JP2002327608A - Valve device for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To interlock the operation of an intake and a discharge valves of a cylinder and a piston without using an additional interlock mechanism such as a gear. SOLUTION: An end surface of the cylinder is formed with a valve seat by providing a small-area opening part for flowing the fluid, and a valve element abutting on the valve seat is arranged outside of the valve seat. The cylinder can move in the axial direction, and the end surface of the cylinder can separate and come from/close to the valve element. When the valve seat and the valve element abut on each other to pressurize the inside of the cylinder, the end surface of the cylinder is energized to the valve element side so that the valve seat and the valve element are crimped, and the movement of the cylinder is controlled by the movement of the piston. A flow-in passage to be opened when the cylinder is lowered is provided between the upper end surface of the cylinder and the valve element, and this flow-in passage is communicated with a crank chamber through a flow-out pipe. The crank chamber is provided with a flow-in port, and the cylinder is provided with an outer flange to be brought in contact with the inner wall of an engine main body, and a discharge port is provided over the outer flange to form a valve device for an internal combustion engine.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a valve device for intake and discharge of a cylinder in an engine or an external combustion engine and a pump.

[0002]

2. Description of the Related Art A conventional engine uses an umbrella-shaped valve called a mushroom valve as a valve for intake and discharge of a cylinder. Both are linked by a cam. Since the mushroom valve has a small valve opening area and cannot have a large opening area due to its structure, it is necessary to attach a plurality of mushroom valves when improving the suction and discharge efficiency to enable high-speed rotation. The interlocking mechanism with the piston becomes complicated.
In addition, in a valve device such as a mushroom valve used in a conventional engine, the internal pressure applied to the valve body is independent of the cylinder diameter, and the valve area (the opening area of the valve seat, when a plurality of valves are provided) Is determined only by the total area). Therefore, when the valve area is increased to improve the discharge efficiency, the energy loss for opening the valve increases. In addition, the crankcase compression type two-cycle engine uses the crankcase for scavenging, and therefore has poor scavenging efficiency, and must mix lubricating oil with fuel. Therefore, it is difficult to solve the problem of the exhaust gas.

[0003]

SUMMARY OF THE INVENTION A first object of the present invention is to interlock the movement of the intake / discharge valve of the cylinder and the movement of the piston without using an additional interlocking mechanism such as a gear. A second object of the present invention is to increase the valve area while reducing the energy loss for opening the valve as much as possible, to increase the intake / exhaust efficiency, and to be suitable for high-efficiency operation. . A third object of the present invention is to improve the exhaust gas even in a two-cycle engine without using the crank chamber for scavenging, eliminating the need to mix lubricating oil with fuel.

[0004]

According to a first aspect of the present invention, there is provided a cylinder to which a fluid is supplied, a piston mounted in the cylinder, and a valve for switching suction and discharge of a pressure fluid to and from the cylinder. In the engine, a valve seat is formed by providing an opening for fluid inflow with a smaller area than the end face of the piston on the end face of the cylinder, and a valve body abutting on the valve seat is provided outside the valve seat. I do. The cylinder is movable in the axial direction, the end face of the cylinder is detachable from the valve body, and when the valve seat comes into contact with the valve body and the inside of the cylinder is pressurized, the end face of the cylinder is on the valve body side. And the valve seat and the valve element are pressed against each other, and the movement of the cylinder is controlled by the movement of the piston. Between the upper end surface of the cylinder and the valve body, there is provided an inflow passage that opens when the cylinder is lowered, and this inflow passage communicates with a crank chamber through an inflow pipe, and an inflow port is provided in the crank chamber. The cylinder is provided with an outer flange in contact with the inner wall of the engine body, and a discharge port is provided above the outer flange to constitute a valve device of the motor. The engine according to the present invention includes an internal combustion engine, an external combustion engine, and a pump. The end surface of the cylinder may be a normal cylinder in which the cylinder is integrated with the main body, or may have a structure in which a cylinder end surface member is attached to one end of the cylinder main body so as to be movable along a central axis of the cylinder.

According to a second aspect of the present invention, there is provided a cylinder to which a fluid is supplied, a piston mounted in the cylinder,
An engine having a valve for switching the suction and discharge of the pressurized fluid to and from the cylinder, wherein an end portion of the cylinder is provided with an opening for fluid inflow having a smaller area than the end surface of the piston to form a valve seat; A valve body abutting on the valve seat is disposed outside the valve seat. The cylinder is movable in the axial direction, the end face of the cylinder is detachable from the valve body, and when the valve seat comes into contact with the valve body and the inside of the cylinder is pressurized, the end face of the cylinder is on the valve body side. And the valve seat and the valve element are pressed against each other, and the movement of the cylinder is controlled by the movement of the piston. An inflow passage is provided between the upper end surface of the cylinder and the valve body that opens when the cylinder descends.The cylinder is composed of an upper cylinder and a lower cylinder. Each of the cylinders is urged upward to form a gap between the upper and lower cylinders, thereby exhausting gas. An outer flange is provided on the upper outer side of the lower cylinder, a lower portion of the outer flange is used as a fresh air inflow chamber, an inflow port is provided in the inflow chamber, and an inflow pipe communicates with the inflow path to constitute a valve device of the motor. I do.

According to a third aspect of the present invention, there is provided a cylinder to which a fluid is supplied, a piston mounted in the cylinder,
An engine having a valve for switching the suction and discharge of the pressure fluid to and from the cylinder, wherein the cylinder is movable up and down, and an opening for fluid inflow to the cylinder is provided on a bottom surface of a piston mounted in the cylinder. Forming a valve seat, providing a valve body mounting portion above the valve seat, and disposing a valve body for opening and closing the opening in the valve body mounting portion so as to be movable up and down;
The valve body has a top-end cylindrical shape in which a lower end abuts on a valve seat and an upper edge abuts on an upper edge of the valve body mounting portion. When the piston rises, a valve seat of the piston abuts on a lower end of the valve body. The valve seat is urged to the valve body side when the fluid flows between the piston and the cylinder to push up the cylinder and pressurize the cylinder, so that the valve seat is urged toward the valve body side. Configure the device.

[0007]

The basic operation of the present invention will be described with reference to FIGS. 1 to 7 applied to a two-stroke engine. FIG.
As shown in FIG. 1, in the engine 1, a cylinder 3 is installed above the crank chamber 2 so as to be able to move up and down. The cylinder 3 is urged upward by a cylinder spring 4 whose upper end is received by an outer flange 31 of the cylinder 3, and a piston 5 is mounted in the cylinder 3.
The outer edges of the ancestor and the flange 31 are in contact with the inner wall of the engine body. In the figure, reference numeral 6 denotes a crank. An opening 7 for fluid inflow is formed in the upper end surface of the cylinder 3, and the periphery of the opening 7 is a valve seat 8. And the valve seat 8
A valve body 9 that comes into contact with the valve seat 8 when the cylinder 3 is lifted is disposed above the valve body 9. An inflow passage 10 is formed between the upper end surface of the cylinder 3 and the valve body 9 and opens when the cylinder 3 descends. The inflow passage 10 is connected to the crank chamber 2 by an inflow pipe 11, Fresh air sucked from the inlet 12 of the crank chamber 2 is supplied to the cylinder 3 through the inflow path 10. Reference numeral 13 in the figure denotes a discharge port provided at a lower portion of the cylinder 3 and above the outer flange 31.

FIG. 2 shows a state in which the piston 5 is at the bottom dead center (crank angle 0 °). In this state, the lower end of the piston 5 comes into contact with the projection 14 provided at the lower end of the cylinder 3, Is pushed down by the piston 5 and the valve seat 8 and the valve element 9 are separated from each other and fresh air is discharged from the inflow passage 10 into the cylinder 3.
Since the gas flows into the inside and the discharge port 13 is also open, the residual gas in the cylinder 3 is discharged from the discharge pipe 13a, and the inside of the cylinder 3 is replaced with fresh air.

FIG. 3 shows a state at a crank angle of 60 degrees.
In this state, as the piston rises, the cylinder 3 rises with the force of the cylinder spring 4, and the valve seat 8 contacts the valve body 9 to close the opening 7, but the discharge port 13 remains open.

FIG. 4 shows a state at a crank angle of 85 degrees.
The outlet 13 is closed by the piston 5, and the inside of the cylinder enters a compression step. In this compression process, the pressure contact force between the valve seat 8 and the valve body 9 increases as the compression increases. That is, the cylinder 3 can be moved up and down, and when the piston is raised, an upward force acts on the upper end surface of the cylinder. Therefore, the valve seat 8 is pressed against the fixed valve element 9. Therefore, even if the area of the opening 7 is large, the leakage of the compressed fluid in the cylinder can be prevented with a simple valve structure.

FIG. 5 shows a state in which the crank angle is 180 degrees, and ignition is performed near the top dead center of the piston. Although the piston descends due to the pressure generated by the ignited gas, the upward force acts on the cylinder as described above, so that the pressed state of the valve seat and the valve body is maintained. The opening 7 is
The piston further descends to open the exhaust port 13 (FIG. 6 showing a state where the crank angle is 280 degrees), and the combustion gas is exhausted from the exhaust pipe 13a communicating with the engine body. The outlet 13 is open until the cylinder is pushed down by the piston.

FIG. 7 shows a state in which the crank angle is 315 degrees, and the piston 5 is in contact with the convex portion 14 at the bottom of the cylinder 3 to push down the cylinder. At this time, the valve seat 8 and the valve element 9 are separated from each other to open the opening 7, and the fresh air compressed in the crank chamber flows in, and returns to the state of FIG.

[0013]

FIG. 8 to FIG. 11 show a first embodiment of the present invention.
This is an example applied to a two-stroke engine. As shown in FIG. 8, in the engine 1, a cylinder 3 is installed above the crank chamber 2 so as to be able to move up and down. The cylinder 3 is urged upward by a cylinder spring 4 received by an outer flange 31 of the cylinder. The outer edge of the outer flange 31 is in contact with the inner wall of the engine body. The lower end of the cylinder 3 is brought into contact with the projection 15 of the engine body when descending, so that the cylinder 3 descends to the extent necessary to open the discharge port 13. A piston 5 is mounted in the cylinder 3 and is urged upward by a piston spring 16 supported at a lower end of the cylinder 3. Reference numeral 6 in the figure
Is a crank. An opening 7 for fluid inflow is formed in the upper end surface of the cylinder 3, and the periphery of the opening 7 is a valve seat 8. Above the valve seat 8, a valve body 9 which comes into contact with the valve seat 8 when the cylinder 3 is raised is arranged. An inflow passage 1 opened between the upper end surface of the cylinder 3 and the valve body 9 when the cylinder 3 descends.
0 is formed, the inflow passage 10 is connected to the crank chamber 2 by an inflow pipe 11, and fresh air sucked from an inlet 12 of the crank chamber 2 is supplied to the cylinder 3 through the inflow passage 10. ing. The piston spring 16 is stronger than the cylinder spring 4 so that when the piston spring 16 is fully extended, the piston 5 rises and closes the outlet 13.

FIG. 8 shows a state in which the piston 5 is at the bottom dead center (the crank angle is 0 degree). In this state, the piston spring 16 is compressed, the cylinder 3 is pushed by the piston 5 and descends. The seat 8 and the valve 9 are separated. Therefore, fresh air flows into the cylinder 3 from the inflow passage 10, and the discharge port 13 is also open, so that residual gas in the cylinder 3 is discharged from the discharge pipe 13a, and the inside of the cylinder 3 is replaced with fresh air. FIG. 9 shows a state in which the crank angle is 60 degrees. In this state, the piston 5 rises, but the cylinder 3 is pressed by the force of the piston spring 16 and does not rise. Therefore, the opening 7 maintains the open state, and the outlet 13 is closed by the piston 5. Therefore, since the inflow of fresh air from the opening 7 continues even after the outlet 13 is closed, so-called inertial supercharging is performed. FIG. 10 shows a state at a crank angle of 85 degrees. When the piston 5 further rises and the piston spring 16 expands, the force of the cylinder spring 4 overcomes the force of the piston spring 16, the cylinder 3 rises, and the valve seat 8 is moved. The opening 7 contacts the valve 9
Is closed, and the inside of the cylinder enters a compression process. In this compression process, the pressure contact force between the valve seat 8 and the valve body 9 increases as the compression increases. That is, the cylinder 3 can be moved up and down, and when the piston is raised, an upward force acts on the upper end surface of the cylinder. Therefore, the valve seat 8 is pressed against the fixed valve element 9. Therefore, even if the area of the opening 7 is large, leakage can be prevented with a simple valve structure. FIG.
1 indicates a state where the crank angle is 180 degrees, and ignition is performed near the top dead center of the piston. Although the piston descends due to the pressure generated by the ignited gas, the upward force acts on the cylinder as described above, so that the pressed state of the valve seat and the valve body is maintained. The opening 7 is closed until the piston is further lowered to open the discharge port 13 to discharge the combustion gas and the cylinder is pushed down by the piston.
When the piston 5 further descends, the piston spring 16
Since the lower end of the cylinder 3 depressed by the above comes into contact with the projection 15 of the main body, the piston 5 descends while compressing the piston spring 16 and returns to the state of FIG.

In the compression step, since the area of the opening 7 is smaller than the plane area of the piston 5, the axial force applied to the cylinder corresponding to the difference in the area acts in the direction of pressing the valve, and the cylinder spring 4 And the upward force obtained by the difference between the force of the piston spring 16 and the force of the piston spring 16. Therefore, as the cylinder internal pressure increases, the pressure contact force between the valve seat and the valve element increases, and the pressure of the compressed air or the next combustion gas does not leak to the outside. Further, in the above embodiment, only the piston 5 moves up while the cylinder 3 is pushed down by the action of the piston spring 16, so that the inflow can be continued with the outlet 13 closed as shown in FIG. Efficiency is improved.

[0016]

Second Embodiment FIGS. 12 to 15 show a second embodiment.
This is an example in which the present invention is applied to a two-stroke engine. In FIG. 12, a cylinder 3 is installed above the crank chamber 2 of the engine 1 so as to be able to move up and down, and a piston 5 is mounted in the cylinder 3. The cylinder 3 includes an upper cylinder 3a and a lower cylinder 3b. The upper cylinder 3a is urged downward by a valve spring 17, and the lower cylinder 3b is urged upward by a cylinder spring 4 stronger than the valve spring 17. ing. The cylinder spring 4 is received by an outer flange 31 provided above the lower cylinder 3b.
The inflow chamber 18 is formed below the outer flange 31. An opening 7 is formed in the upper end surface of the upper cylinder 3a,
The periphery of the opening 7 serves as a valve seat 8. Above the valve seat 8, a valve body 9 which comes into contact with the valve seat 8 when the upper cylinder 3a is raised is arranged. An inflow passage 10 is formed between the upper end surface of the upper cylinder 3a and the valve body 9 and opens when the upper cylinder 3a is lowered. The inflow passage 10 is connected to the inflow chamber 18 by an inflow pipe 11. The fresh air sucked from the inflow port 12 of the inflow chamber 18 is supplied to the cylinder 3 via the inflow path 10.

FIG. 12 shows a state in which the piston 5 is at the bottom dead center (the crank angle is 0 degree). In this state, the upper cylinder 3a is pushed down by the valve spring 17, and the valve seat 8 and the valve body 9 are separated. The fresh air flows away from the inflow passage 10 into the cylinder 3. On the other hand, the lower end of the piston 5 comes into contact with the convex portion 14 provided at the lower end of the lower cylinder 3b, and the lower cylinder 3b is pushed down by the piston 5 and descends, so that a gap is formed between the upper cylinder 3a and the lower cylinder 3b. Arises
Since this gap serves as the discharge port 13 and the discharge pipe 13a is open, the residual gas in the cylinder 3 is discharged, and the inside of the cylinder 3 is replaced with fresh air. When the piston 5 rises, the lower cylinder 3b rises by the force of the cylinder spring 4, comes into contact with the lower end of the upper cylinder 3a, and the outlet 13 is closed. When the piston 5 further rises, as shown in FIG. 13 (showing a state at a crank angle of 75 degrees), the upper cylinder 3
a is pushed up by the lower cylinder 3b and rises, and the valve seat 8
Abuts on the valve body 9 to close the opening 7, and the inside of the cylinder enters a compression process.

FIG. 14 shows a state where the crank angle is 180 degrees, and ignition is performed near the top dead center of the piston. Although the piston descends due to the pressure generated by the ignited and combusted gas, the cylinder 3 is subjected to an upward force as described above, so that the compressed state between the valve seat and the valve body is maintained. When the piston 5 further descends and the lower end of the piston 5 comes into contact with the projection 14 of the lower cylinder 3b, the lower cylinder 3b descends. At the same time as the discharge port 13 is opened by the lowering of the lower cylinder 3b, the combustion gas blows down and is discharged at a stretch. On the other hand, the upper cylinder 3a, which has lost the upward force due to the lowering of the lower cylinder 3b, is pushed down by the valve spring 17 when the internal pressure of the cylinder is reduced due to the discharge of the combustion gas, and the valve seat 8 is separated from the valve body 9 to open the opening. 7 opens.

FIG. 15 shows the operation when the fuel is not ignited. If the fuel is not ignited, the cylinder pressure is only the compression pressure. It is pressed, but when the piston descends, the internal pressure decreases, and the upper cylinder 3a
The discharge port 13 is opened only when the piston descends along with b and the piston descends to the vicinity of the bottom dead center. In the compression step, as in the first embodiment, as the cylinder internal pressure increases, the pressure contact force between the valve seat and the valve element increases, and the pressure of the compressed air or the next combustion gas does not leak to the outside.

In the above description, the optimum size of the discharge gap (discharge port 13) formed between the upper cylinder 3a and the lower cylinder 3b differs depending on the operating conditions, but the step of the main body that regulates the amount of downward movement of the upper cylinder is different. The position of the portion 15a can be changed so that an optimal discharge state can be obtained. When the cylinder pressure is adjusted to be completely closed when the pressure in the cylinder is zero or negative pressure, the engine can be used to reduce the engine pressure.
(Cycle engine).

In the above embodiment, as follows:
The problem of the conventional two-stroke engine is solved. (1) Since the discharge port is closed before the inlet port is closed, the outflow of fresh air is small, and supercharging can be performed, so that combustion efficiency is improved, unburned HC is also reduced, and especially low-speed torque performance is improved. . (2) Since the inflow chamber 18 is provided independently, the crank chamber 2 is not used for inflow. Therefore, the lubricating oil can be stored in the crankcase as in the case of a four-stroke engine, so that the lubricating oil does not burn together with the fuel, and carbon is attached to the ignition plug and the exhaust gas becomes blue smoke. Nor. (3) The exhaust port can be located at the end of the cylindrical part of the engine, and the exhaust heat can be evenly distributed around the cylinder, so that there is no local temperature unevenness in the cylinder itself and thermal deformation Less is. Therefore, the fitting accuracy with the piston or the piston ring can be improved, the airtightness is improved, and the leakage of the combustion gas and the lubricating oil is prevented as much as possible. (4) When the fuel is not ignited, the opening of the discharge port can be delayed to suppress the discharge, the blow-through of the fuel at the time of starting can be suppressed, and the starting performance can be improved. (5) The suction and discharge conditions during operation can be automatically adjusted. That is, when the combustion pressure during operation is low (at a low load), the fuel is discharged in a short time after ignition and the internal pressure of the cylinder is reduced. The inlet is open and emissions are suppressed. On the other hand, when the combustion pressure is high, the lowering of the upper cylinder is delayed because the time until the internal pressure is reduced by the discharge after ignition is long. Therefore, the opening time of the discharge port becomes long, and the discharge is efficiently performed. (6) By removing the pump chamber and separately installing a compressor or the like on the inflow side, the diameter of the main body can be reduced, and a multi-cylinder engine can be obtained.

[0022]

Third Embodiment An external combustion engine indicated by a reference symbol A on the left side of FIG. 16 corresponds to the third aspect, in which a piston 5 is provided with a valve seat 8. In FIG. 16, the cylinder 3 is mounted on the engine body so as to be able to move up and down. The cylinder 3 is connected to a crank 6 so that the ascending and descending motion is converted into a rotational motion and output. A piston 5 is mounted in the cylinder 3. The piston 5 has a bottomed cylindrical shape and has an opening 4 at the bottom.
7, the periphery of which forms a valve seat 8 and is urged downward by a piston spring 16. An inflow port 45 for a pressure fluid is provided at an upper portion of the engine body, and a valve body 9 is mounted below the inflow port 45. This valve is 9
Is a cylindrical body whose upper part is closed by a closing plate 9a,
The lower end thereof is in contact with the valve seat 8 of the piston, and is urged downward by a valve spring 17. The peripheral edge of the closing plate 9a abuts on a valve body mounting seat 50 formed on the engine body, and comes into contact with the valve body mounting seat 50 when the piston descends. Further, a discharge opening 51 is provided in the peripheral wall of the valve body 9 so as to communicate with the discharge port 22 of the engine body when the valve body is lowered. In the figure, reference numeral 52 denotes a heater, and 53 denotes a cooler.

Here, as shown in the figure, when the cylinder 3 is at the bottom dead center, the piston 5 is also located below. Therefore, the valve body 9 is lowered, and the valve is closed by the force of the valve spring 17, so that the pressure fluid does not flow in, the fluid in the cylinder is discharged through the opening 51 and the discharge port 22 of the valve body 9, and the fluid is released. The cylinder 3 is raised by the balance weight and inertia. When the cylinder 3 rises, the piston 5
And the valve seat 8 comes into contact with the valve body 9 to push up the valve body 9. When the valve 9 rises, the closing plate 9a of the valve 9 moves away from the mounting seat 50 of the valve, so that the inflow port 45 and the cylinder 3 communicate with each other, and the pressure fluid flows into the cylinder 3. Since the cylinder 3 is pushed down with the inflow of the pressure fluid,
The piston 5 is pushed down by the action of the piston spring 16 and separates from the valve body 9. When the piston 5 is lowered, the valve body 9 is lowered by the action of the valve spring 17, so that the opening 51 communicates with the discharge port 22 and the opening 51 communicates with the cylinder 3, so that the fluid in the cylinder is discharged. Return to the state shown in FIG.

According to this embodiment, since the cylinder itself moves with the stroke of the piston, the guide distance can be made longer with the same size of the engine main body as compared with the case where the crank is connected to the piston. Therefore, fluttering is reduced, which is particularly advantageous for a large-diameter cylinder. The pressure fluid inlet 45 and the valve body mounting seat 5
There is no flow path between 0 and the outside of the crankcase. Then, when the internal pressure of the cylinder 3 increases due to the inflow of the pressurized fluid, the piston 5 is pushed upward by the internal pressure, so that the valve seat 8 and the valve element 9 are further pressed against each other to increase the airtightness. Therefore, there is little possibility that the pressure fluid leaks to the outside of the cylinder such as the crank chamber, and an external combustion engine having a simple structure and low energy loss can be obtained. As described above, since the energy loss is small, it is also effective for small-scale power generation using wave force, volcanic gas emitted from a volcano, or the like using a slight pressure difference.

The pump indicated by reference numeral B on the right side of FIG. That is, the discharge port 22 is provided in the upper part of the pump body, and the inflow port 45 is provided below the discharge port 22. The valve body 9 has a bottomed cylindrical shape, and its bottom is open, and a spherical auxiliary valve body 46 for opening and closing the opening 54 is mounted. The piston 5 has a cylindrical portion 5b above a substrate 5a having an opening 49, and the piston 5 is urged upward by a piston spring 16 mounted between the cylindrical portion 5b and the pump body. Have been.

Here, when the cylinder 3 shown in the drawing is at the bottom dead center, the piston 5 is urged upward by the piston spring 16, so that it comes into contact with the valve body 9 and the auxiliary valve body 46 Since the cylinder 3 is lowered, the inside of the cylinder 3 is cut off from the outside, and the cylinder 3 is raised by an unbalance weight and inertia. As the cylinder 3 rises, the fluid pressure in the cylinder 3 pushes up the valve 5 and pushes up the auxiliary valve body 46, so that the opening 54 is opened.
Exhausted from 2. When the fluid is discharged, the auxiliary valve body 46 descends and the opening 54 is closed. At this time, the inlet 45
When the fluid pressure exceeds the force of the piston spring 16, the piston 5 is pushed down and the valve seat 8 is separated from the valve body 9. Therefore, since the inflow port 45 and the cylinder 3 communicate with each other, fluid accumulates in the cylinder 3 and pushes down the cylinder 3 to return to the state shown in the figure. This pump also has no danger of leakage of the pressure fluid in the cylinder to the outside, and can be used with fluids with a small pressure difference.
It is also effective for air conditioning pumps. When the engine A and the pump B are combined as shown in FIG.
It is possible to operate the engine A by the pressure fluid heated by the above, and to guide the fluid used in the engine A to the pump B to operate the pump B. Therefore, the fluid can be circulated and other than water and air. It is effective for application to an external combustion type engine using the above fluid.

[0027]

According to the present invention, since the intake / discharge valve is provided at the opening smaller than the diameter of the piston mounted on the cylinder or the diameter of the cylinder, the airtightness of the valve is increased as the cylinder internal pressure increases. It is possible to obtain a highly confidential valve device with a simple structure and increase the area of the opening to the limit of the piston diameter, so that an engine such as an engine with high discharge efficiency can be obtained. Can be. In addition, since the valve body controls the pressure of the cylinder between the cylinder and the valve seat provided on the piston, the gasket between the cylinder head and the main body found in conventional motors and pumps (many failures) It becomes unnecessary. Further, in the internal combustion engine of the present invention, the vertical movement of the cylinder is changed by changing the vertical position of the valve body. Since the piston is moved up and down at a constant distance, setting the valve body upward and setting the top dead center of the cylinder high will reduce the compression ratio in the cylinder. When the dead center is set low, the compression ratio in the cylinder is large. That is, by moving the valve body up and down, the compression ratio in the cylinder can be changed during operation of the engine to control the combustion efficiency. As described above, the valve device of the present invention can open and close the intake / discharge valve of the cylinder in conjunction with the piston with a simple structure, and enables highly efficient operation by increasing the valve area. It can be widely applied to internal combustion engines and external combustion engines regardless of two cycles or four cycles.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view illustrating the principle of the present invention.

FIG. 2 is an explanatory view showing a state in which the crank angle is 0 degree.

FIG. 3 is an explanatory view showing a state in which the crank angle is also 60 degrees.

FIG. 4 is an explanatory view showing a state in which the crank angle is 85 degrees.

FIG. 5 is an explanatory view showing a state in which the crank angle is also 180 degrees.

FIG. 6 is an explanatory diagram showing a state in which the crank angle is 280 degrees.

FIG. 7 is an explanatory view showing a state where the crank angle is 315 degrees.

FIG. 8 is a sectional view showing Embodiment 1 of the present invention.

FIG. 9 is an explanatory view showing a state in which the crank angle is also 60 degrees.

FIG. 10 is an explanatory view showing a state in which the crank angle is also 85 degrees.

FIG. 11 is an explanatory view showing a state in which the crank angle is also 180 degrees.

FIG. 12 is a sectional view showing Embodiment 2 of the present invention.

FIG. 13 is an explanatory view showing a state in which the crank angle is also 75 degrees.

FIG. 14 is an explanatory view showing a state in which the crank angle is also 180 degrees.

FIG. 15 is an explanatory view showing a state at a crank angle of 300 degrees when ignition is poor.

FIG. 16 is a sectional view showing Embodiment 3 of the present invention.

[Description of Signs] 1 Engine 2 Crankcase 3 Cylinder 3a Upper cylinder 3b Lower cylinder 3c Receiving groove 3d Cylinder main body 3e Cylinder end face body 4 Cylinder spring 5 Piston 5a Piston cylindrical part 6 Crank 7 Opening 8 Valve seat 9 Valve body 9a Closure plate of valve body 10 Inflow path 11 Inflow pipe 12 Inlet 13 Outlet 14 Convex part 15 Convex part 15a Step 16 Piston spring 17 Valve spring 18 Inflow chamber 22 Outlet 45 Inlet 46 Auxiliary valve body 50 Valve body mounting Seat 51 Opening 52 Heater 53 Cooler 54 Opening

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Claims (3)

[Claims] 1. An engine comprising a cylinder to which a fluid is supplied, a piston mounted in the cylinder, and a valve for switching between suction and discharge of a pressurized fluid to and from the cylinder. A valve seat is formed by providing an opening for fluid inflow with a smaller area than the end surface of the valve seat, a valve body abutting on the valve seat is arranged outside the valve seat, and the cylinder is movable in the axial direction. The end face of the cylinder is detachable from the valve body, and when the valve seat and the valve body come into contact with each other and the inside of the cylinder is pressurized, the end face of the cylinder is urged toward the valve body and the valve seat and the valve are opened. When the body is press-fitted, the movement of the cylinder is controlled by the movement of the piston, and an inflow passage which is opened when the cylinder descends is provided between the upper end surface of the cylinder and the valve body. Both The inflow passage communicates with the crank chamber through an inflow pipe, the crank chamber is provided with an inflow port, the cylinder is provided with an outer flange in contact with the inner wall of the engine body, and the outer flange is provided with a discharge port above the outer flange. Movable valve device 2. An engine comprising a cylinder to which a fluid is supplied, a piston mounted in the cylinder, and a valve for switching between suction and discharge of a pressurized fluid to and from the cylinder, wherein a piston is provided on an end face of the cylinder. A valve seat is formed by providing an opening for fluid inflow with a smaller area than the end surface of the valve seat, a valve body abutting on the valve seat is arranged outside the valve seat, and the cylinder is movable in the axial direction. The end face of the cylinder is detachable from the valve body, and when the valve seat and the valve body come into contact with each other and the inside of the cylinder is pressurized, the end face of the cylinder is urged toward the valve body and the valve seat and the valve are opened. Body and press-fit, the movement of the cylinder is controlled by the movement of the piston, between the upper end surface of the cylinder and the valve body is provided an inflow passage that opens when the cylinder descends, Siri The upper cylinder is constituted by an upper cylinder and a lower cylinder, the upper cylinder is urged downward, and the lower cylinder is urged upward, so that a gap is formed between the upper and lower cylinders, so that exhaust is performed,
A valve device for a motor, wherein an outer flange is provided on the upper outer side of the lower cylinder, a lower portion of the outer flange is used as an inflow chamber for fresh air, an inflow port is provided in the inflow chamber, and the inflow pipe communicates with the inflow path. 3. An engine comprising a cylinder to which a fluid is supplied, a piston mounted in the cylinder, and a valve for switching suction and discharge of a pressurized fluid to and from the cylinder, wherein the cylinder is vertically movable, An opening for fluid inflow into the cylinder is provided on the bottom surface of the piston mounted in the cylinder to form a valve seat, a valve body mounting portion is provided above the valve seat, and the opening is provided in the valve body mounting portion. A valve body that opens and closes a part is disposed so as to be able to move up and down. When the valve seat of the piston comes into contact with the lower end of the valve body and pushes up the valve body, fluid flows between the piston and the cylinder to push up the cylinder, and when the inside of the cylinder is pressurized, the valve seat Energized to the valve body side Engine valve device