JPH0639058Y2 - engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION [Industrial field of application] The present invention supports a cylinder case such that the cylinder case is slidably rotatable with respect to an inner wall of a main body case, and an intake / exhaust port provided in a cylinder is rotated as the cylinder case rotates. A cam plate provided on the main body case side so as to sequentially circulate through an exhaust port, an intake port, a fuel injection port or an ignition port formed at a predetermined phase on the sliding contact surface on the main body case side. Relates to an engine configured to guide the piston forward and backward on the inner peripheral surface thereof.

[Conventional technology]

A general four-cycle reciprocating engine is of a type in which reciprocating motion of a piston is converted into rotational motion by a connecting rod and a crankshaft to take out power, but the connecting rod and the crankshaft are omitted to reciprocate the piston as described above. An engine is considered in which the movement is directly converted into the rotational movement of the cylinder case to reduce the overall size and weight, and one example of the engine is Japanese Patent Publication No. 47-26521 and Japanese Patent Publication No. 48-26521. It is disclosed in Japanese Patent No. 1044.

Then, in the engine as described above, the operation corresponding to the opening and closing of the intake / exhaust valve is performed as follows. In other words, the intake and exhaust ports provided on the cylinder sequentially overlap with the exhaust port and intake port on the body case side to communicate with each other, so that the intake and exhaust ports of the cylinder are opened and intake and exhaust are performed. The intake / exhaust port is closed by the sliding contact surface of the main body case, and the intake / exhaust port of the cylinder is closed.

[Problems to be solved by the invention]

With the above-described structure, the airtightness at the intake / exhaust port of the cylinder during the compression and explosion strokes, and the continuous airtightness at the intake / exhaust port during the intake and exhaust strokes are the same for both the main body case and the cylinder case. It is based on the sliding contact state of the sliding contact surface. Therefore, in order to enhance the airtightness, the entire cylinder case is biased in the direction of the axis of rotation with respect to the main body case,
It is necessary to keep the contact surface pressure of the sliding contact surface high.

However, in order to configure as described above, it is necessary to provide a fitting structure with a large tolerance so that the support portion of the bearing that supports the rotating cylinder case can slide in the direction of the axis of rotation of the cylinder case. However, with such a structure, the smooth rotation of the cylinder case is hindered due to the play due to the large fitting tolerance, which makes high-speed rotation difficult.

Here, the present invention focuses on the above-mentioned problem, and aims to increase the airtightness of the intake and exhaust ports while using another means to maintain smooth rotation of the cylinder case.

[Means for solving problems]

A feature of the present invention is that, in the engine described above, a plate-shaped sealing member having a cylindrical portion fitted in an intake / exhaust port of a cylinder or an exhaust port of a main body case, an intake port, a fuel injection port or an ignition port One of the case and the main body case is provided so as to be slidably contactable in the direction of the axis of rotation of the cylinder case, and the seal member is configured to be biased and pressed against the sliding contact surface of the other cylinder case or the main body case. , Its action and effect are as follows.

[Action]

For example, when the sealing member is provided on the cylinder case side, a so-called sealing surface is formed between the sealing member and the sliding contact surface on the main body case side. Therefore, compared to a structure in which the entire cylinder case is pressed against the main body case, it is not necessary to configure the entire cylinder case to slide in the direction of the rotation axis, and a seal member that is sufficiently lighter than the cylinder case is used. The structure in which the sliding contact surface on the side is pressed can be configured more simply, and a sufficient contact surface pressure can be obtained even with a relatively small biasing force.

[Effect of device]

As described above, in the cylinder case rotation type engine as mentioned above, without changing the rotation support structure of the cylinder case, the sealing property at the sliding contact surface between the cylinder case and the main body case, that is, during intake and exhaust. Also, the airtightness of the cylinder at the time of compression / explosion can be improved, and the efficiency and speed of the engine can be improved.

〔Example〕

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 2 shows the entire longitudinal side surface of the engine, and FIG. 3 shows the longitudinal front surface. The body case (1) of this engine is
The front case (1a) on the output side and the rear case (1b) on the head side are bolt-jointed to form a split structure. The front and rear cases (1a) and (1b) have bearings (2),
A cylinder case (3) is horizontally supported rotatably via (2).

The cylinder case (3) includes the bearing (2),
Front and rear cylindrical shaft cases (4) and (5) supported by (2)
And an intermediate case (6) sandwiched and connected in the middle thereof, and the cylinder case (3) is attached to the intermediate case (6).
A through-type cylinder having an axis perpendicular to the rotation axis (P ₁ ) is formed. A pair of pistons (8), (8) are internally fitted into the cylinder so as to face each other.
A bearing type roller (9) is rotatably supported by a skirt portion of the roller via a piston pin (10).

A cam plate (12) is fastened and fixed together between the front and rear cases (1a), (1b) of the main body case (1), and an oval inner peripheral surface formed in the center of the cam plate (12). Rollers (9), (9) of both pistons (8), (8) in a certain cam hole
Are inscribed, and each piston (8) reciprocates twice for one rotation of the cylinder case (3). A guide portion (1) protruding in the axial direction of the rollers (9) and (9) is provided on the inner peripheral portion of the cam hole.
3) is provided all around the inner circumference of the cam hole.

On the other hand, an engaging arm (7) is supported and extended from the piston pin (10) in a swingable manner, and a bearing type roller (11) is provided at the swinging end of the engaging arm (7). As shown in FIG. 2 and FIG. 3, the guide portion (13) is sandwiched between the rollers (9) and (11), and the piston (8) is fixed to the cam plate (12) during engine operation. The inner peripheral surface of the cam hole is not separated.

The rear end surface of the cylinder is configured to be in sliding contact with the head portion (14) formed in the center of the rear case (1b) in the axial direction of the cylinder case (3), and the rear end surface of the cylinder rotates the cylinder case (3). One intake / exhaust port (15) is formed which is eccentric with respect to the moving shaft center (P ₁ ). Also, the head portion (1
The sliding contact surface of 4) has an exhaust port (16) and an intake port (1) with a predetermined angle phase along the moving direction of the intake port (15).
7) and a fuel injection port (18) are provided, and the intake / exhaust port (15) of the cylinder case (3) is connected to the exhaust port (16) and the intake port of the head section (14) as the cylinder case (3) rotates. (17)
And the fuel injection ports (18) are sequentially positioned at appropriate timings,
Exhaust-intake-compression-explosion-expansion four cycles are performed so that the cylinder case (3) continuously rotates in a fixed direction (A).

Next, the structure of the sliding contact surface between the rear end surface of the cylinder and the head portion (14) on the body case (1) side will be described in detail. As shown in FIG. A plate-shaped seal member (49) having a cylindrical portion (49a) to be fitted therein and rotating integrally with the cylinder case (3) is provided on the cylinder side, and a seal member (49) is provided from the cylinder side to the head portion (14) side. ) Is biased and pressed by a plurality of springs (50) and is in sliding contact with the head portion (14).

The rotation output of the cylinder case (3) is supplied to the spline hole (20) provided at the outer end of the front cylindrical shaft case (4).
It is designed to be taken out from the PTO shaft (not shown) attached to the. A fan (21) is attached to the shaft end of the front cylinder shaft case (4), and the outside air taken in through an opening (22) formed in the rear center of the rear cylinder shaft case (5) is transferred to the cylinder. After passing through the cooling air passage formed between the peripheral ribs (23), it is sucked and discharged from the discharge port (25) provided in the front end peripheral portion of the front cylindrical shaft case (4), and the head portion ( 14) and the cylinder case (3) are configured to be cooled. Further, a worm (5a) is provided on the outer periphery of the rear cylindrical shaft case (5), and a worm gear (51) is engaged with the worm (5a).
The lubricating oil pump (not shown) is driven by the power extracted from 1).

As shown in FIG. 2, a muffler (26) communicating with the exhaust hole (16) is connected to an outer portion of the head portion (14), and a fuel injection device is internally provided in the head portion (14). Has been done. Next, the fuel injection device will be described in detail.
As shown in the figure, a plunger type pump casing (29) is embedded and fixed inside the head portion (14), and the fuel injection port (18) is formed at the tip thereof. In the pump casing (29), a plunger (32) is directly driven back and forth by the rotational force of the cylinder case (3).
Is fitted inside.

The drive structure of the plunger (32) will be described in detail. A governor case (30) incorporating a governor mechanism (to be described later) is attached to a position of the rotary shaft core (P ₁ ) of the seal member (49), and a head portion (14) is attached. The governor case (30) is inserted into the inside of the head part (14) and rotates with the rotation of the cylinder case (3) and the seal member (49). Then, a cylindrical cam (31) having a cam groove (31a) on the outer peripheral surface is attached to the governor case (30) by a spline structure,
The cylindrical cam (31) is brought into sliding contact with the side surface of the plunger (32), and the tip of the cam pin (19) of the plunger (32) is engaged with the cam groove (31a) of the cylindrical cam (31) to form a cam mechanism. By doing so, the plunger (32) is driven to reciprocate once for each rotation of the cylinder case (3) and the seal member (49).

More specifically, the plunger (32) is provided around the plunger chamber (33) formed in the pump casing (29).
A plurality of small holes (34) that are opened when the valve retracts. The small holes (34) are provided in the governor case (30), and the passage (36) and the needle type variable throttle valve (39). Is connected to a passage (38) having In addition, an air intake passage (41) that does not communicate with the governor case (30) but directly communicates the plunger chamber (33) with the outside is also provided, and the air intake passage (41) also has a needle-type on-off valve. (42) is provided. The on-off valve (42) is closed during normal operation.

A cylindrical fuel control valve (37) slidable in the direction of the rotation axis (P ₁ ) is provided inside the governor case (30). The fuel control valve (37) is a governor spring (37). 43)
It is slidingly operated by the governor rod (45) via the.
The fuel enters the governor case (30) from the flow path (40) communicating with the fuel inlet (not shown) provided near the end of the head (14), and the small amount provided in the fuel control valve (37). Hole (37
Enter the aisle (36) from a). Then, the fuel amount is adjusted by a rotary type speed control arm (4
6) Sliding the fuel control valve (37) with the fuel control valve (37), and setting the speed by setting the communication opening between the annular groove (37b) communicating with the small hole (37a) of the fuel control valve (37) and the passage (36). I do.

The fuel control valve (37) is configured to be advanced and retracted by a mechanical governor, and the governor includes a governor spring (43) that presses the fuel control valve (37) in a direction to increase the opening degree of the fuel control valve (37). , And a governor weight (44) that generates a governor force that presses in a direction to reduce the opening degree.

The governor weight (44) is a recess (48) formed at the rear end of the cylinder case (3) so as to be eccentric to the rotation axis (P ₁ ).
It is housed inside and is swingably supported by a bracket (47) fixed to the seal member (49). And, the arm (44
a) is brought into contact with the tip of the push rod (37c) attached to the fuel control valve (37) so that the centrifugal force (governor force) of the governor weight (44) is transmitted to the fuel control valve (37). Has become.

Next, the supercharging structure will be described in detail. As shown in FIGS. 1 and 2, the check valve suction valve (24) and the front case (1a) are provided on the rear case (1b) of the main body case (1). ) Is provided with a check valve type exhaust valve (27), and a pressure accumulating chamber (28) is formed along the outer circumference of the front case (1a). Due to the reciprocating motion of the piston (8) accompanying the rotation of the cylinder case (3), the inside of the main body case (1) has a function of a so-called reciprocating pump, and both pistons (8) are in the cylinder during compression and exhaust strokes. When the case (3) moves in a direction approaching the rotation axis (P ₁ ) of the case (3), the negative pressure at that time causes the outside air to be drawn into the main case (1) from the suction valve (24). On the other hand, when both pistons (8) move away from the rotary shaft core (P ₁ ) in the intake and explosion strokes, the air in the main body case (1) is compressed and passes through the exhaust valve (27). Accumulation chamber (2
Sent to 8). Then, the pressure accumulating chamber (28) and the intake port (17) provided in the head portion (14) are communicatively connected to each other via the supercharging pipe (35).

The entire engine is configured as described above, and its operation will be described in detail below.

The cylinder case (3) is rotated clockwise in FIG. 3, and the intake / exhaust port (15) of the cylinder case (3) overlaps with the exhaust port (16) and both pistons (8), After (8) moves closer and exhaust is performed, the intake and exhaust ports (15) overlap with the intake port (17), and both pistons (8) and (8) move toward centrifugal force and guide part (13). By the guide action, they move away from each other, the compressed air in the pressure accumulating chamber (28) is sent into the cylinder, and the compression stroke continues.

By the end of the intake and compression strokes, the plunger (32) of the fuel injection device is driven backward and forward once. At this time, the plunger (32) is retracted to rapidly suck air into the plunger chamber (33), and at this time, the negative pressure generated in the passage (36) sucks fuel from the fuel control valve (37) to cause air to flow. Mixed while atomizing into. When the variable throttle valve (39) of the passage (38) is throttled at the time of starting the engine, a large amount of fuel is sucked by the negative pressure, so that a very rich air-fuel mixture is formed. The air-fuel mixture thus formed flows into the plunger chamber (33) through the small hole (34), at which time atomization of the fuel is further promoted. Then, due to the forced advance of the plunger (32), a certain amount of the air-fuel mixture in the plunger chamber (33) is compressed and becomes a high-pressure high-temperature air-fuel mixture.

After the completion of the air-fuel mixture compression, the intake / exhaust port (15) of the cylinder case (3) that has completed the intake compression stroke is replaced by the fuel injection port (18).
, The high temperature and high pressure air-fuel mixture in the plunger chamber (33) is ejected into the high temperature compressed air in the cylinder and moves to the explosion and expansion stroke. During this explosive expansion stroke, the plunger (32) is held at the advanced (compression) end position, and is maintained in a state in which the combustion gas is prevented from flowing into the plunger chamber (33).

Then, following the explosion and expansion strokes, the process proceeds to the exhaust stroke, and this cycle is repeated. When the on-off valve (42) of the air intake passage (41) is opened when the engine is stopped, a large amount of outside air flows into the plunger chamber (33), and a very thin air-fuel mixture that cannot be ignited is formed. As a result, the engine can be stopped suddenly.

[Another embodiment]

In the above-described embodiment, the seal member (49) is provided on the cylinder case (3) side. However, as shown in FIG. 4, the seal member (49) is attached to the fuel injection port (18), the exhaust port (16) and the intake port (17). It is also possible to adopt a structure in which a donut plate-shaped seal member (49) having a cylindrical portion (49a) to be fitted in sliding contact is biased and pressed against the cylinder case (3) from the head (14) side to make sliding contact.

It should be noted that reference numerals are added to the claims of the utility model for convenience of comparison with the drawings, but the present invention is not limited to the structure of the accompanying drawings by the entry.

[Brief description of drawings]

The drawings show an embodiment of the engine according to the present invention. Fig. 1 is a vertical sectional side view of the vicinity of the engine head, Fig. 2 is a vertical sectional side view of the entire engine, and Fig. 3 is a vertical sectional front view of the engine.
FIG. 4 is a vertical sectional side view in the vicinity of the head portion in another embodiment. (1) …… Main body case, (3) …… Cylinder case,
(8) …… Piston, (12) …… Cam plate, (15) …… Intake / exhaust port, (16) …… Exhaust port, (17) …… Intake port, (18)
…… Fuel injection port, (49) …… Seal member, (49a) ……
Cylindrical part.

Claims (1)

[Scope of utility model registration request] 1. A cylinder case (3) for a main body case (1)
Slidably rotatably supported with respect to the inner wall of the cylinder, and the intake / exhaust port (15) provided in the cylinder is separated by a predetermined phase from the sliding surface on the main body case (1) side as the cylinder case (3) rotates. The cam plate (12) provided on the main body case (1) side while being configured to sequentially circulate through the exhaust port (16), the intake port (17), the fuel injection port (18) or the ignition port formed in this manner. ) Is an engine configured to guide the pistons (8) and (8) forwards and backwards on the inner peripheral surface thereof, and the intake and exhaust ports (15) of the cylinder or the exhaust port (1) of the main body case (1).
6), a plate-shaped seal member (4) having a cylindrical portion (49a) fitted in the intake port (17), the fuel injection port (18) or the ignition port.
9) is provided in one of the cylinder case (3) and the main body case (1) so as to be slidably contactable in the direction of the axis of rotation of the cylinder case (3), and the seal member (49) is provided in the other cylinder case (3). Alternatively, an engine configured to urge and press the sliding contact surface of the main body case (1).