JPS63124815A - Rotary opening/closing type spherical intake/exhaust valve - Google Patents

Abstract

PURPOSE:To improve the output by fabricating the port of a communicating passage formed inside a spherical intake/exhaust valve to have the starting end part with approximately straight form parallel with the axis of rotation of the valve. CONSTITUTION:An intake/exhaust passage 05 communicating with a spherical intake/exhaust valve 01 has a circle section. The starting end parts of upper-end port 03 and lower-end port 04 of a communication passage 02 which runs through the center of the spherical intake/exhaust valve 01 is formed in such a halved square form to make tangential contact with the round port 06 of the intake/exhaust passage 05. The area early developed when the intake/ exhaust valve is opened may then be enlarged and the intake/exhaust flow rate be increased, whereby improving the output.

Description

[Detailed Description of the Invention] The present invention provides a reciprocating four-stroke internal combustion engine that can rotate around an axis perpendicular to the intake and exhaust passages without using mushroom-shaped intake and exhaust valves. The present invention relates to an intake/exhaust valve in which an intake/exhaust valve is interposed in an intake/exhaust passage, and the intake/exhaust passage is opened/closed by rotation of the intake/exhaust valve.

Historically, in the mushroom-shaped intake and exhaust valves used in normal internal combustion engines, this maximum opening area increases as the valve diameter and valve lift increase, but the valve diameter is limited by the cylinder radius, and the valve lift increases. Since the value is limited by the impact caused by the reciprocating movement of the valve, the valve opening area is made as wide as the crossbar area of the intake and exhaust passages to reduce the flow resistance for intake and exhaust, thereby reducing the intake and exhaust flow resistance during high-speed operation. It is difficult to increase emission efficiency.

In order to improve this, an intake/exhaust valve was installed in the intake/exhaust passage so as to be rotatable in one direction or in a reciprocating direction about an axis perpendicular to the intake/exhaust passage.
However, since the intake and exhaust valves are formed in a cylindrical shape, it is difficult to seal the cylindrical end face.

In order to improve this sealing property, the rotary opening/closing type intake and exhaust valves were formed into spherical shapes as shown in FIGS.
3-117116), the cross-sectional areas of the communication passage and the intake/exhaust passage C in the intake/exhaust valve a are set to the same extent to reduce the intake and exhaust flow resistance, and the We were able to increase the discharge efficiency.

However, in a rotary opening/closing type spherical intake/exhaust valve, the opening shape of the intake/exhaust passage and the communication passage in the intake/exhaust valve is circular or close to a circle, so the intake/exhaust valve Since the frontage surface of the valve at the beginning of opening is in the shape of an overlapping part of ellipses, its opening area is narrower than the opening area of the ear-shaped intake/exhaust valve at the same time. The flow resistance of the discharge is high, and as a result, the flow rate of the rotary opening/closing spherical intake/exhaust valve changes to the ear-like intake/exhaust flow rate shown in the curve 1 in Figure 3 above a certain rotation angle, as shown in the ■ curve in Figure 3. Although it is large compared to the flow rate of the valve, it is small at angles below this, and therefore the advantage of low flow resistance in the fully open state cannot be fully utilized.

The present invention relates to an improvement of a rotary opening/closing spherical intake/exhaust valve that overcomes these difficulties, and is an internal combustion engine. In an intake/exhaust system in which a spherical intake/exhaust valve is rotatably interposed in an intake/exhaust passage of a first valve, and the intake/exhaust passage is opened/closed by rotation of the spherical intake/exhaust valve, the spherical intake/exhaust valve is formed within the spherical intake/exhaust valve. The end edge of the opening of the port in the communication passage, and the frontage l of the spherical intake/exhaust valve communication passage.
ζ A curved line is formed along the longitudinal direction of one or both of the opening start side edges of the ports in the intake II air passage in a shape close to a straight line parallel to the center of rotation of the spherical intake/exhaust valve. By doing so, compared to internal combustion engines in which the opening between the intake and exhaust passages and the communication passage in the intake and exhaust valves is circular or nearly circular, the opening area of the intake and exhaust valves at the initial stage of opening is widened, and the opening area of the intake and exhaust valves is widened. The flow resistance of intake and discharge at the initial stage of the valve can be reduced.

X''Ll The difference between the conventional spherical intake/exhaust valve and the spherical intake/exhaust valve of the present invention will be explained in more detail.

In the conventional spherical intake/exhaust valve a shown in FIG. The air passage C is formed in the same cross section as this communication passage.

On the other hand, in the spherical intake/exhaust valve 01 of the first embodiment of the present invention shown in FIG. 5, the intake/exhaust passage 05 is formed to have a circular cross section. The upper and lower ports 03 and 04 of the communication passage 02 provided in this spherical intake and exhaust valve 01 and their cross-sectional shapes are formed as shown in FIG. 6.

That is, the upper end port 03 and the lower end port 04 of the communication path 02
On the opening start sides 03a and 04a, ■, [F] in Fig. 6
As shown in FIG.
It is formed in the shape of half a square so that it is circumscribed by .

To explain in detail, the upper end bows 1 to 0 of the communication path 02
3, the left 1' portion 03b is a semicircle with the same radius as the circular port 06 of the intake/exhaust passage 05, and the right half 03a on the opening side is a rectangle that circumscribes the circular port 06 of the intake/exhaust passage. At the lower end port 04 of the communication passage 02, the left half 04a on the opening side is a rectangle circumscribing the circular port 06 of the intake passage 05, and the right half 04 on the opposite side
b is a semicircle with the same radius as the circular port 06 of the intake/exhaust passage.

The central cross section of the communicating path 02 has a shape intermediate between a regular hexagon and a circle, as shown in (■) in FIG. 7, and approaches the upper tenth port 1-03.04 of the communicating path 02. As shown in Figure 7, port 03.0
It is formed in a shape similar to that of 4.

The communication passage o2 and the upper and lower end ports 03.04 of the intake/exhaust valve 01 of the first embodiment of the present invention are configured as described above, so that the conventional one shown in FIG. In the first embodiment, the center line of the communication passage C205 is oriented horizontally, and the intake and exhaust valves a and 01 are oriented at 30 degrees and 45 degrees from the state where the intake and exhaust passage C205 is fully opened.

In the states of ■, ■, ■, and [F] that are swung at 60° and 90°, in this example R, the opening start sides 03a and 04a of ports 03.04 as seen along the center line of the communication path 02 is formed into a rectangular shape with a straight line part parallel to the rotation axis of the suction valve 01 and parts at right angles at both ends, so that the opening faces are Figures 4 and 5
As is clear from the shapes shown below each of ■, ■, ■, and [F] in the figure, the first embodiment of the present invention is better than the fourth embodiment.
Compared to the conventional one shown in the figure, the opening area is particularly large immediately after the opening, and as shown by the ■ curve in Figure 3, when the rotation angle θ is small, the flow rate is particularly large. High efficiency.

In the spherical intake/exhaust valve 01 of the first embodiment shown in FIGS. 5 to 7, the cross-sectional shape of the communication passage 02 is shown in FIG. 6, but as shown in FIG. Communication path 02
The intake/exhaust valve may have a square cross-sectional shape over the entire length and have an external shape as shown in FIG. As shown in Figure 10, ■, ■, ■, ■ in Figure 5
The shape is the same as that of each lower part, and the inflow corresponding to the rotation angle has a characteristic as shown by the ■ curve in FIG.

Further, the communication passage 02 of the spherical intake/exhaust valve 01 may be formed in a cylindrical shape, and the cross-sectional shape of the intake/exhaust passage 05 may be formed in a square shape similar to the port 03.04 of the communication passage 02. The opening surface shape of the spherical intake/exhaust valve 01 of the third embodiment is as shown in FIG. 11, and compared to the conventional one shown in FIG. 4, the area immediately after the opening is larger.

A fourth embodiment of the present invention illustrated in FIGS. 12 to 17 will be explained below.

An engine 1 mounted on a motorcycle (not shown) is 1
In a 4-cylinder gasoline engine, a crankshaft 6 is rotatably supported in the crankcase 2 of the engine 1, and a piston 7, which is fitted in the cylinder block 3 in a freely movable manner, connects the connecting The piston 7 is connected to the crankshaft 6 through the piston 7, and the reciprocating movement of the piston 7 rotates the crankshaft 6 in the forward direction.

Furthermore, two intake passages and two exhaust passages 1o are formed in the cylinder head 4 and head cover 5, respectively, and a separate carburetor 11 is connected to each intake passage 9, and an exhaust pipe is also provided in the tillage passage 10. 12 are connected.

Furthermore, the intake passage 9. A spherical intake valve 132 and a spherical air valve 14 are respectively fitted into the exhaust passage 10 so as to be able to swing about a direction perpendicular to the longitudinal direction thereof, and between the head cover 5 and the spherical intake valve 131 and the spherical exhaust valve 14. An upper sealing material 15 is interposed between the cylinder head 4 and the spherical intake valve 131 and the spherical exhaust valve 14, and a shim 1G,
I! Fi-face C-type ring bullet material 17. Lower seal material 18
is interposed therebetween, and one surface of the shim 1G and the resilient material contact surface of the lower seal material 18 are formed into a curved surface having approximately the same diameter as the cross-sectional outer diameter of the ring-shaped resilient material 17 having a C-shaped cross section.

Thus, the cross-sectional shapes of the intake passage 9 and the exhaust passage 10 are formed in a circular shape, and the upper sealing material 15 and the acyl material 18 are formed in a ring shape.

Further, the cross-sectional shape of the communication passages 13a, 14a of the spherical intake and exhaust valves 13, 14 is formed in the same shape as the embodiment shown in FIGS. 5-7.

Further, the circumferential surface of the spherical intake/exhaust valve 13, 14 is cut out or missing at a plane parallel to the plane formed by its center line of rotation and the center line of the communication passages 13F1, 148.

14b is formed.

Notches 13C and 14c oriented in the radial direction are formed in the opposing end surfaces of each of the left and right spherical exhaust valves 13, and the base 19a of the connecting piece 19 engages with the pair of adjacent notches i3c and 14c. is formed, and the connecting disk 20 has [yo,
A cross groove 20a is formed in which the top part 19b of the connecting piece 19 can be fitted loosely at right angles to the phase H, and the connecting piece 1 is inserted into the notches 13c and 14c of a pair of adjacent spherical intake/exhaust valves 13 and 14.
9-1. While engaging the portion 19a, the connecting piece 19
By engaging the cross grooves 20a of the connecting disc 20 with their tops 19b orthogonal to each other, a misaligned shaft joint is formed, and a pair of adjacent spherical intake and exhaust valves 13. i4i;L Even if their centers of rotation are shifted from each other, rotational torque is smoothly transmitted from one spherical intake/exhaust valve 13.14 to the other spherical intake/exhaust valve 13.14 (J5
Although the spherical intake valve is not shown in FIG. 15, the spherical intake valve 13 is also configured with an offset shaft joint similar to the spherical plowing valve 14).

Furthermore, protrusions i3d and 14d are formed on the other end face of one spherical intake valve 139 and the other spherical exhaust valve 14, and protrusions 22a and 23a are also formed on the inner end of the valve drive shaft 22.23. Similar to the connecting plate 20 and Ii′i1, a cross groove 21a is formed on the connecting disc 21, and conical protrusions 13d, 14d
, the connecting disc 21 with the protrusions 22a and 23a perpendicular to each other.
The spherical intake valve 1 is fitted into the cross groove 21a of the spherical intake valve 1.
32 spherical exhaust valve 14 is connected to the valve drive shaft 22. The valve drive shaft 22. is connected to a valve drive @23. The intake valve driven gear t is attached to the valve drive shaft 23. 24. An exhaust valve driven gear 25 is integrally fitted.

Furthermore, a crank gear 26 is integrally fitted to the crankshaft 6, and the crank gear 26 is meshed with an idle gear 27 having twice the number of teeth as the crank gear 26, which is pivotally supported on the crank case 2. The idle gear 28 integrated with the cam gear A730.3 is connected to a pair of cam gears 30.31 via a drive gear 29.
Cams 32 and 33 are integrally attached to each of the cams 1 and 1, and when the crankshaft 6 rotates in the direction along with the crank gear 26, the idle gears 27 and 28 rotate in the B direction, the drive gear 29 in the direction, and the cam gears 30 and 31 ．． cam 3
2.33 is designed to be rotationally driven in the B direction.

Moreover, a cam follower 34.35 is pivotally supported on the cylinder head 4, and the cam follower 34.35 swings in contact with the cam 32.33.
．． An exhaust valve drive gear 37 is integrally formed with the intake valve drive gear 36. The exhaust valve drive gear 37 is the intake valve driven gear 24. They are meshed with the exhaust valve driven gear 25, respectively.

Further, a return spring 38 is interposed between the head cover 5 and the cam followers 34.35, and the spring force of the return spring 38 causes the cam followers 34.3 to
5 is in constant pressure contact with the cams 32 and 33.

Furthermore, a lubricating oil passage 39 is formed in the head cover 5 to lubricate the sliding contact portions between the upper seal 15 and the intake valves 13 and exhaust valves 14. il? 1:
A lubricating oil passage 40 for cooling the ring-shaped elastic material 17 having a C-shaped cross section and a C-shaped cross section is formed.

The embodiment shown in FIGS. 12 to 17 is configured as described above, so that when the crankshaft 6 is rotated in the forward direction by the starter motor (not shown), the cam gears 30.31 and cams 32.33 are rotated. Cranksi 1/
The cam follower 34.35 in contact with the cam 32.33 is driven to swing up and down once every two revolutions of the crankshaft 6, and the intake valve driven gear 24 , exhaust valve driven gear 25
．． Valve drive @1122.23. The spherical intake valve 139 and the spherical exhaust valve 14 are each driven to rotate by 90 degrees, and the intake passage 9
, 10 are opened and closed, thus providing the required suction, compression, expansion,
The four exhaust strokes are repeated, and the engine 1 enters the operating state.

Further, the cross-sectional shape of the communicating passages 13a, 14a is formed in the same shape as the embodiment shown in FIGS.
b, 111b is formed, so that the spherical intake valve 13
The opening area of the two spherical exhaust valves 14 in the initial opening state is the first
As shown in Fig. 7, it is significantly wider than the conventional spherical intake/exhaust valve (see Fig. 4), and as shown by the V curve in Fig. 3, the flow rate increases significantly, and the intake/exhaust valve High efficiency.

Furthermore, since the spherical intake valve 139 and the spherical exhaust valve 14 are moved intermittently, vibrations unlike those of the ear-shaped intake and exhaust valves are less likely to occur.

Furthermore, the lower sealing material 18 is pressed against the spherical intake valve 13° and the spherical exhaust valve 14 by the spring force of the ring-shaped elastic material 17 with a C-shaped cross section and the combustion gas pressure acting on the inner peripheral surface of the ring-shaped elastic material 17 with a C-shaped cross section. Since the pressing force also acts on the upper sealing material 15 and the spherical intake valve 139 and the spherical exhaust valve 14, the intake passage 9. The airtightness between the exhaust passage 10, the spherical intake valve 131 and the spherical exhaust valve 14 is high.

Moreover, the cross section of the surface of the C-shaped ring-shaped resilient material 17 has a shape close to a circle, and the upper surface of the cam 1G and the lower surface of the lower seal material 18 that contact the resilient material are made of a ring-shaped resilient material with a C-shaped cross-section. Since it is formed on a curved surface with the same diameter as 17, the cross section C
The surface of the ring-shaped elastic material 17 is brought into close contact with the shim 16 and the lower seal material 18 over a wide area, ensuring reliable sealing, preventing local wear and stress concentration, and improving durability. heads towards Ohin.

Furthermore, since the two pairs of spherical intake valves 139 and spherical exhaust valves 14 are connected to each other via mutually offset shaft joints formed by connecting pieces 19 and 20, each spherical intake valve 13 and spherical exhaust valve 14 are made of upper seal material. 15. It can be brought into close contact with the lower sealing material 18 without any difficulty.

Furthermore, since the lubricating oil passages 39 and 40 are formed in the head cover 5 and the cylinder head 4, the sliding contact portions between the intake valve 13 and exhaust valve 14 and the upper seal 15 and lower seal 18 are sufficiently lubricated. At the same time, the ring-shaped elastic material 17 having a C-shaped cross section is sufficiently cooled, and the elastic material 11 is prevented from becoming sagging.

11 II As described above, in the present invention, the opening area of the intake and exhaust valve at the initial stage of opening can be widened, and the flow resistance of intake and exhaust at the initial stage of valve opening can be reduced, so that the intake and exhaust flow rate of the internal combustion engine can be reduced. can be increased to increase output and improve efficiency.

[Brief explanation of the drawing]

Figures 1 and 2 are longitudinal sectional views of a conventional rotary open/close type spherical intake and exhaust valve, with Figure 1 showing the exhaust communication state, Figure 2 the suction communication state, and Figure 3 showing the conventional rotary opening/closing spherical intake and exhaust valve. A characteristic diagram illustrating flow matrix characteristics in each embodiment of the present invention;
Fig. 4 is a diagram illustrating a vertical cross section of a conventional rotary opening/closing type spherical intake/exhaust valve and its opening shape, and Fig. 5 is a drawing showing an m cross section and its opening shape of an embodiment of a rotary opening/closing type spherical intake/exhaust valve according to the present invention. FIG. 6 is a cross-sectional view of FIG. 5, FIG. 7 is a perspective view of the valve body, FIG. 8 is a cross-sectional view of the valve body of another embodiment, and FIG. 9 is a cross-sectional view of the valve body of another embodiment. Its perspective view, FIG. 10 is a drawing showing the opening shape thereof, FIG. 11 is a drawing showing the opening shape of another embodiment, and FIG. 12 is a one-cylinder motorcycle for a motorcycle equipped with a specific example of the present invention. 13 is a vertical left side view of a four-cycle gasoline engine, FIG. 13 is a vertical right side view of the main part of the engine, FIG. 14 is a sectional view taken along the xrv-xrv line in FIG. 13, and FIG. 15 is a main part of the engine. Partially exploded perspective view, 1st
6 is an enlarged U-sectional side view of the main part of FIG. 12, and FIG. 17 is a drawing showing the shape of the opening. 1...Engine, 2...Crankcase, 3...
Cylinder block, 4... Cylinder head, 5...
Head cover, 6... Crankshaft, 7... Piston, 8... Connecting rod, 9... Intake passage, 10... Exhaust passage, 11... Carburetor,
12... Exhaust pipe, 13... Spherical intake valve, 14...
Spherical exhaust valve, 15... Upper seal material, 16...
Shim, 17...C-shaped ring-shaped elastic material, 18...
Lower seal material, 19... connecting piece, 20... connecting plate,
21... Connection disk, 22.23... Valve drive shaft, 24
...Intake valve driven gear, 25...Exhaust valve driven gear, 26...Crank gear, 27.28...Idle gear, 29...Drive gear, 30.31...
Cam gear, 32.33...Cam, 34.35...Cam follower, 36...Intake valve drive gear, 37.
...Exhaust valve drive gear, 38...Return spring, 39, 40...Lubricating oil path.

Claims (1)

[Claims] In an intake/exhaust system in which a spherical intake/exhaust valve is rotatably interposed in an intake/exhaust passage of an internal combustion engine, and the intake/exhaust passage is opened/closed by rotation of the spherical intake/exhaust valve, the spherical intake/exhaust valve is formed within the spherical intake/exhaust valve. When viewed along the longitudinal direction of one or both of the opening start side edge of the port in the communication passage and the opening start side edge of the port in the intake/exhaust passage opened to the spherical intake/exhaust valve communication passage. A rotary open/close type spherical intake/exhaust valve for an internal combustion engine, wherein the line is formed in a shape close to a straight line parallel to the center of rotation of the spherical intake/exhaust valve.