum is adjusted in the axial direction as described above, the position of the first piston and the second piston may also be changed because the position of the guide groove is changed. For example, if the length of the rotating drum is shortened, the size of the working space can be reduced because the distance between the first piston and the second piston is reduced. On the other hand, when the length of the rotating drum is increased, the distance between the first piston and the second piston is increased, the size of the working space can be increased. Therefore, the performance of the crankless engine can be effectively changed by adjusting the length of the rotary drum.

The cylinders may be arranged on the outer circumference of the rotating drum to be spaced apart from each other at random intervals along the circumferential direction. Therefore, the first piston, the second piston and the fuel explosion device may be provided in the cylinders, respectively. Since the cylinders, the first pistons and the second pistons are arranged together in a single rotating drum, the rotating drum can be used in common, and the number of cylinders of the engine can be increased without increasing the size of the appearance relatively large. Can be.

The guide groove may be formed in the same number as the cylinders. In addition, the guide grooves may be formed in the rotating drum in a shape connected to each other along the circumferential direction. Then, the first pistons and the second pistons all perform the same stroke regardless of the position.

Unlike the above, the guide groove portion may be formed in more or less than the number of the cylinder. In addition, the guide grooves may be formed in the rotating drum in a shape connected to each other along the circumferential direction. Then, the first pistons and the second pistons perform different strokes according to their positions.

Such cylinders may be provided at a plurality of positions along the longitudinal direction of the rotating drum, respectively. The guide grooves may be formed on the outer circumference of the rotating drum corresponding to the cylinders, respectively. That is, since the cylinders, the first pistons and the second pistons can be disposed at positions spaced apart from each other in the longitudinal direction of the rotating drum, the number of cylinders of the engine can be simply increased.

On the other hand, according to another embodiment of the present invention, a cylinder formed on one side of the intake and exhaust valve disposed intake valve and exhaust valve, a piston provided on the other side of the cylinder to be reciprocated, the intake and exhaust portion provided in the piston and the cylinder A fuel explosion device for exploding fuel in the interior of the working space when the working space formed therebetween is formed to a minimum size, and a moving force of at least one of the pistons as disposed in parallel with the cylinder and reciprocating of the piston; It provides a crankless engine comprising a rotating drum rotated by.

That is, compared with the crankless engine according to the embodiment of the present invention described above, the crankless engine according to another embodiment of the present invention is different from the point that the number of pistons provided in the cylinder, other than the configuration of the present invention It can be configured similarly to one embodiment of the. In addition, the crankless engine according to another embodiment of the present invention is described as having a single number or two pistons arranged in the cylinder, but is not limited thereto, and three or more pistons are arranged in the cylinder according to the engine design conditions and circumstances. You may.

The crankless engine according to the embodiment of the present invention may further include a valve opening and closing device arranged on the cylinder or the engine case and controlling opening and closing of the exhaust valve and the intake valve according to the rotation angle of the rotary drum. That is, the valve opening and closing device may automatically open and close the exhaust valve and the intake valve by using the rotational force of the rotary drum. Therefore, the timing belt and camshaft used in the conventional reciprocating piston engine can be omitted.

The valve opening and closing device may include a drum protrusion protruding from an outer circumference of the rotating drum, a valve opening part rotatably provided at an outside of the cylinder or the engine case, and disposed at one end of the exhaust valve or at an end of the intake valve, And an opening / closing control part provided between the other side of the valve opening and closing part and the drum protrusion part to open and close the intake valve or the exhaust valve by rotating the valve opening and closing part when the rotating drum is rotated.

At least one of the valve opening and closing part or the opening / closing control part may be disposed to change the position of the cylinder or the engine case so as to adjust the opening and closing time of the intake valve and the exhaust valve. Therefore, when an error occurs in the timing of the intake valve and the exhaust valve during long time use of the crankless engine, the timing of the intake valve and the exhaust valve is appropriately controlled by a simple method of simply adjusting the position of the rotation shaft of the valve opening and closing portion. Can be adjusted.

The drum protrusion may be formed of an intake drum protrusion and an exhaust drum protrusion disposed at different positions of the rotary drum. At this time, the intake drum projection portion and the exhaust drum projection portion may be formed in a plurality along the circumferential direction on the outer circumference of the rotary drum. That is, the intake valve may be opened and closed by the intake drum protrusion, and the exhaust valve may be opened and closed by the exhaust drum protrusion.

The opening and closing control unit may be formed of an opening and closing control protrusion protruding to the other side of the valve opening and closing part so that the end is movably contacted to the outer circumference of the rotating drum formed with the drum protrusion when the rotating drum is rotated. That is, the opening and closing adjustment protrusion may be rotated in the radial direction of the rotating drum by the drum protrusion when the rotating drum is rotated, and the valve opening and closing portion may be rotated together with the opening and closing adjustment protrusion.

Alternatively, the opening and closing control unit, the movement guide disposed between the valve opening and closing portion and the rotary drum, and the movable guide is provided to be movable, the other end of the valve opening and closing portion and the opening and closing adjustment rod is disposed on the outer periphery of the rotary drum Can be formed. That is, the opening and closing adjustment rod may be moved in the radial direction of the rotating drum along the movement guide by the drum protrusion when the rotating drum is rotated, the valve opening and closing portion may be rotated by the opening and closing adjustment rod.

Meanwhile, unlike the above, the drum protrusion may be formed of an intake drum protrusion and an exhaust drum protrusion disposed at different positions of the rotary drum. In this case, the intake drum protrusion and the exhaust drum protrusion may be formed in a gear shape along the circumferential direction on the outer circumference of the rotating drum. That is, the intake valve may be opened and closed by the intake drum protrusion, and the exhaust valve may be opened and closed by the exhaust drum protrusion.

The opening and closing control unit may be formed of a cam gear coupled to the drum protrusion, and an opening and closing control cam provided on the rotating shaft of the cam gear and slidably contacting the other side of the valve opening and closing part. That is, the cam gear may be rotated together with the drum protrusion when the rotating drum is rotated, the opening and closing adjustment cam may be rotated together with the cam gear, and the valve opening and closing portion may be rotated by the opening and closing adjustment cam. have.

In the crankless engine according to the embodiment of the present invention, the weight and size of the engine can be significantly reduced by omitting the crank and the connecting rod. In addition, the crankless engine of the present invention can improve the efficiency and performance of the engine as the weight and size are reduced.

In addition, the crankless engine according to the embodiment of the present invention may be arranged to face two pistons to cancel each other vibration generated when the engine is driven. Therefore, the crankless engine of the present invention can significantly reduce the amount of vibration generated, thereby reducing the necessity of the vibration design and the adverse effect of the vibration.

In addition, the crankless engine according to an embodiment of the present invention, by forming a guide hole formed in the shape of a modified sinusoidal wave in the rotating drum, it is possible to convert the linear motion to the rotational force from the moment of explosion, the performance and efficiency of the engine only with a simple design change Can improve. That is, the crankless engine of the present invention changes the shape of the guide groove to easily change the maximum compression time and the maximum compression pressure of the engine, the opening and closing time of the valve and the opening and closing time, the top dead center and the bottom dead center of the piston, and the feed speed of the piston. I can regulate it.

In addition, the crankless engine according to the embodiment of the present invention can arrange the cylinders, the first pistons and the second pistons in a single rotating drum to increase or decrease the number of cylinders of the engine. In addition, since the crankless engine of the present invention uses only a single rotating drum irrespective of the number of cylinders, first pistons and second pistons, a high-power engine because the change in the size of the engine appearance due to the increase in the number of cylinders is small. Can be made relatively small.

1 is a front view showing a crankless engine according to an embodiment of the present invention.
FIG. 2 is a cross-sectional view taken along line II of FIG. 1.
3 is a view showing a guide hole of the cylinder shown in FIG.
4 to 7 are operation state diagrams showing the intake stroke, the compression stroke, the expansion stroke, and the exhaust stroke of the crankless engine shown in FIG. 1, respectively.
8 to 12 are views illustrating various examples of the guide groove illustrated in FIG. 1 in a form in which the rotating drum is unfolded.
13 is an operating state diagram showing an example of the valve opening and closing device shown in FIG.
14 to 16 are each an operational state diagram showing another example of the valve opening and closing device shown in FIG.
17 is a front view showing a crankless engine according to another embodiment of the present invention.
18 is a cross-sectional view of the crankless engine shown in FIG. 17.
19 is a schematic view showing various structures of guide grooves according to the number of cylinders in another embodiment of the present invention.
20 is a front view showing a crankless engine according to another embodiment of the present invention.
21 is a front view showing a crankless engine according to another embodiment of the present invention.

Hereinafter, embodiments according to the present invention will be described in detail with reference to the accompanying drawings. However, the present invention is not limited to or limited by the embodiments. Like reference symbols in the drawings denote like elements.

1 is a front view showing a crankless engine according to an embodiment of the present invention, Figure 2 is a cross-sectional view taken along the line II shown in Figure 1, Figure 3 is a guide hole of the cylinder shown in Figure 1 It is a figure which shows a part.

Referring to FIG. 1, the crankless engine 100 according to an embodiment of the present invention includes a cylinder 110, a first piston 120, a second piston 130, a fuel explosion device 140, and a rotating drum ( 150, and a valve opening and closing device 160. Here, the working space S is formed in the cylinder 110, the first piston 120, and the second piston 130. The working space S is a space for receiving fuel and air. The working space S may change in volume as the first piston 120 and the second piston 130 are moved.

1 and 2, the cylinder 110 is a cylindrical member having a hollow inside. The first piston 120 and the second piston 130 may be disposed in the left and right portions of the cylinder 110 to be movable in the left and right directions. An intake and exhaust unit 112 in which the intake valve 114 and the exhaust valve 116 are disposed may be formed in the middle of the cylinder 110.

The intake and exhaust unit 112 may be formed in a hollow shape. The inside of the intake and exhaust unit 112 may be formed in a cross-sectional area smaller than the internal cross-sectional area of the cylinder 110. This is because an unnecessary increase in the operating space S due to the internal space of the intake and exhaust unit 112 can be prevented. Therefore, the maximum compression pressure of the working space S by the first piston 120 and the second piston 130 may also be increased.

The intake valve 114 and the exhaust valve 116 may be arranged in a single position or a plurality of positions in the intake and exhaust section 112. Hereinafter, in the present exemplary embodiment, two intake valves 114 are disposed in front of the intake and exhaust unit 112, and two exhaust valves 116 are disposed in the rear of the intake and exhaust unit 112.

1 to 3, the first piston 120 may be provided to reciprocate on the left side of the cylinder 110, and the second piston 130 may reciprocate on the right side of the cylinder 110. It may be provided to be movable. The first piston 120 and the second piston 130 may be arranged symmetrically about the intake and exhaust 112 of the cylinder 110, and operate in a direction symmetrical with each other when the crankless engine 100 operates. Can be. That is, the first piston 120 and the second piston 130 may be disposed to face each other with respect to the intake and exhaust unit 112, and are simultaneously moved toward or away from the intake and exhaust unit 112. Can be moved simultaneously in the direction.

Therefore, since the vibration generated from the first piston 120 and the vibration generated from the second piston 130 are opposite to each other, vibrations of the first piston 120 and the second piston 130 may be canceled with each other. . As such, the crankless engine 100 is formed in a structure that cancels the vibrations of the first piston 120 and the second piston 130 from each other, so that the design difficulty due to the vibration can be greatly reduced, and the engine due to the vibration Adverse effects can also be prevented.

Guide protrusions 122 and 132 may be formed to protrude in a radial direction on the outer circumference of the first piston 120 and the second piston 130. The guide protrusions 122 and 132 may be formed on the outer circumferences of the first piston 120 and the second piston 130 to be spaced apart from each other at arbitrary angles along the circumferential direction. Hereinafter, in the present exemplary embodiment, two guide protrusions 122 and 132 are formed on the outer circumferences of the first piston 120 and the second piston 130.

In addition, guide holes 118 through which guide protrusions 122 and 132 are movably penetrated may be formed at left and right sides of the cylinder 110, respectively. A plurality of guide holes 118 may be formed at positions facing the guide protrusions 122 and 132. The guide hole parts 118 may be formed to have a width equal to the thickness of the guide protrusions 122 and 132 along the moving directions of the first piston 120 and the second piston 130. Accordingly, the guide protrusions 122 and 132 and the guide hole portions 118 not only serve to guide the movement of the first piston 120 and the second piston 130, A function of stably supporting the first piston 120 and the second piston 130 may also be performed.

The first piston 120 and the second piston 130 may be formed so as not to expose the guide hole 118 between the first piston 120 and the second piston 130 when the crankless engine 100 is driven. have. That is, when a part of the guide hole 118 is exposed between the first piston 120 and the second piston 130, the sealed state of the working space S is broken, so that the performance and efficiency of the crankless engine 100 may be improved. Because it is greatly reduced. Therefore, the shape of the first piston 120 and the second piston 130 may be designed in a direction that always maintains the sealed state of the operating space (S) when the crankless engine 100 is driven.

1 and 2, the fuel explosion device 140 is a device that explodes fuel inside the working space when the working space S is formed to a minimum size. The fuel explosion device 140 may be provided at the intake and exhaust unit 112. However, the number and location of the fuel explosion device 140 is not limited to the present embodiment, a single number or a plurality may be disposed at various positions of the cylinder 110 as necessary.

If the crankless engine 100 is a diesel engine, the fuel explosion device 140 is a fuel injection mechanism (not shown) for injecting fuel gas into the interior of the working space S at the time when the size of the working space S is minimum. May be provided). When the size of the working space S is minimum, the first piston 120 and the second piston 130 may compress the air in the working space S to a temperature at which the fuel gas naturally ignites.

Alternatively, if the crankless engine 100 is a gasoline engine, the fuel explosion device 140 may include a fuel ignition mechanism for igniting fuel gas in the operating space S at a time when the size of the operating space S is minimum. have. When the size of the working space S is minimum, the first piston 120 and the second piston 130 may compress the air in the working space S to a pressure for completely burning the fuel gas.

In the present embodiment, the crankless engine 100 is a gasoline engine, and the fuel explosion device includes a fuel ignition mechanism. In addition, in the present embodiment, the crankless engine 100 is described as being a four-stroke single cycle engine composed of an intake stroke, a compression stroke, an expansion stroke, and an exhaust stroke.

1 and 2, the rotary drum 150 receives linear kinetic energy of the first piston 120 and the second piston 130 when the crankless engine 100 is driven and converts the rotational kinetic energy into rotational kinetic energy. Device. Therefore, in the crankless engine 100 of the present embodiment, since the rotating drum 150 plays a role of the crank used in the conventional reciprocating piston engine, the crank and the connecting rod may be omitted.

The rotary drum 150 may be disposed in parallel with the cylinder 110 at a position close to the cylinder 110. Guide grooves 152 may be formed at the left side and the right side of the rotating drum 150 so that end portions of the guide protrusions 122 and 132 penetrating the guide hole 118 may be movably inserted. Only one of the guide protrusions 122 and 132 of the first piston 120 and the second piston 130 may be inserted into the guide groove 152. Accordingly, the first piston 120 and the second piston 130 are directly connected to the rotating drum 150 through the guide protrusions 122 and 132 and the guide groove 152.

On the other hand, the rotary drum 150 may be formed in a hollow cylindrical shape. Inside the rotary drum 150 may be provided with a shift output unit 154 for outputting to the outside after the rotational force (F) of the rotary drum 150 is shifted. That is, the speed change output unit 154 is a speed change mechanism when the rotational force F of the rotary drum 150 is accelerated or decelerated at a desired speed.

For example, the speed change output unit 154 may be formed as a planetary gear set for reducing the rotational force F of the rotating drum 150. That is, the ring gear 154a may be mounted on the inner circumference of the rotating drum 150, and the sun gear 154b may be mounted at the center of the hollow portion of the rotating drum 150, and the ring gear 154a and the sun gear 154b may be mounted. A plurality of planetary gears (154c) may be disposed between the (). The ring gear 154a may be rotated at the same speed as the rotary drum 150, and the planetary gears 154c are connected to each other by a carrier (not shown). Therefore, when one of the sun gear 154b and the planetary gear 154c is fixed and the other of the sun gear 154b and the planetary gear 154c is connected to the output shaft 156, the rotational force output to the output shaft 156 is achieved. F may have a rotation speed smaller than that of the ring gear 154a.

However, the shift output unit 154 is not limited to the planetary gear set, and a shift mechanism having various structures capable of accelerating and decelerating the rotation force F of the rotating drum 150 may be used.

4 to 7 are operation state diagrams showing the intake stroke, the compression stroke, the expansion stroke, and the exhaust stroke of the crankless engine shown in FIG. 1, respectively. 8 to 12 are views illustrating various examples of the guide groove illustrated in FIG. 1 in a form in which the rotating drum is unfolded.

4 to 8, the guide groove 152 of the present embodiment smoothly converts the moving force of the first piston 120 and the second piston 130 to the rotational force F of the rotating drum 150. It may be formed into a shape that can be. For example, the guide groove 152 may be formed in a closed curve shape of at least one of a sine wave or a modified sinusoidal wave in the circumferential direction on the outer circumference of the rotating drum 150. The modified sinusoidal wave is a waveform in which a part of the sinusoidal wave is modified.

As illustrated in FIG. 8, when the guide groove 152 is formed as a sinusoidal wave, the first piston 120 and the second piston 130 may be moved in the same pattern as that of the conventional reciprocating piston engine. It can be operated in the same stroke as the reciprocating piston engine. When the first piston 120 and the second piston 130 are reciprocated along the cylinder 110, the guide protrusions 122 and 132 may be moved along the guide groove 152, and the guide protrusions ( The moving force of 122 and 132 may be applied to the inclined side surface of the guide groove 152. As such, the rotary drum 150 may be rotated by the force of the force applied to the side surface of the guide groove 152.

As illustrated in FIG. 8, the guide groove 152 may be formed in a shape in which one cycle guide grooves 152a are connected to each other in the circumferential direction on the outer circumference of the rotating drum 150. Here, the one cycle guide groove 152a corresponds to a guide groove corresponding to a path in which an end of the guide protrusions 122 and 132 is moved during one cycle operation of the crankless engine 100. When the guide groove 152 is formed in a structure in which a plurality of single cycle guide grooves 152a are connected as described above, the crankless engine 100 may perform a plurality of operating cycles when the rotating drum 150 is rotated once. have. Therefore, when the number of one cycle guide groove 152a forming the guide groove 152 is adjusted, the rotation speed of the rotating drum 150 rotated per one operation cycle of the crankless engine 100 may be changed.

Unlike the above, the guide groove 152 may be formed such that the rotary drum 150 is rotated more than once in one cycle of operation of the crankless engine 100. However, if the rotating drum 150 is rotated more than once during one cycle of operation of the crankless engine 100, the diameter of the rotating drum 150 must be very small, and the rotational speed of the rotating drum 150 is also too necessary. Will be faster. Hereinafter, in the present exemplary embodiment, the guide groove 152 is formed in a shape in which a plurality of operating cycles are performed by the crankless engine 100 when the rotary drum 150 is rotated once.

9 illustrates another example of the guide groove 152. Referring to FIG. 9, the inflection portions H1, H2, H3, and H4 of the guide groove 152 may have a larger curvature in a narrower range than the inflection portions H1, H2, H3, and H4 of the sinusoidal wave. Each can be formed. The inflection portions H1, H2, H3, and H4 are portions at which the moving directions of the first piston 120 and the second piston 130 are changed. That is, the inflection portions H1, H2, H3, and H4 correspond to upper and lower convex portions, and the top dead center (TDC) and the bottom dead center (BDC) of the first piston 120 and the second piston 130. Corresponds to. The top dead center (TDC) of the first piston 120 and the second piston 130 is a position where the first piston 120 and the second piston 130 are moved closest to the intake and exhaust part 112, and the first piston The bottom dead center (BDC) of the 120 and the second piston 130 is a position where the first piston 120 and the second piston 130 are moved farthest to the intake and exhaust part 112.

The inflection portions H1, H2, H3, and H4 of the guide groove 152 shown in FIG. 8 are formed in a very gentle curved shape with a small curvature. Therefore, the direction of movement of the first piston 120 and the second piston 130 may be changed at a very slow speed. As a result, since the time G2 at which the moving directions of the first piston 120 and the second piston 130 are changed is also greatly increased, the use efficiency of the first piston 120 and the second piston 130 may be reduced. Can be.

On the other hand, the inflection portions H1, H2, H3, and H4 of the guide groove 152 shown in FIG. 9 are formed in a sharp curved shape with a large curvature. Accordingly, the direction of movement of the first piston 120 and the second piston 130 may be changed at a very high speed. As a result, since the time G1 at which the moving directions of the first piston 120 and the second piston 130 are changed is also shortened by a predetermined time G2-G1, the first piston 120 and the second piston 130 are reduced. Increasing the number of movement per unit time of) may increase the frequency of use of the first piston 120 and the second piston (130). In addition, as shown in FIG. 9, one cycle period H1 to H5 of the crankless engine 100 may be shortened by '(G2-G1) * 4'. Specifically, since the time of 'G2-G1' is shortened in the sections of H1 to H2, the sections of H2 to H3, the sections of H3 to H4, and the sections of H4 to H5, respectively, the starting point of H5 is also lower than before. It can be shortened by '(G2-G1) * 4'.

10 shows another example of the guide groove 152. Referring to FIG. 10, the curved portions H1, H2, H3, and H4 of the guide groove 152 may be formed at different positions. That is, the inflection portion H3 formed between the exhaust stroke C and the intake stroke D is more in the top dead center TDC direction than the inflection portion H1 formed between the compression stroke A and the expansion stroke B. The inflection portion H4 formed between the intake stroke D and the compression stroke A may have a lower dead center BDC than the inflection portion H2 formed between the expansion stroke B and the exhaust stroke C. Can be formed in the lower direction.

When the inflection portion H3 corresponding to the top dead center of the exhaust stroke C is formed higher, the exhaust efficiency of the engine can be improved since the exhaust gas is completely exhausted by the height difference. In addition, when the inflection portion H4 corresponding to the bottom dead center of the intake stroke D is formed lower, the intake efficiency of the fuel gas may be increased by the height difference, and thus the intake efficiency of the engine may be improved. In particular, since the increase in the fuel intake in the intake stroke (D) increases the maximum compression pressure in the compression stroke (A), complete combustion of the fuel gas can be implemented to improve engine efficiency.

11 shows another example of the guide groove 152. Referring to FIG. 11, the curved portions H1, H2, H3, and H4 of the guide groove 152 may be formed similarly to the guide groove 152 illustrated in FIG. 8. However, the guide groove 152 of FIG. 11 is the direction of movement of the tangential T1 of the guide groove 152 and the guide protrusions 122 and 132 at the operating point E (E ′) of the fuel explosion device 140. The angle θ formed between T2 may be formed to form 0 degrees to 50 degrees. Of course, the angle θ formed between the tangent T1 of the guide groove 152 and the moving direction T2 of the guide protrusions 122 and 132 at the operation point E (E ′) of the fuel explosion device 140. ) May be formed at 0 degrees to 90 degrees depending on the design condition and situation of the engine. However, when the angle θ formed between the tangent T1 of the guide groove 152 and the moving direction T2 of the guide protrusions 122 and 132 is formed to be close to 90 degrees, the guide groove 152 is guide protrusion. There is a possibility of disturbing the movement of (122) (132). Therefore, in the present embodiment, it will be described that the angle θ formed between the tangent T1 of the guide groove 152 and the moving direction T2 of the guide protrusions 122 and 132 is formed to be close to 0 degrees.

As such, the angle formed between the direction T2 of the guide protrusions 122 and 132 and the tangent T1 of the guide groove 152 at the operation point E (E ') of the fuel explosion device 140 as described above. When θ) is formed at 0 degrees to 50 degrees, the guide protrusions 122 and 132 smoothly move along the guide grooves 152 at high speed, thereby improving the efficiency of the engine. Particularly, when the angle formed between the tangent T1 of the guide groove 152 and the moving direction T2 of the guide protrusions 122 and 132 is formed at 0 degrees at the operation point E 'of the fuel explosion device 140. In addition, the linear movement force of the first piston 120 and the second piston 130 may be all converted to the rotational force of the rotary drum 150.

12 illustrates another example of the guide groove 152. The guide groove 152 of FIG. 12 includes all of the features of the guide groove of FIGS. 9 to 11 described above. That is, like the guide groove of FIG. 9, the inflection portions H1, H2, H3, and H4 of the guide groove 152 may be formed with a large curvature in a narrow range. As shown in the guide groove of FIG. 10, the inflection portion H3 formed between the exhaust stroke C and the intake stroke D is superior to the inflection portion H1 formed between the compression stroke A and the expansion stroke B. FIG. The inflection portion H4 formed between the suction stroke D and the compression stroke A may be formed higher in the direction of the point TDC, and the inflection portion formed between the expansion stroke B and the exhaust stroke C It may be formed lower in the bottom dead center (BDC) direction than H2). In addition, as in the guide groove of FIG. 11, the tangent T1 of the guide groove 152 and the moving direction T2 of the guide protrusions 122 and 132 at the operation point E (E ′) of the fuel explosion device 140. The angle θ formed between) may be formed to form 0 degrees to 50 degrees.

Hereinafter, in the present exemplary embodiment, the guide groove 152 illustrated in FIG. 12 is formed in the rotating drum 150 among the guide grooves 152 illustrated in FIGS. 8 and 12. In addition, the guide groove 152 illustrated in FIG. 12 has a tangent T1 of the guide groove 152 and a moving direction T2 of the guide protrusions 122 and 132 at the operation point E of the fuel explosion device 140. It will be described that the angle θ formed between) is formed at 45 degrees. However, the guide groove 152 illustrated in FIG. 12 has a tangential and guide protrusion of the guide groove 152 at the operating point E ′ of the fuel explosion device 140 according to the design condition and the situation of the crankless engine 100. An angle formed between the moving directions of the 122 and 132 may be formed to 0 degrees.

13 is an operating state diagram showing an example of the valve opening and closing device shown in Figure 1, Figures 14 to 16 is an operating state diagram showing another example of the valve opening and closing device shown in FIG.

2, 3 and 13, the valve opening and closing device 160 is a device for controlling the opening and closing of the exhaust valve 116 and the intake valve 114 according to the rotation angle of the rotary drum 150. The valve opening and closing device 160 may automatically open and close the exhaust valve 116 and the intake valve 114 at an appropriate time using the rotational force F of the rotating drum 150. Therefore, the timing belt and camshaft used in the conventional reciprocating piston engine can be omitted.

The valve opening and closing device 160 may be disposed on an outer circumference of the cylinder 110. However, the valve opening and closing device 160 may be disposed in other parts that do not move according to the design conditions and the situation of the crankless engine 100. For example, the valve opening and closing device 160 may be disposed in an engine case (not shown) for accommodating the cylinder 110 and the rotary drum 150 therein, but the description thereof will be omitted. do.

The valve opening and closing device may include a drum protrusion 162, a valve opening and closing portion 164, and an opening and closing control unit 166.

The drum protrusion 162 is a protrusion protruding on the outer circumference of the rotating drum 150. The drum protrusion 162 may be formed of an intake drum protrusion 162a and an exhaust drum protrusion 162b disposed at different positions of the rotary drum 150. The intake drum protrusion 162a and the exhaust drum protrusion 162b may be formed in circumferential directions on the outer circumference of the rotating drum 150. In addition, the intake drum protrusion 162a and the exhaust drum protrusion 162b may be formed at different positions in the circumferential direction of the rotary drum 150 according to opening and closing times of the intake valve 114 and the exhaust valve 116. have. In addition, the intake drum protrusion 162a and the exhaust drum protrusion 162b may be provided in the rotary drum 150 to adjust the position in the circumferential direction of the rotary drum 150. By adjusting the positions of the intake drum protrusion 162a and the exhaust drum protrusion 162b in this manner, the opening and closing time and opening and closing period of the valve can be freely adjusted.

The valve opening / closing part 164 is a member that is disposed at one end of the exhaust valve 116 or the end of the intake valve 114 to open and close the exhaust valve 116 or the intake valve 114. The valve opening and closing portion 164 may be rotatably provided in a hinge structure outside the cylinder 110 or the engine case. The valve opening and closing portion 164 may be formed of an intake valve opening and closing portion 164a for opening and closing the intake valve 114 and an exhaust valve opening and closing portion 164b for opening and closing the exhaust valve 116.

The rotating shaft 168 of the valve opening and closing part 164 is provided to the engine case (not shown) or the cylinder 110 of the crankless engine 100 so as to selectively control the opening and closing time of the intake valve 114 and the exhaust valve 116. Position adjustment may be possible. The position of the valve opening and closing portion 164 may be changed along the outer circumference of the rotating drum 150. Therefore, when the timing of the intake valve 114 and the exhaust valve 116 is shifted when the crankless engine 100 is used for a long time, the position of the rotation shaft 168 of the valve opening / closing part 164 is changed to intake valve 114 and exhaust gas. The timing of the valve 116 can be adjusted simply.

For example, a bracket 169 supporting the rotation shaft 168 may be formed to protrude from the cylinder 110, and a hole 169a through which the rotation shaft 168 penetrates the rotation drum 150 in the bracket 169. It may be formed long in the same similar direction as the outer peripheral surface of, the fastening mechanism 168a for fastening the position of the rotating shaft 168 at a specific position of the hole may be provided on the bracket 169 and the rotating shaft 168. Of course, as described above, the timing of the intake valve 114 and the exhaust valve 116 is changed by simultaneously changing the positions of the intake drum protrusion 162a and the exhaust drum protrusion 162b in the circumferential direction of the rotary drum 150. Can be adjusted more freely.

The opening and closing control unit 166 is a member for opening and closing the intake valve 114 or the exhaust valve 116 by rotating the valve opening and closing portion 164 by the drum protrusion 162 when the rotating drum 150 rotates. The opening and closing control unit 166 may be formed as an opening and closing control protrusion 166 protruding to the outer circumference of the rotary drum 150 from the other side of the valve opening and closing portion 164.

The opening and closing adjustment protrusion 166 may be integrally formed at the other side of the valve opening and closing portion 164. An end portion of the opening / closing adjustment protrusion 166 is in contact with or close to the outer circumference of the rotating drum 150, and rotates the valve opening / closing portion 164 while riding the drum protrusion 162 when the rotating drum 150 rotates. have. The opening / closing adjustment protrusion 166 is formed on the other side of the intake valve opening and closing portion 164a and interferes with the intake drum protrusion 162a, and the exhaust valve opening and closing portion 164b. It may be formed on the other side of the exhaust opening and closing adjustment projections (166b) to interfere with the exhaust drum projection (162b).

On the other hand, Figure 14 shows another example of the valve opening and closing device 560. Referring to FIG. 14, the valve opening and closing device 560 may include a drum protrusion 162, a valve opening and closing unit 164, an opening and closing control unit 166, and a position adjusting unit 562. That is, compared with the valve opening and closing device 160 shown in FIG. 13, the valve opening and closing device 560 of FIG. 14 has a position adjusting unit 562 instead of omitting the bracket 169 and the fastening mechanism 168a of FIG. 13. ) Is different. Therefore, hereinafter, only the position adjusting unit 562 will be described, and detailed description of the other components will be omitted.

For example, the position adjusting unit 562 may be composed of a moving block 564, a fixing bracket 566, an adjusting screw 568. That is, the moving block 564 may be provided to be movable in the engine case in the same similar direction as the outer circumference of the rotary drum 150, the fixed bracket 566 is the engine at a position spaced apart from the moving block 564 a predetermined distance It may be fixed to the case, the adjustment screw 568 may be fastened to the fixed bracket 566 so that the end is in contact with the moving block 564. At this time, the moving block 564 may be elastically supported toward the adjustment screw 568, the rotation shaft 168 of the valve opening and closing portion 164 may be rotatably disposed. Therefore, when the adjustment screw 568 is rotated, the position of the moving block 564 is moved in accordance with the change in the position of the adjustment screw 568 can also be adjusted the position of the valve opening and closing portion 164.

However, the configuration of the position adjusting unit 562 is not limited to the above-described configuration, various configurations may be applied according to the design conditions and circumstances of the engine. For example, the position of the valve opening and closing portion 164 may be adjusted using an actuator or an electric motor.

In addition, another example of the valve opening and closing device 260 is shown in FIG. 15. Referring to FIG. 15, the valve opening and closing device 260 may include a drum protrusion 162, a valve opening and closing unit 164, an opening and closing control unit 266, and a position adjusting unit 562. That is, compared with the valve opening and closing device 560 shown in FIG. 14, the valve opening and closing device 260 of FIG. 15 has a different configuration of the opening and closing control unit 266. Therefore, hereinafter, only the opening and closing adjustment unit 266 will be described, and detailed description of the configuration other than that will be omitted.

The opening / closing control unit 266 illustrated in FIG. 15 includes a movement guide 267 disposed between the valve opening and closing portion 164 and the rotary drum 150, and a movement guide 267, which is movable in the valve opening and closing portion 164. It may be formed of the opening and closing control rod 268 is disposed at both ends of the other side and the outer periphery of the rotary drum 150). The movement guide 267 may be formed in a cylindrical shape having a hollow portion formed therein. An intermediate portion of the opening / closing control rod 268 may be disposed in the hollow portion of the movement guide 267 to be movable in the radial direction of the rotary drum 150. The movement guide 267 may be provided in the movement block 564 of the position adjusting unit 562. The opening and closing control unit 266 is provided between the intake opening and closing control unit disposed between the intake valve opening and closing portion 164a and the intake drum projection portion 162a, and between the exhaust valve opening and closing portion 164b and the exhaust drum protrusion portion 162b. It may be formed as an opening and closing control unit for exhaust disposed.

16 shows another example of the valve opening and closing device 360. Referring to FIG. 16, the valve opening and closing device 360 illustrated in FIG. 16 may include a drum protrusion 362, a valve opening and closing unit 164, an opening and closing control unit 366, and a position adjusting unit 562. That is, compared with the valve opening and closing device 560 shown in FIG. 14, the valve opening and closing device 360 of FIG. 16 has a different configuration of the drum protrusion 362 and the opening / closing control unit 366. Therefore, hereinafter, only the drum protrusion 362 and the opening / closing control unit 366 will be described, and a detailed description of the other components will be omitted.

The drum protrusion 362 shown in FIG. 16 may be formed in a gear shape along the circumferential direction on the outer circumference of the rotating drum 150. Meanwhile, in the present embodiment, the singular drum protrusions 362 are described as being shared by two opening and closing control units 366, but two drum protrusions 362 corresponding to the two opening and closing control units 366 as necessary. Can be formed.

The opening / closing adjustment part 366 shown in FIG. 16 is provided on the cam gear 367 coupled to the drum protrusion 362 and the rotation shaft 168 of the cam gear 367 and slides on the other side of the valve opening / closing part 164. It may be formed of an opening and closing control cam 368 in contact with. The cam gear 367 may rotate together with the drum protrusion 362 when the rotating drum 150 rotates. The opening and closing control cam 368 may rotate together with the cam gear 367 to rotate the valve opening and closing portion 164. The rotation shaft of the cam gear 367 and the opening and closing adjustment cam 368 may be rotatably provided at the moving block 564 of the position adjusting unit 562. The opening and closing control unit 366 is provided between the intake opening and closing control unit disposed between the intake valve opening and closing portion 164a and the intake drum projection portion 162a, and between the exhaust valve opening and closing portion 164b and the exhaust drum projection portion 162b. It may be formed as an opening and closing control unit for exhaust disposed.

In addition, the valve opening and closing apparatus of the present embodiment may be configured by the intake valve 114 and the exhaust valve 116 as a solenoid valve to adjust the operation timing of the valve in an electronic control method according to the rotational speed of the engine. In addition, the manner of adjusting the position of the valve opening and closing portion 164 and the opening and closing control portion 266, 366 is not limited to the above-described examples, various methods may be applied according to the design conditions and circumstances.

17 is a front view illustrating a crankless engine according to another embodiment of the present invention, and FIG. 18 is a cross-sectional view of the crankless engine illustrated in FIG. 17. And, Figure 19 is a schematic diagram showing various structures of the guide groove portion according to the number of cylinders in another embodiment of the present invention. 17-19, the same reference numerals as those shown in Figs. 1 and 2 denote the same members. Hereinafter, descriptions will be made focusing on differences from the crankless engine 100 illustrated in FIGS. 1 and 2.

17 and 19, the crankless engine 400 according to another embodiment of the present invention is different from the crankless engine 100 shown in Figs. 1 and 2, the cylinder 110, the first An engine body 410, 412, 414, 416, including a piston 120, a second piston 130, a fuel explosion device 140, and a valve opening and closing device 160, has a single rotating drum 150. The difference is that a plurality is arranged in.

That is, the engine bodies 410, 412, 414, and 416 may be disposed on the outer circumference of the rotating drum 150 to be spaced apart from each other at arbitrary intervals along the circumferential direction. Since the engine bodies 410, 412, 414, and 416 are all arranged on a single rotating drum 150, the rotating drum 150 may be used in common, and the engine may increase even though the number of cylinders of the engine increases. The outer size of may not increase relatively.

The engine bodies 410, 412, 414, 416 as described above may be provided at a plurality of positions along the length direction of the rotary drum 150, respectively. When the engine main bodies 410, 412, 414, 416 are disposed at positions spaced apart from each other in the longitudinal direction of the rotary drum 150, the guide grooves 152 are also spaced apart from each other in the longitudinal direction of the rotary drum 150. It may be formed at each position. In addition, only by changing the structure to increase the length of the rotating drum 150, the number of cylinders of the engine can be increased simply.

The guide groove 152 may be formed in the same number as the engine bodies 410, 412, 414, and 416. The plurality of guide grooves 152 may be formed in a shape connected to the rotary drum 150 along the circumferential direction. When the guide grooves 152 are formed as described above, the engine bodies 410, 412, 414, 416 all perform the same stroke regardless of the position.

On the other hand, unlike the above, the guide groove 152 may be formed in a number more or less than the number of the engine body (410, 412, 414, 416). The plurality of guide grooves 152 may be formed in a shape connected to the rotary drum 150 along the circumferential direction. When the guide grooves 152 are formed as described above, the engine bodies 410, 412, 414, 416 perform different strokes according to positions. Therefore, when the crankless engine 400 is formed of a plurality of cylinders, each of the engine main bodies 410, 412, 414, and 416 generates a rotational force F at different points in time, so that the crankless engine 400 ) Output can be obtained more continuously.

19, the configuration of the crankless engine 400 according to the number of the engine main bodies 410, 412, 414, 416 and the guide grooves 152 is schematically illustrated in FIG. 19. Is shown.

As shown in (a) (b) (c) of FIG. 19, if the number of the engine bodies 410, 412, 414, 416 and the guide grooves 152 is the same, the engine bodies 410, 412 are described. 414 and 416 all perform the same stroke. However, as shown in (i) of FIG. 19, when the number of the engine bodies 410 and 412 and the guide grooves 152 is the same, but the engine bodies 410 and 412 are spaced apart from each other at different angles, Engine bodies 410 and 412 perform different strokes.

And, as shown in (d) (e) (f) of FIG. 19, if the number of the engine body 410, 412, 414, 416 is more than the number of the guide groove 152, the engine body 410 412, 414, and 416 perform different strokes. 19 (g) (h), if the number of the engine bodies 410, 412, 414 is less than the number of the guide grooves 152, the engine bodies 410, 412 ( 414 perform different administrations.

 As described above, if the number of the engine main bodies 410, 412, 414, 416 and the guide grooves 152 is not the same (FIGS. 19 (d) to 19 (h)), the engine main body 410. When the number of the engine bodies 410, 412, 414, 416 and the guide grooves 152 is the same because the (412) 414 and 416 may sequentially perform different strokes (FIG. 19). It is more preferable than (a)-FIG. 19 (c)).

In addition, even when the number of the engine bodies 410 and 412 and the guide grooves 152 is the same, when the engine bodies 410 and 412 are arranged to be spaced apart from each other at different angles (FIGS. 19 (d) to 19 ( h)), the engine bodies 410, 412, 414, 416 may sequentially perform different strokes. Therefore, since the arrangement position of the engine bodies 410 and 412 may be eccentrically arranged to one side according to the design conditions and the situation of the engine, the design freedom of the engine may be improved.

In addition, when the number of the engine bodies 410, 412, 414, 416 is greater than the number of the guide grooves 152 (FIG. 19 (d) to FIG. 19 (f)) and the engine body 410. When the number of the (412) 414, 416 is one more than the number of the guide grooves 152 (Figs. 19 (g) to 19 (h)), the engine main body 410, 412, 414 ( Since 416 perform different strokes sequentially, both can achieve the same similar engine performance. However, when the number of the engine bodies 410, 412, 414, 416 is more than the number of the guide grooves 152 (FIG. 19 (d) to FIG. 19 (f)), it is relatively easy to manufacture. There is an advantage.

Looking at the operation of the crankless engine 100 according to an embodiment of the present invention configured as described above are as follows.

The crankless engine 100 repeatedly executes four strokes of the intake stroke D, the compression stroke A, the expansion stroke B, and the exhaust stroke C. FIG.

4 and 12, in the suction stroke D, the first piston 120 is moved to the left and the second piston 130 is moved to the right. In addition, the intake valve 114 is in an open state, and the exhaust valve 116 is in a closed state.

At this time, since the first piston 120 and the second piston 130 are moved farther than the bottom dead center (BDC) in a direction away from the intake and exhaust unit 112, the size of the operating space (S) is the maximum. Therefore, since the intake amount of the fuel gas sucked through the intake valve 114 is greatly increased, the intake efficiency of the crankless engine 100 can be improved.

5 and 12, in the compression stroke A, the first piston 120 is moved to the right and the second piston 130 is moved to the left. The intake valve 114 and the exhaust valve 116 are both closed.

In this case, since the suction amount of the fuel gas sucked in the suction stroke D is increased, the maximum compression pressure may be improved by increasing the fuel gas compressed in the compression stroke A. FIG. Thus, complete combustion of the fuel gas can be realized upon combustion of the fuel gas.

6 and 12, in the expansion stroke B, the first piston 120 is moved to the left and the second piston 130 is moved to the right. The intake valve 114 and the exhaust valve 116 are closed. In this case, the explosive force of the fuel gas may be transmitted to both the first piston 120 and the second piston 130.

On the other hand, at the initial stage of the expansion stroke B, the fuel explosion device 140 is operated at a time slightly delayed at the time E when the size of the working space S is minimized to explode the fuel gas in the working space S. Let's do it. The reason why the operation point E of the fuel explosion device 140 is slightly delayed is because it is advantageous to operate the fuel explosion device 140 after being slightly moved from the apex of the inflection portion H1 of the guide groove 152. to be.

6 and 13, in the exhaust stroke C, the first piston 120 is moved to the right and the second piston 130 is moved to the left. The intake valve 114 is closed and the exhaust valve 116 is open.

At this time, since the first piston 120 and the second piston 130 are moved farther than the top dead center (TDC) in the direction closer to the intake and exhaust 112, the size of the operating space (S) is minimized. Therefore, since the residual amount of the exhaust gas exhausted through the exhaust valve 116 is greatly reduced, the exhaust efficiency of the crankless engine 100 can be improved.

20 is a front view showing a crankless engine according to another embodiment of the present invention. In Fig. 20, the same reference numerals as those shown in Figs. 1 to 13 denote the same members. Hereinafter, descriptions will be made mainly on points different from the crankless engine 100 illustrated in FIGS. 1 to 13.

The crankless engine 600 shown in FIG. 20 is different from the crankless engine 100 shown in FIGS. 1 to 13 in that the length of the rotating drum 150 is adjustable.

For example, the rotary drum 150, the main body parts 650, 652, 654, the main body parts 650, 652, 654 separated in the axial direction of the rotary drum 150 in the rotation direction. Constraints and rotates the engaging portion 656 to movably couple the body portions 650, 652, 654 in the axial direction of the rotary drum 150, and the body portions 650, 652, 654. The fastening part 658 may be provided to restrain the axial direction of the drum 150.

Here, in the present embodiment, the main body parts 650 and 652 and 654 disposed on the left and right sides of the rotary drum 150 are moved to the three main body parts 650 and 652 and 654 so as to be movable in the left and right directions. However, the present invention is not limited thereto, and two, four or five main body parts may be configured according to design conditions and situations.

In addition, the coupling part 656 may include a coupling protrusion 656a formed to protrude on either side of the main body parts 650 and 652 and 654, and the main body parts 650 and 652 and 654. It may include a coupling groove (656b) formed on the other side corresponding to the coupling protrusion (656a). Coupling protrusion 656a may protrude in a cylindrical shape from the side of the body portion (650, 652, 654). On the outer circumferential surface of the engaging protrusion 656a, a plurality of gears formed in the axial direction of the rotary drum 150 may be formed in the circumferential direction. The coupling groove 656b may be formed in a shape in which the coupling protrusion 656a may be inserted into the side surfaces of the main body parts 650 and 652 and 654. On the inner circumferential surface of the coupling groove 656b, a plurality of gears elongated in the axial direction of the rotary drum 150 may be formed in the circumferential direction so as to be engaged with the gears of the coupling protrusion 656a. Accordingly, the rotary drum 150 may be widened or narrowed in the left and right direction about the coupling portion of the coupling protrusion 656a and the coupling groove 656b. However, the coupling part 656 is not limited to the coupling protrusion 656a and the coupling groove 656b described above, and the main body parts 650, 652, 654 may be rotated according to design conditions and circumstances. Various structures for movably coupling in the axial direction may be applied.

In addition, the fastening part 658 is fastened to the fastening flanges 658a formed on the main body parts 650, 652 and 654 so as to face each other, and the fastening flanges 658a, and thus the main body part 650. It may include a fastening member (658b) for fixing the (652) (654). However, the fastening part 658 is not limited to the fastening flange 658a and the fastening member 658b, and various fastening structures may be applied according to design conditions and situations.

When the length of the rotary drum 150 is adjusted in the axial direction as described above, since the position of the guide groove 152 is changed, the positions of the first piston 120 and the second piston 130 may also be changed. That is, when the length of the rotary drum 150 is shortened, since the distance between the first piston 120 and the second piston 130 is reduced, the size of the operating space (S) can be reduced. On the other hand, when the length of the rotary drum 150 is increased, the size of the operating space (S) can be increased because the distance between the first piston 120 and the second piston 130 is increased. Therefore, by adjusting the length of the rotating drum 150, the performance of the crankless engine can be effectively changed.

21 is a front view showing a crankless engine according to another embodiment of the present invention. In Fig. 21, the same reference numerals as those shown in Figs. 1 to 13 denote the same members. Hereinafter, descriptions will be made mainly on points different from the crankless engine 100 illustrated in FIGS. 1 to 13.

The crankless engine 700 shown in FIG. 20 differs from the crankless engine 100 shown in FIGS. 1 to 13 in that only a single cylinder 710 and a piston 720 are provided in the rotating drum 150. Is different.

Accordingly, the crankless engine 700 of FIG. 20 may be applied to a small engine that does not need to use two pistons 120 and 130, unlike the crankless engine 100 of FIGS. 1 to 13.

As described above, one embodiment of the present invention has been described by specific embodiments, such as specific components, and limited embodiments and drawings, but this is only provided to help a more general understanding of the present invention. The present invention is not limited thereto, and various modifications and variations can be made by those skilled in the art to which the present invention pertains. Therefore, the spirit of the present invention should not be limited to the described embodiments, and all of the equivalents and equivalents of the claims, as well as the following claims, will fall within the scope of the present invention. .

100, 400, 600, 700: crankless engine
110, 710: cylinder
120: first piston
130: second piston
140: fuel explosion device
150: rotating drum
160, 260, 360: valve opening and closing device
410, 412, 414, 416: engine body

Claims (23)

A cylinder having an intake and exhaust portion disposed between the intake valve and the exhaust valve;
A first piston provided on one side of the cylinder to reciprocate;
A second piston provided on the other side of the cylinder to be reciprocated so as to face each other on the same axis as the first piston with respect to the intake and exhaust unit;
A fuel explosion device which is provided in the intake and exhaust unit and explodes fuel in the working space when the working space formed between the cylinder, the first piston and the second piston is formed to a minimum size; And
And a rotating drum disposed in parallel with the cylinder and rotated by a moving force of the first piston and the second piston during the reciprocating movement of the first piston and the second piston.
The first piston and the second piston are driven in opposite directions along the cylinder to simultaneously compress or expand the working space,
Guide protrusions protruding toward the rotating drum are formed on the first piston and the second piston, and guide holes are formed on one side and the other side of the cylinder to move the guide protrusions, and one side of the rotating drum. And the other side is formed with a guide groove that is inserted into the end of the guide projection to be movable so as to convert the movement force of the first piston and the second piston opposite to each other rotational force,
The guide groove has a closed curve shape of at least one of a sinusoidal wave or a modified sinusoidal wave in a circumferential direction on an outer circumference of the rotary drum so that the guide protrusion rotates the rotary drum when the first piston and the second piston reciprocate. ,
The crankless engine of each of the guide grooves is formed with a larger curvature in a narrower range than that of the sinusoidal wave so that the moving directions of the first piston and the second piston are quickly changed.
In a crankless engine formed of a four-stroke, one-cycle engine,
A cylinder having an intake and exhaust portion disposed between the intake valve and the exhaust valve;
A first piston provided on one side of the cylinder to reciprocate;
A second piston provided on the other side of the cylinder to be reciprocated so as to face each other on the same axis as the first piston with respect to the intake and exhaust unit;
A fuel explosion device which is provided in the intake and exhaust unit and explodes fuel in the working space when the working space formed between the cylinder, the first piston and the second piston is formed to a minimum size; And
And a rotating drum disposed in parallel with the cylinder and rotated by a moving force of the first piston and the second piston during the reciprocating movement of the first piston and the second piston.
The first piston and the second piston are driven in opposite directions along the cylinder to simultaneously compress or expand the working space,
Guide protrusions protruding toward the rotating drum are formed on the first piston and the second piston, and guide holes are formed on one side and the other side of the cylinder to move the guide protrusions, and one side of the rotating drum. And the other side is formed with a guide groove for inserting the end of the guide projection to be movable so as to convert the movement force of the first piston and the second piston to the rotational force of the rotary drum,
The guide groove has a closed curve shape of at least one of a sinusoidal wave or a modified sinusoidal wave in a circumferential direction on an outer circumference of the rotary drum so that the guide protrusion rotates the rotary drum when the first piston and the second piston reciprocate. ,
The crankless engine of the guide groove portion is formed in different positions so as to form the operating space to the maximum in the intake stroke to the maximum, and to minimize the operating space in the exhaust stroke.
A cylinder having an intake and exhaust portion disposed between the intake valve and the exhaust valve;
A first piston provided on one side of the cylinder to reciprocate;
A second piston provided on the other side of the cylinder to be reciprocated so as to face each other on the same axis as the first piston with respect to the intake and exhaust unit;
A fuel explosion device which is provided in the intake and exhaust unit and explodes fuel in the working space when the working space formed between the cylinder, the first piston and the second piston is formed to a minimum size; And
And a rotating drum disposed in parallel with the cylinder and rotated by a moving force of the first piston and the second piston during the reciprocating movement of the first piston and the second piston.
The first piston and the second piston are driven in opposite directions along the cylinder to simultaneously compress or expand the working space,
Guide protrusions protruding toward the rotating drum are formed on the first piston and the second piston, and guide holes are formed on one side and the other side of the cylinder to move the guide protrusions, and one side of the rotating drum. And the other side is formed with a guide groove for inserting the end of the guide projection to be movable so as to convert the movement force of the first piston and the second piston to the rotational force of the rotary drum,
The guide groove has a closed curve shape of at least one of a sinusoidal wave or a modified sinusoidal wave in a circumferential direction on an outer circumference of the rotary drum so that the guide protrusion rotates the rotary drum when the first piston and the second piston reciprocate. ,
And the guide groove portion is formed such that an angle between a tangent of a surface contacting the guide protrusion and a moving direction of the guide protrusion at an operating time of the fuel explosion device forms 0 to 50 degrees.
4. The method according to any one of claims 1 to 3,
The guide protrusion is formed in the circumferential direction on the outer circumference of the piston is spaced apart at an arbitrary angle,
And a plurality of guide holes formed in a position opposite to the guide protrusions.
4. The method according to any one of claims 1 to 3,
The end of the guide projection is moved along the number of single cycle guide groove in the single cycle operation of the crankless engine,
The guide groove portion is a crankless engine formed in the shape of connecting a plurality of one cycle guide groove portion in the circumferential direction on the outer circumference of the rotary drum.
4. The method according to any one of claims 1 to 3,
The intake and exhaust unit is formed in a hollow shape,
The inside of the intake and exhaust unit is a crankless engine formed with a cross-sectional area smaller than the cross-sectional area of the cylinder.
4. The method according to any one of claims 1 to 3,
The fuel explosion device includes a fuel injection mechanism for injecting fuel gas into the working space when the size of the working space is minimum,
And a crankless engine in which the air in the working space is compressed to a temperature at which the fuel gas spontaneously ignites when the size of the working space is minimum.
4. The method according to any one of claims 1 to 3,
The fuel explosion apparatus includes a fuel ignition mechanism for igniting fuel gas in the working space when the size of the working space is minimum,
And a fuel gas and air in the working space are compressed to a pressure for completely burning the fuel gas when the size of the working space is minimum.
4. The method according to any one of claims 1 to 3,
The rotating drum is formed in a hollow shape,
A crankless engine having a shift output unit configured to output a rotation force of the rotary drum to the outside after the rotational drum is rotated.
10. The method of claim 9,
The shift output unit is a crankless engine formed of a planetary gear set for reducing the rotational speed of the rotating drum.
4. The method according to any one of claims 1 to 3,
The rotating drum is a crankless engine formed to be adjustable in the axial direction to change the position of the guide groove.
4. The method according to any one of claims 1 to 3,
The cylinder is a crankless engine disposed on the outer circumference of the rotary drum spaced apart from each other at random intervals along the circumferential direction.
The method of claim 12,
The guide groove portion is formed in the same number as the cylinders,
The crankless engine formed in the rotating drum in a shape in which the guide grooves are connected to each other along the circumferential direction.
The method of claim 12,
The guide groove portion is formed in more or less than the number of the cylinder,
The crankless engine formed in the rotating drum in a shape in which the guide grooves are connected to each other along the circumferential direction.
The method of claim 12,
The cylinders are each provided in a plurality of positions spaced apart along the longitudinal direction of the rotating drum,
And a crankless engine, each of which is formed at a position corresponding to the cylinders on the outer circumference of the rotating drum.
4. The method according to any one of claims 1 to 3,
The crankless engine further includes a valve opening and closing device for controlling opening and closing of the exhaust valve and the intake valve according to a rotation angle of the rotary drum.
The valve opening and closing device is a crankless engine disposed in the cylinder or engine case.
17. The method of claim 16,
The valve opening and closing device,
A drum protrusion protruding from the outer circumference of the rotating drum;
A valve opening / closing part rotatably provided at an outer side of the cylinder or the engine case, and having one side disposed at an end of the exhaust valve or an end of the intake valve; And
An opening / closing control part provided between the other side of the valve opening and closing part and the drum protrusion part to open and close the intake valve or the exhaust valve by rotating the valve opening and closing part when the rotating drum is rotated;
Crankless engine having a.
18. The method of claim 17,
At least one of the valve opening and closing portion or the opening and closing control unit is provided with a crankless engine that can be changed in position in the cylinder or the engine case to adjust the opening and closing time of the intake valve and the exhaust valve.
18. The method of claim 17,
The drum protrusion is formed of an intake drum protrusion and an exhaust drum protrusion disposed at different positions of the rotating drum,
And a plurality of the intake drum protrusions and the exhaust drum protrusions formed on the outer circumference of the rotary drum along a circumferential direction.
20. The method of claim 19,
The opening and closing control unit is a crankless engine formed of the opening and closing adjustment projections protruding on the other side of the valve opening and closing part so that the end is movably contacted to the outer circumference of the rotating drum formed with the drum projection when the rotating drum is rotated.
20. The method of claim 19,
The opening and closing control unit,
A movement guide disposed between the valve opening and closing portion and the rotary drum; And
An opening / closing control rod provided to be movable in the movement guide and having both ends disposed at the other side of the valve opening and closing part and the outer circumference of the rotary drum;
Crankless engine formed with.
20. The method of claim 19,
The drum protrusion is formed of an intake drum protrusion and an exhaust drum protrusion disposed at different positions of the rotating drum,
The crankless engine of the intake drum projection portion and the exhaust drum projection portion formed in a gear shape along the circumferential direction on the outer circumference of the rotary drum.
The method of claim 22,
The opening and closing control unit,
A cam gear coupled to the drum protrusion; And
An opening / closing control cam provided on a rotation shaft of the cam gear and slidably contacting the other side of the valve opening / closing part;
Formed crankless engine.

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