JPH0444820Y2 - - Google Patents

Description

[Detailed description of the invention] [Industrial application field] This invention consists of a cylinder case equipped with a reciprocating piston that is rotatably supported in the main body case, and an intake/exhaust port formed on the end face of the cylinder case that is connected to the main body. The present invention relates to a fuel injection device used in an engine configured to have an exhaust hole formed in the end face of a head portion of a case and an intake hole in circulation.

[Conventional technology]

As the above-mentioned engine, there is one already proposed by the applicant as Utility Model Publication No. 47-37933.

In the above-mentioned prior art, the fuel injection pump is driven by a small diameter cam of a camshaft that is geared to the main shaft of the engine, similar to a general engine.

[Problem that the invention attempts to solve]

However, the above conventional technology requires an interlocking mechanism between the main shaft of the engine and the camshaft, which increases the number of parts and tends to increase costs.In addition, it requires assembly while adjusting the timing of the cam. Attachment was becoming complicated.

Furthermore, since a small-diameter cam is used, the amount of lift cannot be increased, and the shape of the cam is restricted. Furthermore, if the lift amount is reduced in order to give priority to the cam shape, extremely high precision machining is required.

The present invention aims to solve the above-mentioned problems of the conventional technology by effectively utilizing a rotary cylinder case.

[Means for solving problems]

Therefore, in the present invention, in the engine having the above configuration, a large-diameter cam is provided near the outer circumference of the cylinder case, and the cam is configured to press and drive the fuel injection operating member.

[Effect]

According to the above configuration, since the cam has a large diameter,
Its circumference is long, so even if the lift amount is large, the lift amount for a unit rotation is small, and the actuating member is smoothly pressed and driven.

[Effect of idea]

Therefore, according to the present invention, there is no need for an interlocking structure between the engine main shaft and the cam, and it can be manufactured at low cost, and by using a cam with a large circumference, a large lift amount can be obtained with any cam profile. Therefore, it has become possible to reduce the amount of lift per unit rotation angle and smoothly press and drive the actuating member.

Furthermore, since the lift amount is large, particularly high-precision machining is not required, which is advantageous in terms of machining.

Also, since the cam rotates together with the cylinder case, timing and center alignment during assembly are extremely easy.

〔Example〕

Hereinafter, one embodiment of the present invention will be described based on illustrative drawings.

FIG. 1 shows an overall longitudinal side view of the engine, and FIG. 2 shows its longitudinal front view. The main body case 1 of this engine has a two-part structure in which a front case 1a, which is the output side, and a rear case 1b, which is the head side, are bolted together. 3 is rotatably supported horizontally.

The cylinder case 3 includes the bearings 2,
It consists of front and rear cylindrical shaft cases 4, 5 supported by the cylinder shaft 2, and an intermediate case 6 sandwiched and connected between them.
A penetrating cylinder 7 having an axis perpendicular to the rotation axis P of the cylinder case 3 is formed in the intermediate case 6 .

A pair of pistons 8 , 8 are fitted inside the cylinder 7 so as to face each other, and a steel ball (solid or hollow) 9 is rotatably attached to the skirt portion of each piston 8 via a bearing metal 10 having a partially spherical shell shape. and is supported by a stopper ring 11 to prevent it from coming off.

A cam plate 12 is fastened together between the front and rear cases 1a, 1b of the main body case 1, and the steel balls of the pistons 8, 8 are inserted into an oblong cam hole 13 formed in the center of the cam plate 12. 9 and 9 are inscribed, and each piston 8 reciprocates twice for each rotation of the cylinder case 3.

The rear end surface of the cylinder 7 is configured to slide in the cylinder case axial direction with a head portion 14 formed at the center of the rear case 1b, and a cylinder 7 is provided on the rear end surface of the cylinder case eccentrically with respect to the cylinder case rotation axis P.
Inlet/outlet ports 15 are formed. Further, on the sliding surface of the head portion 14, exhaust holes 1 are formed with a predetermined angular phase along the moving direction of the intake and exhaust ports 15.
6, an intake hole 17 and a fuel injection hole 18 are provided,
As the cylinder case 3 rotates, the intake/exhaust port 1
5 is sequentially communicated with the intake/exhaust holes 16, 17 and the nozzle 18 at appropriate timings to perform four cycles of exhaust-intake-compression-explosion-expansion, so that the cylinder case 3 is driven to rotate continuously in a constant direction A. It's summery.

The rotational output of the cylinder 3 is then fitted into the pulley 19 attached to the outer end of the front cylinder shaft case 4 or into the shaft end spline hole 20.
It is adapted to be taken out from a PTO shaft (not shown).

A fan 21 is attached to the shaft end of the front cylinder shaft case 4 together with the output pulley 19, and a fan 21 is attached to the shaft end of the front cylinder shaft case 4 so as to circulate the outside air taken in from an opening 22 formed at the center of the rear part of the rear cylinder shaft case 5 around the cylinder 7. After the cooling air passes through the cooling air passage 24 formed between the ribs 23, it is suctioned and discharged from the exhaust port 25 provided on the front end circumference of the front cylinder shaft case 4, and is discharged from the head 14 and the cylinder 7.
It is configured to provide cooling.

The exhaust hole 1 is provided on the outer side of the head portion 14.
A muffler 26 that communicates with the intake hole 6 and an air cleaner 27 that communicates with the intake hole 17 are connected to each other, and a fuel inlet 28 that is connected via piping to a fuel tank (not shown) is provided. is connected to a fuel injection device described below.

Details of the fuel injection system are shown in FIG.

That is, a plunger type pump casing 29 is embedded and fixed inside the head portion 14, and the injection nozzle 18 is formed at the tip thereof. Inside this pump casing 29, there is a Rocker arm 3.
A plunger 32, which is driven forward and backward by a spring 31 and biased to return to a backward position by a spring 31, is fitted inside the plunger 32. A group of small holes 34 are formed around the circumference of the plunger chamber 33 formed in the pump casing 29, and are opened when the plunger 32 is retracted.
This group of small holes 34 is connected to the intake hole 17 via an annular groove 35 and a passage 36.

A fuel control valve 37 whose opening degree is adjusted is provided in the intake system passage 36. The fuel control valve 37 includes a fixed sleeve 38 located on the rotational axis P of the cylinder case 3 and embedded in the head 14, and a tapered needle that moves back and forth along the axis P with respect to the fixed sleeve 38. 39, the fuel inlet 28 is communicated with the inside of the sleeve 38 via a flow path 40, an annular groove 41, and a communication hole 42, and the space between the sleeve 38 and the needle 39 is opened by moving the needle 39 back and forth. By adjusting the opening degree, the amount of fuel flowing into the passage 36 of the intake system is adjusted.

The needle 39 is configured to be controlled to advance and retreat by a mechanical governor. This governor is
A governor spring 43 that presses the needle 39 in a direction that increases the opening of the control valve 37, and a governor weight 4 that generates a governor force that presses the needle 39 in a direction that decreases the opening of the control valve.
4, and is configured to be able to set the speed by adjusting the forward and backward movement of a spring receiving rod 45 that receives the rear end of the governor spring 43 using a speed regulating arm 46. The speed regulating arm 46 is linked to a speed regulating lever (not shown) via a release wire 47.

The governor weight 44 is attached to the cylinder case 3
It is housed in a recess 48 formed eccentrically with respect to the rotation axis P at the rear end, and is pivotably supported on a bracket 49 screwed and fixed to the cylinder case 3. An arm 44a connected from the governor weight 44 is brought into contact with the tip of a push rod 39a connected from the needle 39, so that the centrifugal force (governor force) of the governor weight 44 is transmitted to the needle 39. There is.

The rocker arm 30 for driving the plunger is supported by a ball fulcrum 51 formed integrally with the head cover 50, and one end of the arm 51 is connected to the push rod 5.
2 to one end of the bell crank 53,
Furthermore, the other end of this bell crank 53 is provided with a ball 5 on the outer periphery of a cam 54 which is integrally formed with the rear cylinder shaft case 5.
5, and the plunger 32 is driven to reciprocate once for each rotation of the cylinder case 3. The tip of the rocker arm 30 on the plunger side is engaged in a recess 57 of an abutment piece 56 that is driven and fixed to the rear end of the plunger 32, thereby preventing the rocker arm 30 from swinging laterally.

The engine according to the present invention is constructed as described above, and its operation will be explained next.

The cylinder case 3 is rotated clockwise in FIG. 5, and the intake/exhaust port 15 overlaps the exhaust hole 16, and both pistons 8, 8 move toward each other to perform exhaustion, and then the intake/exhaust port 15 overlaps with the exhaust hole 16. The exhaust port 15 overlaps with the intake hole 17, and both pistons 8, 8 move away from each other due to centrifugal force, so that the cylinder 7
Air is taken in and then enters the intake compression stroke.

Then, before this intake compression stroke is completed, the plunger 32 is driven backward and forward once, and the spring 31
Air is rapidly sucked into the plunger chamber 33 by the retreat of the plunger 32 via the control valve 3 due to the negative pressure generated in the passage 36 at this time.
Fuel is sucked in from 7 and mixed with the air while being atomized. The air-fuel mixture thus formed flows into the plunger chamber 33 through the group of small holes 34, and atomization of the fuel is further promoted at this time. Then, due to the forced advance of the plunger 32, the plunger chamber 33
A certain amount of the air-fuel mixture within is compressed and becomes a high-pressure, high-temperature air-fuel mixture.

After this air-fuel mixture compression is completed, the intake/exhaust port 15 of the cylinder case 3, which has completed the intake compression stroke, is connected to the nozzle 1.
8, the high-pressure, high-temperature air-fuel mixture in the plunger chamber 33 is ejected into the high-temperature compressed air in the cylinder 7, and the explosion and expansion stroke begins. During this explosion and expansion stroke, the plunger 32 is held at the final advance (compression) position, and the combustion gas is maintained in a state where it is prevented from flowing into the plunger chamber 33.

Then, following the explosion and expansion stroke, the engine moves to the exhaust stroke, and this cycle is repeated thereafter.

The intake/exhaust port 15 and the head portion 1 when the cylinder 7 is in the intake compression stroke and the explosion expansion stroke.
4, a thrust ring 59 with a seal ring 58 is fitted into the stepped portion of the mouth edge of the intake/exhaust port 15, and the internal pressure of the cylinder 7 is transferred between the front parts of the thrust ring 59. 60, the thrust ring 59 is brought into close contact with the head portion 14.

Further, on the end surface of the head portion 14, the air intake/exhaust port 1 is provided.
An annular groove 61 for collecting gas leaked from the groove 6 is formed, and a part of the groove 61 is communicated with the intake hole 17 via a passage 62.
The cylinder 7 is configured to return the gas recovered in the cylinder 1 to the cylinder 7 together with the intake air.

Incidentally, lubricating oil is stored in the main body case 1 to lubricate various sliding and rolling parts.

[Another Embodiment] In the embodiment, 54 is a circumscribed type, but it can also be configured to be an inscribed type.

The cam 54 can also be implemented as a side cam with a cam profile formed on the side surface near the outer periphery.

The cam 54 is inserted into the intermediate case 6 of the cylinder case 3.
It can also be formed integrally with the

In a type in which the exhaust hole 16 and the intake hole 17 are provided with intake/exhaust valves, a large-diameter valve operating cam similar to the fuel injection cam 54 may be provided in the cylinder case 3.

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional side view of the engine according to the present invention;
Figure 2 is a longitudinal front view, Figure 3 is an enlarged sectional view of the fuel injection device, Figure 4 is a front view from the head side,
FIG. 5 is a front view of the head portion taken longitudinally. 1...Body case, 3...Cylinder case, 8
...Piston, 14...Head part, 15...Intake/exhaust port, 16...Exhaust hole, 17...Intake hole, 53...
...Operating member, 54...cam.

Claims (1)

[Scope of utility model registration request] A cylinder case 3 equipped with a reciprocating piston 8 is rotatably supported on the main body case 1, and an intake/exhaust port 15 formed on the end face of the cylinder case 3 is an exhaust hole formed on the end face of the head portion 14 in the main body case 1. 16, and an engine configured to have circulation communication with the intake hole 17, a large-diameter cam 54 is provided near the outer periphery of the cylinder case 3, and the cam 54 presses and drives an operating member 53 for fuel injection. An engine fuel injection system configured to