JP2006016983A - Communication connecting/disconnecting means for engine for connecting/disconnecting communication between intake or exhaust port and combustion chamber - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a communication connecting/disconnecting means for an engine which can connect/disconnect communication between a port and a combustion chamber without employing reciprocating motion as with a valve for intake or exhaust employed for a conventional engine. <P>SOLUTION: A communication connecting/disconnecting means for an engine for connecting/disconnecting communication between a port for intake or exhaust and a combustion chamber, is equipped with a second member in which a port opening connected to the port and a combustion chamber opening connected to the combustion chamber, and a first member which has an inside flow passage and which is turnable around a first shaft with respect to the second member. In a communication turning range which is the prescribed turning range of the first member with respect to the second member therearound, the port and the combustion chamber are communicated to each other through the medium of the inside flow passage. When the first member is out of the communication turning range, the communication between the port and the combustion chamber is prohibited. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

  The present invention relates to a communication intermittent means for an engine that interrupts communication between an intake or exhaust port and a combustion chamber, and more particularly, reciprocation such as an intake or exhaust valve used in a conventional engine. The present invention relates to a communication interrupting means for an engine that interrupts communication between a port and a combustion chamber without using motion.

Engines are widely used as a power source for vehicles such as automobiles such as four or two wheels, ships, trains, airplanes, and machines such as mowers, pumps, blowers, and the like. Various types of engines are used for this engine, and the most common one is a four-cycle engine.
In a 4-cycle engine, the mixture of fuel and air is introduced from the intake port into the combustion chamber when the intake valve opens and the piston descends (intake stroke), and the intake valve closes and the piston ascends to raise the mixture. When the piston reaches the upper limit, the mixture is ignited and the mixture is combusted and expanded (expansion stroke). Finally, when the piston reaches the lower limit, the exhaust valve opens and the combustion gas increases as the piston rises. Is expelled from the combustion chamber to the exhaust port (exhaust stroke) and the exhaust valve is closed. In order for the engine to operate in this manner, it is necessary to introduce an air-fuel mixture into the combustion chamber and discharge combustion gas from the combustion chamber. These valves are opened and closed.

These intake valves and exhaust valves are normally urged in a closing direction by a valve spring (normally closed), and camshafts of camshafts (cam protrusions) rotated by the rotation of the crankshaft are affected by the urging force. By pushing the valve directly or indirectly against the valve, the valve is opened (the valve protrudes toward the inside of the cylinder head), and when the camshaft further rotates and the cam crest does not push the valve, the biasing force again The valve is closed. In other words, the intake valves and exhaust valves that are currently used intermittently communicate between the port and the combustion chamber by reciprocating motion (see, for example, Patent Document 1 and Non-Patent Document 1).
In order to increase the engine output, it is necessary to increase the engine speed and reduce the frictional resistance.

JP 2001-55911 A (FIGS. 1 and 6) GP Planning Center "How is the car mechanics engine?" Grand Prix Publishing Co., Ltd., March 13, 2000, p. 66-92

However, in the conventional intake and exhaust valves by reciprocating motion, a large frictional resistance (for example, the cam surface of the camshaft and the camshaft) is used to convert the rotational motion of the crankshaft to reciprocating motion to drive these valves. Friction generated between the sliding member (for example, the end of the valve stem) occurs.
In the intake valve and the exhaust valve by reciprocating motion, when the engine speed increases (that is, when the speed of the reciprocating motion of the valve increases), the valve that has been pushed by the cam crest is no longer pressed by the cam crest. However, if the valve spring does not return to the closed position (valve bounce) or if the valve spring force is weak, the valve will not be able to follow the cam crest (valve jump), and the valve motion and valve spring will resonate (valve surging). ) And other problems arise. When these problems occur, the valve opening / closing timing is out of order, resulting in a decrease in engine output and efficiency, or sometimes a collision between the valve and the piston causing damage to the engine.
Moreover, in order to eliminate or reduce these problems, if a strong valve spring is used, the resistance for pushing the valve spring increases, so the frictional resistance increases, and the resulting engine output decreases, Wear of the valve seat increases.

  Therefore, in the present invention, the communication for the engine can be intermittently connected between the port and the combustion chamber without using the reciprocating motion such as the intake or exhaust valve used in the conventional engine. It aims to provide a means.

  The “communication on / off means for the engine that interrupts the communication between the intake or exhaust port and the combustion chamber” (hereinafter referred to as “this means”) of the present invention is defined between the intake or exhaust port and the combustion chamber. And a second member in which a port port connected to the port and a combustion chamber port connected to the combustion chamber are disposed, and an internal flow path. And a first member rotatable about the first axis with respect to the second member, and the predetermined rotation of the first member relative to the second member around the first axis. The port and the combustion chamber communicate with each other through the internal flow path in the communication rotation range, and the port and the combustion chamber are prohibited from communication when the first member is outside the communication rotation range. It is the communication intermittent means.

This means is a communication intermittent means for the engine for interrupting the communication between the intake or exhaust port and the combustion chamber, like the reciprocating intake or exhaust valve used in the conventional engine.
The means includes a first member and a second member, and the first member is rotatable about the first axis with respect to the second member. The first member has an internal flow path, and the internal flow path is at least two open ends (they exist on the surface of the first member. These open ends communicate with each other through the internal flow path). have. Further, the second member is provided with a port port connected to the port and a combustion chamber port connected to the combustion chamber.
When the first member rotates around the first axis with respect to the second member, the internal flow path is within a communication rotation range that is a predetermined rotation range of the first member relative to the second member around the first axis. The port and the combustion chamber communicate with each other (ie, the open end of the internal flow path communicates with the port port, and the other open end of the internal flow channel communicates with the combustion chamber port so that the port and the combustion chamber communicate with each other through the internal flow channel. And the communication between the port and the combustion chamber is prohibited when the first member is outside the communication rotation range (that is, one or both of the port port and the combustion chamber port are connected to the internal flow path). The communication between the port and the combustion chamber is prohibited by disconnection from the open end.
Here, “rotation” of the first member around the first axis with respect to the second member refers to alternately rotating in both forward and reverse directions (rotation angle is less than 360 degrees) and in both forward and reverse directions. It is a concept that includes all of rotating alternately (rotating angle of 360 degrees or more) and rotating in the same direction (rotating angle of 360 degrees or more) (that is, rotation and rotation around the first axis). Including everything in motion.)
In this way, this means rotates the first member around the first axis with respect to the second member without using reciprocating motion such as an intake or exhaust valve used in conventional engines. Thus, communication between the port and the combustion chamber can be interrupted. Therefore, according to the present means, the above-described problems (for example, for converting the rotational motion into the reciprocating motion) that may occur when the reciprocating motion such as the intake or exhaust valve used in the conventional engine is used. Friction resistance, valve bounce, valve jump, valve surging, engine damage due to collision between valve and piston, etc.) can be avoided.

The first member has a first surface formed by at least a part of a rotation surface centered on the first axis, both ends of the internal flow path exist on the first surface, and the second member has Even if the port has a second surface along the first surface, and the port port and the combustion chamber port are present on the second surface (hereinafter referred to as “rotating surface main means”). Good.
By doing so, the first surface of the first member and the second surface of the second member face each other well (the second surface has a shape along the first surface). Since the first surface is formed by at least a part of the rotation surface about the first axis, the first member can be rotated well about the first axis with respect to the second member. Since both ends of the internal flow path (two of the open ends) exist on the first surface and the port port and the combustion chamber port exist on the second surface, the first surface and the second surface face each other. In the communication rotation range, the port and the combustion chamber communicate with each other through the internal flow path (that is, one end at both ends of the internal flow path communicates with the port port, and the other end at both ends of the internal flow path burns. By communicating with the chamber port, the port and the combustion chamber communicate with each other through the internal flow path.) Outside the communication rotation range, one or both of the port port and the combustion chamber port are disconnected from both ends of the internal flow path. By being blocked by the first surface, communication between the port and the combustion chamber is prohibited.
The “both ends of the internal flow path” referred to here is, of at least two open ends of the internal flow path, an open end with which the port port can communicate, and an open end with which the combustion chamber port can communicate, (I.e., the two open ends where the port port and the combustion chamber port can communicate simultaneously).

In the case of the rotating surface main means, the second member may support the first member by the second surface so as to be rotatable.
In this way, if the second surface of the first member supports the first surface of the first member and the second member supports the first member, the first member can be rotatably supported. It is not necessary to provide separate means, and the load on the separate means can be reduced (the number and scale of the separate means can be reduced).

In the case of the rotating surface main means, the first member may have a right circular column shape with the first axis as an axis, and the first surface may be formed by a side surface of the right circular column.
Since the processing for forming a right circular cylinder shape can usually be performed easily and accurately, the accuracy of the first member can be increased and the manufacturing cost can be reduced.

In this means, the rotation of the first member relative to the second member about the first axis may be rotation in the same direction.
By doing so, it is only necessary to always rotate the first member in a certain direction, so that a mechanism for rotating (rotating) the first member can be easily configured. For example, when using a timing belt (cogged belt) and a pulley as in the case of driving a conventional camshaft, a timing chain and a sprocket are used to reduce the rotation of the crankshaft at a predetermined reduction ratio. In this case, the first member may be rotated via a combination of a plurality of gears.

The internal flow path may be formed along a straight line.
In this way, the gas flowing between the port and the combustion chamber (if the port is an intake port, it is an air-fuel mixture flowing from the intake port to the combustion chamber, and if the port is an exhaust port, the gas flows from the combustion chamber. The combustion gas flowing to the exhaust port) can be reduced in resistance when flowing through the internal space, so that the efficiency and output of the engine in which this means is disposed can be increased.

At least one of the first member and the second member may have an internal space filled with metallic sodium.
Since the first member and the second member are heated by the heat from the engine in which this means is disposed and the heat from the combustion gas flowing through these members, it is necessary to promote heat dissipation. Here, the metallic sodium becomes liquid when the temperature becomes high, and moves around in the internal space with the movement of the first member or the second member in which the internal space is formed. The movement of the liquid metal sodium promotes the heat transfer of the part along the internal space (sodium heated by the high temperature part of the internal space is cooled by the low temperature part of the internal space, so that the sodium transfers the heat. ), Preventing local overheating of the first member or the second member and promoting heat dissipation.

The both ends of the internal flow path may be formed substantially symmetrical with respect to the first axis.
In this way, when the first member rotates with respect to the second member around the first axis, both ends of the internal flow path are alternately located at the same position each time it rotates 180 degrees, so that it does not rotate 360 degrees. As compared with the case where both ends of the internal flow path do not come to the same position, 1/2 rotation of the first member is sufficient. For this reason, the rotation speed of the first member can be suppressed, the frictional resistance accompanying the rotation can be reduced, and the load of the support means for rotatably supporting the first member can be reduced.

  As described above, this means is provided by rotating the first member around the first axis with respect to the second member without using reciprocating movement such as an intake or exhaust valve used in a conventional engine. The communication between the combustion chamber and the combustion chamber can be interrupted. Therefore, this means can be used for both the intake intermittent means for interrupting communication between the intake port and the combustion chamber and the exhaust intermittent means for interrupting communication between the exhaust port and the combustion chamber. .

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. However, the present invention is not limited by these.

FIG. 1 is a partial cross-sectional view of an engine (hereinafter referred to as “the present engine”) 11 having this means (a cross section perpendicular to a rotation axis of a crankshaft (not shown) of the engine 11). FIG. 2 is a cross-sectional view taken along the line AA of FIG. 1 (a piston 92, a connecting rod 93, a pulley 33a, etc., which will be described later). 3 is a cross-sectional view of the first members 31a and 31b (showing a cross section perpendicular to a straight line formed along internal flow paths 32a and 32b to be described later). For 31a, the cross-sectional position is indicated by BB in FIG.
The engine 11 is a four-cycle engine using gasoline as fuel, and is the same as the conventional four-cycle engine except that the intake valve, the exhaust valve, the camshaft, etc. used in the conventional engine are replaced by this means. It has the structure of. That is, a piston 92 is slidably fitted inside a cylindrical cylinder 91, and a crankshaft (not shown) and the piston 92 are connected by a connecting rod 93. A water jacket 91 w through which cooling water flows is formed in the wall of the cylinder 91. A combustion chamber 15 is formed by being surrounded by the cylinder head 94 and the head of the piston 92. A spark plug 95 (spark plug) is attached to the cylinder head 94, and one end of the spark plug 95 (ignition part that generates a spark) is located in the combustion chamber 15. The cylinder head 94 includes first members 31a and 31b and second members 41a and 41b. In these drawings, the flow path of the cooling water (water jacket), the flow path of the circulating oil, the bolts and nuts are omitted as appropriate for easy illustration and understanding. Fixing etc. are done.

As will be described later, this means allows the port 13 and the combustion chamber 15 to communicate with each other in accordance with the intake timing (the communication between the port 13 and the combustion chamber 15 is referred to as “intake communication”. The combustion chamber 15 and the port 17 communicate with each other in accordance with the exhaust timing (the communication between the port 17 and the combustion chamber 15 is referred to as “exhaust communication.” Except for the exhaust timing, this exhaust communication is established. Will be refused.) In the drawing, the ports ahead of the second members 41a and 41b are not shown (in fact, the ports ahead of the second members 41a and 41b are the intake valves and exhausts by the conventional reciprocating motion. It has the same structure as the port ahead of the cylinder head of a 4-cycle engine using a valve.)
As a result, the engine 11 has a mixture of fuel (gasoline) and air from the intake port 13 through the combustion chamber 15 by intake communication at the intake timing, as in a conventional four-cycle engine using an intake valve and exhaust valve by reciprocating motion. After the intake air communication is cut off, the air-fuel mixture is compressed by the piston 92 ascending (compression stroke), and the air-fuel mixture is ignited by the spark plug 95 when the piston 92 reaches almost the upper limit. Then, the air-fuel mixture is combusted and expanded, and the piston 92 descends (expansion stroke). When the piston 92 reaches near the lower limit, the exhaust timing is entered and the exhaust gas is exhausted and the combustion gas is expelled from the combustion chamber 15 to the exhaust port 17 (exhaust stroke), and then the exhaust communication is cut off. By repeating such a cycle, the engine 11 can rotate a crankshaft (not shown).
In the following, the present engine 11 will be mainly described with respect to this means different from the conventional engine, and the other description will be omitted.

This means includes an intake intermittent means 21a for intermittently connecting the intake port 13 and the combustion chamber 15 of the engine 11, and an exhaust intermittent means 21b for intermittently connecting the exhaust port 17 and the combustion chamber 15. Both are arranged. The basic structure of both the intake intermittent means 21a and the exhaust intermittent means 21b is the same.
This means includes first members 31a and 31b (those constituting the intake intermittent means 21a are indicated with a subscript "a" as 31a, and those constituting the exhaust intermittent means 21b are indicated with a subscript "b" and 31b. And the second members 41a and 41b (here, the second member 41a and the second member 41b are integrally formed together with the mounting portion 94a of the spark plug 95, and the cylinder head). 94), pulleys 33a and 33b that are non-rotatably attached to one end of the first members 31a and 31b, pulleys that are attached to the pulleys 33a and 33b and the crankshaft (whichever And a timing belt 35 (cogged belt) that is stretched over the belt.

The first members 31a and 31b have a right cylindrical shape with a first axis (indicated by a dotted line C in FIGS. 2 and 3 and indicated as a point C in FIG. 1) as an axis. Internal flow paths 32a and 32b are formed along a straight line orthogonal to the axis (the dotted line D in FIG. 2 for the first member 31a). The internal flow paths 32a and 32b are relative to the straight line orthogonal to the first axis (the first member 31a is a dotted line D in FIG. 2, which is perpendicular to the plane shown in FIG. 3). The shape of the vertical cross section is the same at any position along the straight line, and both ends of the internal flow paths 32a and 32b (here, the internal flow paths 32a and 32b both have two open ends) are opened. (That is, each of the internal flow paths 32a and 32b is provided so as to penetrate the first members 31a and 31b formed therein).
The first members 31a and 31b have a plurality of internal spaces 34a and 34b in which metallic sodium is enclosed.
The first members 31a and 31b may be made of a material used to form an intake or exhaust valve used in a conventional engine.

The second members 41a and 41b have an elongated rectangular parallelepiped shape, and are formed into a right circular cylinder shape that is slightly larger than the diameter of the right circular cylinder formed by the first members 31a and 31b. ) Internal fitting holes (both ends open). A slight gap is actually formed between the outer surface of the first member 31a, 31b and the inner surface of the inner fitting hole of the second member 41a, 41b, but for ease of illustration. Illustration of the gap is omitted (in fact, lubricating oil is supplied to the gap).
Each of the first members 31a and 31b is inserted into the internal fitting holes of the second members 41a and 41b except for the vicinity of both end portions, and the first shaft (see FIGS. 2 and 3) with respect to the second members 41a and 41b. Middle, dotted line C. It can be rotated (rotated here) around point C) in FIG.
Note that, here, the inner surfaces of the inner fitting holes of the second members 41a and 41b are formed by the adhered liner sheets 41a1 and 41b1, but this is not necessarily essential. The second members 41a and 41b are made of a material used to form a conventional engine cylinder head, and the liner seats 41a1 and 41b1 are made of a material used to form a conventional valve seat. May be.

In a predetermined rotation range (communication rotation range) of the first members 31a and 31b with respect to the second members 41a and 41b around the first axis (dotted line C in FIG. 2 and FIG. 3; point C in FIG. 1). The combustion chambers connected to the port ports 43a and 43b connected to the ports 13 and 17 and the combustion chamber 15 so as to correspond to the positions of both ends of the internal flow paths 32a and 32b formed in the first members 31a and 31b. The openings 45a and 45b are formed in the second members 41a and 41b.
Therefore, a predetermined rotation range of the first members 31a and 31b with respect to the second members 41a and 41b around the first axis (communication rotation range. That is, one end of both ends of the internal flow paths 32a and 32b and the port port. 43a, 43b and the ports 13, 17 through the internal flow paths 32a, 32b in the range where the other end of the internal flow paths 32a, 32b communicates with the combustion chamber ports 45a, 45b). The combustion chamber 15 communicates with the combustion chamber 15. Specifically, the port 13 and the combustion chamber 15 communicate with each other via the port port 43a, the internal flow path 32a, and the combustion chamber port 45a, and the combustion chamber 15 communicates with the port port 43b, the internal flow path 32b, and the combustion chamber port 45b. The port 17 communicates.
Then, one end of both ends of the internal flow paths 32a and 32b is outside the predetermined rotation range (communication rotation range) of the first members 31a and 31b with respect to the second members 41a and 41b around the first axis. At least one of the communication with the port ports 43a and 43b and the communication between the other end of the internal flow paths 32a and 32b and the combustion chamber ports 45a and 45b (of course, both may be used). In the range that is cut off, communication between the ports 13 and 17 and the combustion chamber 15 is prohibited. Here, both the port ports 43a and 43b and the combustion chamber ports 45a and 45b are detached from both ends of the internal flow paths 32a and 32b, and are closed by the side surfaces of the right circular cylinder formed by the first members 31a and 31b. Communication between 13, 17 and the combustion chamber 15 is prohibited.
In FIG. 1, the port 13 and the combustion chamber 15 communicate with each other, and the communication between the port 17 and the combustion chamber 15 is prohibited. Further, displacement of the first members 31a and 31b in the first axial direction relative to the second members 41a and 41b is limited by a bearing (not shown), and the first shaft of the first members 31a and 31b relative to the second members 41a and 41b. The position in the direction is maintained.

Thus, the rotation of the first members 31a, 31b relative to the second members 41a, 41b around the first axis (dotted line C in FIG. 2 and point C in FIG. 1) causes the ports 13, 17 and Communication with the combustion chamber 15 can be freely allowed or prohibited. For this reason, the rotation of the first members 31a and 31b with respect to the second members 41a and 41b around the first shaft causes the port 13 to be synchronized with the intake timing in the same manner as an intake valve and an exhaust valve by reciprocating movements conventionally used. And the combustion chamber 15 are communicated (intake communication), and the combustion chamber 15 and the port 17 can be communicated in accordance with the exhaust timing (exhaust communication).
Various methods are conceivable for rotating the first member 31a to communicate with the intake timing in accordance with the intake timing and to rotate the first member 31b to communicate with the exhaust timing in accordance with the exhaust timing. You may use the method of rotating the cam shaft for driving the intake valve and exhaust valve by reciprocation. That is, the first member 31a, 31b is rotated in accordance with the rotation of a crankshaft (not shown) of the engine 11, for example, when a timing belt (cogged belt) and a pulley are used, or when a timing chain and a sprocket are used. A case where a plurality of gears are combined can be exemplified. Here, as described below, a timing belt (cogged belt) and a pulley are used.

  The pulleys 33a and 33b that are non-rotatably attached to one end of the first members 31a and 31b are rotated by the timing belt 35 (cogged belt) as the crankshaft rotates (timing belt). 35 is spanned between pulleys (not shown) attached to the crankshaft and pulleys 33a and 33b, so that when the crankshaft is rotated, the pulleys 33a and 33b are rotated). Thus, the first members 31a and 31b are rotated with the rotation of the crankshaft. Here, the rotation shaft of the crankshaft, the rotation shaft of a pulley (not shown) attached to the crankshaft, the rotation shafts of the pulleys 33a and 33b, and the rotation shafts of the first members 31a and 31b (here, the first shaft ( 2 and 3, the dotted line C. The point C)) in FIG.

The number of teeth of a pulley (not shown) attached to a crankshaft (not shown) (the number of teeth meshed with the teeth provided on the inner periphery of the timing belt 35 provided on the outer periphery of the pulley) and the pulleys 33a and 33b The number of teeth (the number of teeth provided on the outer circumference of the pulleys 33a and 33b and the number of teeth meshing with the inner circumference of the timing belt 35) is 1/4 of the number of revolutions of the crankshaft. Thus, the pulleys 33a and 33b are rotated. Along with the rotation of the pulleys 33a and 33b, the first members 31a and 31b are also rotated at a rotation speed that is 1/4 of the rotation speed of the crankshaft.
Further, the ports 13 and 17 communicate with the combustion chamber 15 in accordance with the intake and exhaust timing so that the intake and exhaust valves used in the conventional engine are opened and closed in accordance with the intake and exhaust timing. Thus, the first members 31a and 31b are rotated. Specifically, the port 13 and the combustion chamber 15 communicate with each other via the port port 43a, the internal flow path 32a, and the combustion chamber port 45a in accordance with the intake timing (this communication is cut off at other than the intake timing). According to the exhaust timing, the combustion chamber 15 and the port 17 communicate with each other through the port port 43b, the internal flow path 32b, and the combustion chamber port 45b (this communication is interrupted except at the exhaust timing). To be. Further, in order to allow sufficient intake time and exhaust time, communication between one end of both ends of the internal flow paths 32a and 32b and the port ports 43a and 43b and other of both ends of the internal flow paths 32a and 32b are possible. The shapes of both ends of the internal flow paths 32a and 32b, the port ports 43a and 43b, and the combustion chamber ports 45a and 45b are determined so that the communication between the end and the communication with the combustion chamber ports 45a and 45b continues for a predetermined time. Yes. The shapes of the internal flow paths 32a and 32b, the port ports 43a and 43b, the combustion chamber ports 45a and 45b shown in FIG. 1, and the rotation angles of the first member 31a and the first member 31b may be changed as appropriate. Needless to say.

As described above, this means (device) includes the intake intermittent means 21 a (intake intermittent means) for intermittently connecting the intake port 13 and the combustion chamber 15 of the engine 11, the exhaust port 17 and the combustion chamber 15. And an exhaust intermittent means 21b (intake intermittent apparatus) for intermittently communicating with each other.
This means as the intake intermittent means 21 a is an engine communication intermittent means for interrupting communication between the intake port 13 and the combustion chamber 15, and is connected to the port port 43 a connected to the port 13 and the combustion chamber 15. It has the 2nd member 41a by which the combustion chamber port 45a connected is arrange | positioned, and the internal flow path 32a, A 1st axis | shaft (dotted line C in FIG.2 and FIG.3) with respect to this 2nd member 41a. 1 is a predetermined rotation range of the first member 31a with respect to the second member 41a around the first axis. The port 13 and the combustion chamber 15 communicate with each other through the internal flow path 32a in the communication rotation range, and the communication between the port 13 and the combustion chamber 15 is prohibited when the first member 31a is outside the communication rotation range. It is a continuous interruption means.
And this means which is the intake intermittent means 21a is a first surface formed by at least a part of a rotation surface centering on the first axis (dotted line C in FIG. 2 and FIG. 3, point C in FIG. 1). The first member 31a has a right columnar side surface formed by the first member 31a here, and both ends of the internal flow path 32a have the first surface (a right columnar shape formed by the first member 31a). The second member 41a is a second surface (the second member 41a has a first member 31a) along the first surface (a side surface of a right circular cylinder formed by the first member 31a). And the port port 43a and the combustion chamber port 45a are formed on the second surface (the inner surface of the inner fitting hole in which the first member 31a is fitted). Exist.

And in this means which is the intake intermittent means 21a, the second member 41a can rotate the first member 31a by the second surface (the inner surface of the inner fitting hole into which the first member 31a is fitted). To support.
As described above, in this means serving as the intake air interrupting means 21a, the first member 31a has a right cylindrical shape with the first axis as an axis, and the first surface is formed by a side surface of the right circular cylinder. Is.
Further, in this means, which is the intake intermittent means 21a, the rotation of the first member 31a relative to the second member 41a around the first axis is rotation in the same direction.
The internal flow path 32a is formed along a straight line (a straight line perpendicular to the first axis (dotted line D in FIG. 2)).
In addition, the first member 31a has an internal space 34a in which metallic sodium is enclosed.
The both ends of the internal flow path 32a are formed substantially symmetrical with respect to the first axis.

Similarly, this means, which is the exhaust intermittent means 21b, is an engine continuous intermittent means for interrupting communication between the exhaust port 17 and the combustion chamber 15, and includes a port port 43b connected to the port 17 and the combustion chamber. 15 includes a second member 41b in which a combustion chamber port 45b connected to the first member 15 is disposed, and an internal flow path 32b, and a first axis with respect to the second member 41b (dotted line C in FIG. A first member 31b rotatable about the point C), and communicating with the second member 41b around the first axis within a predetermined rotation range of the first member 31b. The port 17 and the combustion chamber 15 communicate with each other through the internal flow path 32b in the rotation range, and the communication between the port 17 and the combustion chamber 15 is prohibited when the first member 31b is outside the communication rotation range. It is the communication intermittent means.
And this means which is the exhaust intermittent means 21b is a first surface (here, a first surface formed by at least a part of a rotation surface centered on the first axis (dotted line C in FIG. 3, point C in FIG. 1). The first member 31b has a right columnar side surface formed by the first member 31b, and both ends of the internal flow path 32b are on the first surface (a right columnar side surface formed by the first member 31b). The second member 41b has a second surface (a second member 41b, which the first member 31b has) fitted along the first surface (a side surface of a right circular cylinder formed by the first member 31b). The inner surface of the inner fitting hole), and the port port 43b and the combustion chamber port 45b exist on the second surface (the inner surface of the inner fitting hole into which the first member 31b is fitted).

And in this means which is the exhaust intermittent means 21b, the second member 41b can rotate the first member 31b by the second surface (the inner surface of the inner fitting hole into which the first member 31b is fitted). To support.
As described above, in this means, which is the exhaust intermittent means 21b, the first member 31b has a right circular cylinder shape with the first axis as an axis, and the first surface is formed by a side surface of the right circular cylinder. Is.
Further, in this means as the exhaust intermittent means 21b, the rotation of the first member 31b with respect to the second member 41b around the first axis is rotation in the same direction.
Further, the internal flow path 32b is formed along a straight line (a straight line orthogonal to the first axis).
In addition, the first member 31b has an internal space 34b in which metallic sodium is enclosed.
The both ends of the internal flow path 32b are formed substantially symmetrical with respect to the first axis.

  In this way, by using the intake intermittent means 21a (intake intermittent apparatus) and the exhaust intermittent means 21b, which are the present means, in an engine, without using reciprocating motion such as an intake or exhaust valve used in a conventional engine, The communication between the ports 13 and 17 and the combustion chamber 15 can be interrupted by the rotation of the first members 31a and 31b around the first axis with respect to the second members 41a and 41b. Therefore, according to the present means, problems that may occur when using a reciprocating motion such as an intake or exhaust valve used in a conventional engine (for example, a frictional resistance for converting a rotational motion into a reciprocating motion, a valve Bounce, valve jump, valve surging, engine breakage due to collision between valve and piston, etc.) can be avoided. In addition, since this means does not use anything that becomes resistance to circulating intake or exhaust, such as an intake or exhaust valve used in a conventional engine, this means smoothly performs intake and exhaust. Efficiency can be improved. Further, since a complicated configuration (for example, a camshaft, a rocker arm, a valve spring, etc.) for driving an intake or exhaust valve by reciprocating motion used in a conventional engine is not required, the use of this means The durability and reliability can be significantly improved, and the engine can be reduced in weight, simplified, reduced in noise, reduced in cost, improved in fuel efficiency, improved in output, and increased in engine speed. In addition, this means can also solve the noise and output reduction caused by the deviation of the valve clearance when using the intake or exhaust valve by reciprocating motion. In addition, the cross-sectional area of the flow path through which the intake and exhaust flows (area in the cross section perpendicular to the flow direction) is also easily increased as compared with the case of using a conventional reciprocating intake or exhaust valve. be able to.

It is a partial cross section figure of an engine provided with this means. It is AA sectional drawing of FIG. It is sectional drawing of a 1st member.

Explanation of symbols

11 This engine 13 (Intake) port 15 Combustion chamber 17 (Exhaust) port 21a Intake intermittent means 21b Exhaust intermittent means 31a, 31b First member 32a, 32b Internal flow path 33a, 33b Pulley 34a, 34b Internal space 35 Timing belt 41a, 41b Second member 41a1, 41b1 Liner sheet 43a, 43b Port port 45a, 45b Combustion chamber port 91 Cylinder 91w Water jacket 92 Piston 93 Connecting rod 94 Cylinder head 94a (Ignition plug) mounting portion 95 Ignition plug

Claims (9)

A communication intermittent means for an engine for intermittently communicating between an intake or exhaust port and a combustion chamber,
A second member in which a port port connected to the port and a combustion chamber port connected to the combustion chamber are disposed;
A first member having an internal flow path and rotatable about the first axis with respect to the second member;
With
The port communicates with the combustion chamber through the internal flow path in a communication rotation range that is a predetermined rotation range of the first member relative to the second member around the first axis, and the first member is Communication intermittent means for prohibiting communication between the port and the combustion chamber outside the communication rotation range. The first member has a first surface formed by at least a part of a rotation surface centered on the first axis;
Both ends of the internal flow path exist on the first surface,
The second member has a second surface along the first surface;
The communication intermittent means according to claim 1, wherein the port port and the combustion chamber port are present on the second surface.         The communication intermittent means according to claim 2, wherein the second member supports the first member by the second surface so as to be rotatable.         4. The communicating intermittent means according to claim 2, wherein the first member has a right circular column shape with the first axis as an axis, and the first surface is formed by a side surface of the right circular column. .         5. The communicating intermittent means according to claim 1, wherein the rotation of the first member relative to the second member about the first axis is rotation in the same direction.         The communication intermittent means according to any one of claims 1 to 5, wherein the internal flow path is formed along a straight line.         The communication intermittent means according to any one of claims 1 to 6, wherein at least one of the first member and the second member has an internal space in which metallic sodium is sealed.         The communicating intermittent means according to any one of claims 1 to 7, wherein the both ends of the internal flow path are formed substantially symmetrically with respect to the first axis.         9. At least one of an intake intermittent means for interrupting communication between the intake port and the combustion chamber and an exhaust intermittent means for interrupting communication between the exhaust port and the combustion chamber. An engine comprising the communication intermittent means according to claim 1.

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