JP3117801B2 - Engine lubricant supply device - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a lubricating oil supply device for an engine mounted on a motorcycle or the like, and more particularly, to automatically supply an appropriate amount of lubricating oil to an engine according to the operating condition of the engine. Device for

[0002]

2. Description of the Related Art A conventional lubricating oil supply device is disclosed, for example, in Japanese Patent Application Laid-Open No. 62-258111.

[0003] According to this, a cylindrical distributor is rotatably supported around the axis of a pump case of a hydraulic pump, and a plunger is fitted into the distributor so as to be reciprocable in the axial direction. The space surrounded by the inner surface of the distributor and the fitting end of the plunger is a pump chamber, and the distributor rotates with the driving of the engine, and the rotation causes the plunger to reciprocate. Then, the lubricating oil discharged from the pump chamber with the reciprocation of the plunger is supplied to the lubricated portion of the engine.

In the above case, if the supply amount of the lubricating oil is simply linearly proportional to the number of revolutions of the engine, the supply amount of the lubricating oil may be inappropriate. Then, in the above-mentioned prior art, it is constituted as follows.

That is, a stopper is provided to abut on the plunger to adjust the stroke of the plunger.
This stopper is connected to the throttle grip by a wire. As the operation amount of the throttle grip increases, the supply amount of the lubricating oil is added, and an appropriate amount of the lubricating oil is supplied at each rotation speed.

[0006]

In the conventional lubricating oil supply apparatus, the stopper for adjusting the stroke of the plunger and the throttle grip are connected by a wire as described above. It is difficult for a motorcycle, which is a narrow space, to arrange the wires, that is, the assembly of the lubricating oil supply device to the vehicle body is complicated. In addition, there is a problem that the freedom of layout of the lubricating oil supply device in the vehicle body is reduced due to the routing of the wires.

In addition, there is also a problem that the operation of the throttle grip becomes heavy by the amount corresponding to the actuation of the stopper.

[0008]

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned circumstances, and has been made easy to assemble to a vehicle body and the like, and has improved layout flexibility.
An object of the present invention is to provide a lubricating oil supply device for an engine in which the operability of a throttle grip is not reduced when an appropriate amount of lubricating oil is supplied.

[0009]

The lubricating oil supply device for an engine according to the present invention for achieving the above object is as follows.

[0010] The invention according to claim 1, as illustrated in FIGS. 1 to 7, the cylindrical distributor 2 to the pump case 22
6 is rotatably supported about its axis 25, and the plunger 3 is reciprocally movable in the distributor 26 in the axial direction.
6 and a space surrounded by the inner surface of the distributor 26 and the fitting end of the plunger 36 is formed in a pump chamber 38.
When the engine 1 is driven, the distributor 26 rotates and the plunger 36 reciprocates, and the lubricating oil discharged from the pump chamber 38 with the reciprocation of the plunger 36 causes the lubricated portion of the engine 1 to be lubricated. In the lubricating oil supply device for an engine provided with a stopper 37 that abuts against the plunger 36 and adjusts the stroke of the reciprocating motion of the plunger 36,

An oil chamber 43 is formed in the pump case 22 around the axis 25 of the distributor 26, and an interlocking body 58 which rotates in the oil chamber 43 in conjunction with the distributor 26 is provided. 58 receives the stirring resistance from the lubricating oil 19 in the oil chamber 43 by the rotation thereof, and is relatively displaced with respect to the distributor 26 ;
The stopper 37 is linked to the linking member 58 .

As shown in FIGS. 8 to 11, a second embodiment of the present invention provides a pump case 22 with a cylindrical distributor.
26 is rotatably supported around its axis 25.
Plunger reciprocating in the axial direction inside the distributor 26
36 and the inner surfaces of these distributors 26
The space surrounded by the fitting end of the plunger 36 is
8 and the above distribution
The plunger 36 reciprocates as the table 26 rotates.
So that the plunger 36 reciprocates.
The lubricating oil discharged from the pump chamber 38
So that the plunger 36 contacts the plunger 36.
Adjust the reciprocating stroke of the lever plunger 36
Engine lubricating oil supply device with a stopper 37
And

An oil chamber 43 is formed in the pump case 22 around the axis 25 of the distributor 26, and a sphere 67 is accommodated in the oil chamber 43 in a freely rotatable manner.
7 is provided, and is interlocked with the distributor 26 and rotates in the oil chamber 43 in conjunction with the distributor 26. The spherical body 6 is engaged with the interlocking body 58 and rotates in the oil chamber 43.
7 receives the resistance from the interlocking member 58 so as to relative displacement with respect to the distributor 26, the interlocking member
The stopper 37 is interlocked with 58 .

[0014]

The operation according to the first aspect of the invention is as follows.

[0015] The terms in parentheses described below correspond to the terms of claim 1 in the claims section.

When the engine 1 operates, the engine 1
The lubricating oil 19 is supplied to the lubricated portion 6 of the engine 1 from the pump chamber 38 by reciprocating the plunger 36 in conjunction with the distributor 26.

In conjunction with the distributor 26, the block
The blade (interlocking body) 58 rotates in the oil chamber 43,
The mode (interlocking body) 58 lubricates the oil chamber 43 by its rotation.
Receives resistance from oil 19 and sends to distributor 26
The above blades (sequentially displaced relative to
The stopper 37 interlocks with the moving body 58 to adjust the stroke of the plunger 36 in the reciprocating motion.

Therefore , for example, if the stroke of the plunger 36 is made longer as the speed of the engine 1 increases, the supply amount of the lubricating oil 19 is made to be linearly proportional to the number of revolutions of the engine 1 as compared to the case where Thus, the supply amount of the lubricating oil 19 in the high-speed rotation range can be increased. In this way,
An appropriate amount of lubricating oil 19 can be supplied to each of the low and high speed rotation ranges.

[0019] by, according to the lubricating oil supply device 20, a wire extending from the throttle grip provided prior to the hydraulic pump is not required.

[0020]

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

(Embodiment 1)

FIGS. 1 to 6 show a first embodiment of the first invention.

In FIG. 2, reference numeral 1 denotes a single-cylinder two-cycle engine mounted on a motorcycle.
Has a cylinder 2, a piston 3, a crankcase 4, and a crankshaft 5. Each cylinder 2 has an intake port 6 and an exhaust port 7, respectively. Reference numeral 8 denotes a spark plug.

A carburetor 10 is connected to the intake port 6. The carburetor 10 has a piston valve 11, which is urged by a spring 13 in a direction to close an intake passage 12 of the carburetor 10.

The piston valve 11 is connected to a throttle grip 17 via a wire 16. The intake passage 12 is opened and closed by the operation of the piston valve 11 accompanying the turning operation of the throttle grip 17, that is, the throttle opening is adjusted. As the throttle opening increases, more air-fuel mixture is sucked into the cylinder 2.

Reference numeral 18 denotes a lubricating oil tank, and a lubricating oil supply device 20 for supplying lubricating oil 19 in the lubricating oil tank 18 to the cylinder 2 through the intake port 6 is provided. The lubricating oil supply device 20 includes a plunger type hydraulic pump 21, which interlocks with the crankshaft 5 to suck the lubricating oil 19 in the lubricating oil tank 18 and discharge it to the engine 1. I do.

The hydraulic pump 21 will be described with reference to FIG. 1 and FIGS. For convenience of explanation,
The direction of arrow Fr in FIG.

1 and 3, the hydraulic pump 21 has a pump case 22 made of aluminum. The pump case 22 has a cylindrical case body 23 screwed to the outer wall of the crankcase 4. It has.
An inner hole 24 of the case body 23 extends back and forth, and a distributor 26 is fitted into the inner hole 24 on the axis 25 of the inner hole 24. The distributor 26 is rotatable around the axis 25.

The pins 27 projecting from the case body 23
Of the distributor 26 is fitted into a circumferential groove 28 formed on the outer periphery of the distributor 26, thereby restricting the axial movement of the distributor 26 with respect to the case body 23. The front end of the distributor 26 is linked to the crankshaft 5 by a worm gear 29.

A cylindrical body 31 is fitted into the inner hole 24 at the rear part of the case main body 23 on the axis 25.
The rear portion of the distributor 26 is rotatably fitted around the axis 25 in one inner hole 32. The rear end of the inner hole 24 of the case main body 23 is closed by a cover 33 pressed into the inner hole 24.

The rear part of the distributor 26 has a cylindrical shape, and the plunger 36
However, a stopper 37 is fitted into the front part so as to be reciprocally movable in the axial direction, and a pump chamber 38 is formed in the inner hole 34 between the plunger 36 and the stopper 37.

A first spring 3 is provided between the plunger 36 and the stopper 37 so as to urge them apart from each other.
9 and the plunger 36 is connected to the pump chamber 3.
8 is provided, and a second spring 40 biasing the
The spring 40 has an urging force sufficiently larger than that of the first spring 39.

The pump chamber 38 is connected to the distributor 2
A communication hole 42 is formed in the distributor 26 so as to communicate with the outside of the distributor 6. An annular oil chamber 43 is formed around the axis 25 of the distributor 26 in the middle of the inner hole 24 before and after.

A supply hole 44 connected to the oil chamber 43 is formed in the case main body 23. The supply hole 44 is connected to the lubricating oil tank 18 by a supply pipe 45 shown in FIG.
The lubricating oil 19 in the lubricating oil tank 18 is supplied to the oil chamber 43 by the supply hole 44 and the supply pipe 45.

At a certain rotation angle of the distributor 26, the suction hole 4 for communicating the oil chamber 43 with the communication hole 42 at the same time.
7 is formed on the cylindrical body 31. In addition, this suction hole 4
7, the pump case 2 is located at a radially symmetric position of the axis 25.
2, a discharge hole 48 is formed, and the discharge hole 48 communicates with the intake port 6 as a lubricated part through a discharge pipe 49 and a one-way valve 50 in FIG. The oil chamber 4
2 communicates with the lubricating oil tank 18 in FIG. 2 by a breather pipe 51 to prevent air from remaining in the hydraulic pump 21.

On the other hand, at the rear end of the distributor 26, a cam projection 52 is formed at one location around the axis 25, and a cam shaft 53 which engages with the cam projection 52 is protruded from the plunger 36. I have. Also, this camshaft 5
3 is slidably fitted in a regulating groove 54 formed at the rear end of the cylindrical body 31 so as to prevent the plunger 36 from rotating together with the distributor 26.

When the crankshaft 5 is rotated by the operation of the engine 1, the distributor 26 is rotated via the worm gear 29 in the direction indicated by the arrow A in FIG. With this rotation, when the cam projection 52 is cam-engaged with the cam shaft 53, the plunger 36 is opposed to the second spring 40.
Is moved backward, the plunger 36 is separated from the stopper 37, and the pressure in the pump chamber 38 becomes negative. At this time, the communication hole 42 communicates with the suction hole 47, and the lubricating oil 19 in the suction hole 47, the oil chamber 43, and the supply hole 44 is sucked into the pump chamber 38 (FIG. 1). Arrow B).

Further, when the distributor 26 rotates and the cam engagement of the cam projection 52 with the cam shaft 53 starts to be released, the plunger 36 is actuated by the second spring 40.
Is moved back toward the pump chamber 38, and the pump chamber 38 is pressurized. At this time, the communication hole 42 communicates with the discharge hole 48 as shown in FIGS. Therefore, the lubricating oil 19 in the pump chamber 38 is discharged into the discharge hole 48 (arrow C in FIG. 1), and is supplied to the intake port 6 through the discharge pipe 49 and the one-way valve 50. Lubrication is performed.

Thereafter, the above operation is repeated to supply the lubricating oil supply device 20.

In FIG. 1 and FIGS. 4 to 6, the distributor 26 has a bearing hole 5 penetrating in the radial direction corresponding to the front end of the inner hole 34 of the distributor 26.
The rotary shaft 57 is rotatably fitted in the bearing hole 56 so as to be rotatable around its axis. A blade 58, which is an interlocking body, is screwed to one end of the rotating shaft 57 with a bolt 59, and the blade 58 is located in the oil chamber 43. The blade 58 is urged by a helical spring 60 in one direction around the axis of the rotating shaft 57.

Referring particularly to FIG. 4, a concave portion 55 into which a part of the blade 58 is fitted is formed on the outer surface of the distributor 26. A first stopper surface 55a is formed at one end of the concave portion 55, and a second stopper surface 55b is formed at the other end.

When the blade 58 is urged by the helical spring 60 to rotate in one direction around the axis of the rotary shaft 57 and rotate to the position shown by the solid line in FIG. 55a abuts the blade 58 to prevent further rotation. In this case, the blade 58 in contact with the first stopper surface 55a is inclined with respect to the axis 25 as shown by a solid line in FIGS.

The blade 5 is rotated in the opposite direction to the helical spring 60 around the axis of the rotary shaft 57.
When the blade 58 is rotated to the position shown by the two-dot chain line in FIG.
5b abuts the blade 58 to prevent further rotation.

That is, the first and second stopper surfaces 55
a and 55b determine the rotatable range of the blade 58.

A notch 6 is provided in the middle of the rotating shaft 57.
1 is formed, and the rotary shaft 5 corresponding to the notch 61 is formed.
The front end of the stopper 37 is in pressure contact with the outer surface of 7.

When the engine 1 operates and the distributor 26 rotates in conjunction with the engine 1 as described above, the blade 58 is moved with the distributor 26.
Rotates in the oil chamber 43. At this time, the blade 58 opposes the helical spring 60 due to the stirring resistance received from the lubricating oil 19 in the oil chamber 43, and rotates around the axis of the rotating shaft 57 in the direction opposite to the rotation direction of the distributor 26 (arrow A in the drawing). In other words, the blade 58 is displaced relative to the distributor 26.

When the rotating shaft 57 rotates with the blade 58, the notch 6 formed in the rotating shaft 57
1 is engaged with the stopper 37, that is, the stopper 37 is interlocked with the blade 58.

This will be described more specifically.

1, 5 and 6, when the engine 1 is running at a low speed, the blade 58 associated therewith has a small stirring resistance received from the lubricating oil 19 in the oil chamber 43. In this case, as shown in FIG. 6, the front end of the stopper 37 is in contact with the outer peripheral surface of the rotating shaft 57 and is moved to the rearmost position.

The plunger 36 is also moved backward by being pushed by the stopper 37. For this reason, the engagement amount of the cam projection 52 with the cam shaft 53 is reduced, and the stroke of the plunger 36 is reduced accordingly, that is, the discharge amount of the lubricating oil 19 by the hydraulic pump 21 is suppressed to be small.

On the other hand, when the engine 1 rotates at a high speed, the stirring resistance of the blade 58 associated therewith from the lubricating oil 19 in the oil chamber 43 increases. Then, as shown by the alternate long and short dash lines in FIGS.
Gradually and largely engages with the notch 61, and the stopper 37 moves forward as the engine 1 speeds up.

Then, as the stopper 37 moves forward, the amount of engagement of the cam projection 52 with the cam shaft 53 gradually increases, and the stroke of the plunger 36 increases accordingly. That is, the lubricating oil 19 by the hydraulic pump 21
Is increased in a curved manner.

That is, according to the above configuration, the supply amount of the lubricating oil 19 becomes more linear as the speed increases, as compared with the case where the supply amount of the lubricating oil 19 is simply linearly proportional to the rotation speed of the engine 1. In this way, an appropriate amount of lubricating oil 19 is supplied to each of the low and high speed rotation ranges. If the shape of the notch 61 is variously selected, the corresponding characteristic of the supply amount of the lubricating oil 19 can be obtained.

Also, regardless of whether the operating condition of the engine 1 is low or high, when the plunger 36 enters the distributor 26 at the maximum, the front end of the plunger 36 always comes into contact with the rear end of the stopper 37, and the pump chamber 38
Is extremely small. For this reason, even if air bubbles enter the pump chamber 38 during the operation of the hydraulic pump 21,
When the plunger 36 enters the maximum state and the volume of the pump chamber 38 becomes extremely small, the air bubbles are discharged from the pump chamber 38 together with the lubricating oil 19.

Therefore, since the bubbles are prevented from remaining in the pump chamber 38, an appropriate amount of the lubricating oil 19 corresponding to the stroke of the plunger 36 is always discharged and supplied to the engine 1.

1 and 3, a first oil hole 62 and a second oil hole 63 are formed to connect the oil chamber 43 and the suction hole 47 to the rear of the inner hole 32 of the cylindrical body 31, respectively. Thereby, the engaging portion between the cam projection 52 and the cam shaft 53 is lubricated by the lubricating oil 19.

In FIG. 4, the blade 58 may be made of a shape memory alloy. In this case, when the lubricating oil 19 is at a low temperature, the effective area of the blade 58 'is reduced as shown by the dashed line in the figure. . This prevents the supply amount of the lubricating oil 19 from becoming excessive at the time of starting or the like.

Although the above description is based on the illustrated example, the suction hole 4
7 and two discharge holes 48 are alternately provided at an angle of 90 ° around the axis 25, and the plunger 36 is moved two strokes per rotation of the distributor 26.
The lubricating oil 19 can be supplied alternately to each cylinder of the two-cylinder engine.

(Example 2)

FIG. 7 shows a second embodiment of the first invention.

Note that components and operations common to this embodiment and the first embodiment of the first invention are denoted by the same reference numerals in the drawings, and redundant description thereof will be omitted. Will be described.

In the figure, the supply hole 44 is directly connected to the suction hole 47 without passing through the oil chamber 43. The breather pipe 51 is connected to a rear part of the inner hole 32 of the cylindrical body 31. On the other hand, the oil chamber 43 is filled with another lubricating oil 64 having a viscosity different from that of the lubricating oil 19.
Is connected to another breather tube 65.

In the above configuration, if another lubricating oil 64 having a high viscosity is used, even if the hydraulic pump 21 is small and the oil chamber 43 is small, even if the blade 58 cannot be made sufficiently large, stirring can be performed. The resistance can be made sufficiently large, and thus the supply amount of the lubricating oil 19 can be made appropriate. If sufficient stirring resistance cannot be obtained, countless small steel balls may be mixed into the oil chamber 43.

In the above case, the lubricating oil 19 is
The gap between the inner surface of the inner hole 32 of the cylindrical body 31 and the outer surface of the distributor 26 is made sufficiently small so as not to be mixed.

When the oil chamber 43 is filled with the other lubricating oil 64, first, the distributor 26 is incorporated into the case body 23, and the space between the two (the oil chamber 4) is provided.
3) to about 90% of the other lubricating oil 64,
The cylindrical body 31 having an O-ring fitted on the outer periphery is pushed into the space while being fitted around the distributor 26. At this time, air is vented from the other breather pipe 65, and then the other breather pipe 65 is closed with a stopper (not shown). Thereby, another lubricating oil 64 for the oil chamber 43 is provided.
Is completed.

(Embodiment 3)

FIGS. 8 to 11 show an embodiment of the second invention.

Note that the components and operations common to this embodiment and the first embodiment of the first invention are denoted by the same reference numerals in the drawings, and redundant description thereof will be omitted, and different components will be mainly described. Will be described.

In FIGS. 8 and 9, the suction hole 47 includes four first to fourth suction holes 47a to 47d.

Since the suction hole 47 is constituted by many suction holes as described above, the following operation and effect can be obtained. That is, the suction hole 4
7 is only one as in the first embodiment, when the blade 58 rotates to move the stopper 37 backward, the time during which the lubricating oil 19 is locked in the pump chamber 38 becomes longer, During that time, the stopper 37 becomes difficult to move, and the responsiveness is reduced. However, in the third embodiment,
As described above, since the suction holes 47 are formed of many suction holes, the time during which the lubricating oil 19 is locked is shortened, and the responsiveness is improved.

In the oil chamber 43, a steel mass sphere 67 is freely rotatably accommodated. On the other hand, the blade 58 as an interlocking body can be engaged with the sphere 67 by rotating together with the distributor 26.

The rotating end of the blade 58 is directed forward in the direction of rotation of the distributor 26 (arrow A in each drawing, the direction of rotation being opposite to that of the first and second embodiments). It is urged by a winding spring 68.

A C-shaped stopper 69 is fitted on the distributor 26. The stopper 69 is fixed to the distributor 26 by a stopper pin 70 which is inserted through the stopper 69 and press-fitted into one end of the support hole 56.

A first stopper surface 71 is formed at one end of the stopper 69, and a second stopper surface 72 is formed at the other end. Then, the first stopper surface 71 and the second stopper
The rotation shaft 57 is located between the stopper surfaces 72.

Then, as described above, the blade 58
Is urged by the helical spring 68 to rotate the rotary shaft 5.
7, the first stopper surface 71 of the stopper 69 contacts the blade 58 as shown by a solid line in FIGS. 8, 10 and 11. As shown in FIG. Contact to prevent further rotation.

In this case, as shown in FIG.
When viewed in the axial direction, the angle between the blade 58 and a virtual line 74 orthogonal to the axis 25 is θ.

When the blade 58 is rotated around the axis of the rotary shaft 57 in the opposite direction to the helical spring 68, the blade 58 is shown by a two-dot chain line in FIG. When rotated to the posture, the stopper 69
The second stopper surface 72 abuts the blade 58 to prevent further rotation.

That is, the first and second stopper surfaces 71,
Reference numeral 72 designates a rotatable range of the blade 58.

When the engine 1 operates and the distributor 26 rotates in conjunction therewith, the blade 58 rotates in the oil chamber 43 with the distributor 26. At this time, the blade 58 receives stirring resistance from the lubricating oil 19 in the oil chamber 43.

The blade 58 engages the sphere 67 by the above rotation, and rotates the sphere 67 about the axis 25 of the distributor 26 in the oil chamber 43. At this time, the blade 58 Receive.

Then, the blade 58 is moved by the above two resistances.
Against the helical spring 68, around the axis of the rotating shaft 57,
The blade rotates in a direction opposite to the rotation direction of the distributor (arrow A in the figure), that is, the blade 58 is displaced relative to the distributor.

When the blade 58 engages the sphere 67 as described above, the angle θ
Is set within a range such that it can rotate around the axis of the rotating shaft 57 against the helical spring 68. More specifically,
The center 67a of the sphere 67 is located within the range of the angle θ.

When the rotary shaft 57 rotates with the blade 58, the stopper 37 engages with the notch 61 formed on the rotary shaft 57.
The stopper 37 is linked to the blade 58.

This will be described more specifically.

8, 10, and 11, when the engine 1 is at a very low speed, the blade 58 interlocked with the engine 1 receives little resistance from the lubricating oil 19 and the sphere 67 in the oil chamber 43. And in this case,
As shown in FIG. 6, the front end of the stopper 37 is
And is moved most rearward. Further, the plunger 36 is pushed by the stopper 37.
Has also been moved backwards. For this reason, the engagement amount of the cam projection 52 with the cam shaft 53 is reduced, and the stroke of the plunger 36 is reduced accordingly, that is, the discharge amount of the lubricating oil 19 by the hydraulic pump 21 is suppressed to be small.

When the speed of the engine 1 is slightly increased from the above state, and particularly when the size of the pump 21 is small, the stirring resistance of the lubricating oil 19 received by the blade 58 does not increase so much. However, the blades 5 intersecting at an acute angle
Due to the fact that the sphere 67 enters the wedge shape between the sphere 8 and the stopper 69 and the rolling friction due to the centrifugal force of the sphere 67 increases, the resistance that the blade 58 receives from the sphere 67 increases by the rotation speed of the distributor 26. To increase. Accordingly, the blade 58 responds to this, and the blade 58 rotates around the axis of the rotation shaft 57 in the direction opposite to the rotation direction (arrow A) of the distributor 26 against the helical spring 68 of the above. I do.

Then, along with this, the stopper 37 slightly engages with the notch 61, and the stopper 37 moves slightly forward.

As the stopper 37 moves forward, the amount of engagement of the cam projection 52 with the cam shaft 53 gradually increases, and the stroke of the plunger 36 increases accordingly. In other words, even when the speed of the engine 1 is slightly increased from a low speed, the stroke of the plunger 36 responds to this accurately, and the discharge amount of the lubricating oil 19 from the pump 21 is increased in a curved line with high accuracy.

Further, when the engine 1 rotates at a high speed, the blade 58 associated therewith rotates the lubricating oil 19 in the oil chamber 43.
And the ball 67 receives a large resistance. The subsequent operation is the same as in the first embodiment. Therefore, it is possible to appropriately supply the lubricating oil 19 over the entire low and high speed regions of the engine 1.

A plurality (about 2 to 5) of the spheres 67 having the same diameter may be provided. If the number is appropriately selected, the resistance of the blade 58 to the spheres 67 can be changed to provide lubrication. The supply amount of the oil 19 can be arbitrarily selected. Furthermore,
Instead of the interlocking member, the blade 58 may be a simple rod-shaped member that does not receive much agitation resistance of the lubricating oil 19.

[0091]

According to the present invention, the following effects are obtained.

According to the first aspect of the present invention, a cylindrical distributor is supported on a pump case so as to be rotatable around its axis, and a plunger is fitted into the distributor so as to be reciprocally movable in the axial direction. The space surrounded by the fitting end is the pump chamber,
The distributor rotates with the driving of the engine and the plunger reciprocates, and the lubricating oil discharged from the pump chamber is supplied to the lubricated portion of the engine with the reciprocating motion of the plunger. In an engine lubricating oil supply device provided with a stopper that abuts against a plunger to adjust the stroke of the reciprocating motion of the plunger,

In the pump case, the distribution
The oil chamber is formed around the axis of over motor, the distributor
An interlocking body that rotates in the oil chamber in conjunction with the
The interlocking member rotates the lubricating oil in the oil chamber to stir
To be displaced relative to the distributor
The stopper is linked to the linking member.

For this reason, when the engine operates,
The distributor rotates with the engine, and
Plunger reciprocates in conjunction with this distributor
The lubricating oil is supplied from the pump chamber to the lubricated parts of the engine.
It is.

Interlocked with the distributor
Rotates in the oil chamber, and this interlocking body rotates the oil chamber
Resistance to the above distributors
Relative to the interlocking body that is displaced in this way.
The plunger moves in conjunction with the
Is adjusted.

Thus , for example, if the stroke of the plunger is made longer as the engine speed increases, the rotational speed of the lubricating oil is increased in comparison with the case where the supply amount of the lubricating oil is simply linearly proportional to the engine speed. The supply amount of the lubricating oil in the region can be increased, and in this way, an appropriate amount of lubricating oil can be supplied to each of the low and high speed rotation regions.

[0097] by, according to the lubricating oil supply device, since the wire extending from the throttle grip provided prior to the hydraulic pump is not necessary, the wiring is also required, thus, this to the vehicle body such as The lubricating oil supply device can be easily assembled and the degree of freedom in layout can be improved.

Further, the adjustment of the stroke of the plunger for supplying an appropriate amount of lubricating oil to the engine can be automatically obtained by the interlocking body rotating in the oil chamber in conjunction with the engine. That is, since the interlocking member does not interlock with the throttle grip, the operability of the throttle grip is prevented from being reduced.

Further, the wear of the interlocking member is prevented by the lubricating oil in the oil chamber , which is beneficial for the life of the lubricating oil supply device.

According to a second aspect of the present invention, the pump case has a cylindrical shape.
Supports the distributor so that it can rotate around its axis
And is axially reciprocated in this distributor.
Insert the ranger and fit inside of these distributors
The space surrounded by the fitting end of the plunger is the pump chamber,
The distributor rotates as the engine runs.
The plunger to reciprocate and
The water discharged from the pump chamber with the reciprocation of the lang
Make sure that lubricating oil is supplied to the lubricated parts of the engine.
The plunger is brought into contact with the plunger to
Engine lubricating oil with a trowel adjustment stopper
In the supply device,

An oil chamber is formed in the pump case around the axis of the distributor, and a sphere is freely rotatably accommodated in the oil chamber. The sphere can be engaged with the sphere and interlocked with the distributor. the interlocking member to rotate in the oil chamber is provided, receives the resistance from the sphere to rotate the interlocking member engaged with the oil chamber, the interlocking member is so displaced relative to the distributor, the above interlocking member Strike
The hopper is linked .

For this reason, the structure common to the first aspect of the present invention is provided.
In addition to effects arising from the formation, the interlocking body, the spherical body
A large resistance can be received from the sphere according to the weight and size, and accordingly , the relative displacement of the interlocking body with respect to the distributor can be further increased.

Therefore, the accuracy of adjusting the stroke of the plunger by the stopper is improved, and the amount of the lubricating oil supplied can be made more appropriate, because the stopper is more interlocked with the interlocking body.

[Brief description of the drawings]

FIG. 1 is a partially enlarged sectional view of FIG. 2 in Example 1.

FIG. 2 is a simplified schematic side view of the first embodiment.

FIG. 3 is a cross-sectional view taken along line 3-3 of FIG. 1 in the first embodiment.

FIG. 4 is a partial cross-sectional view taken along line 4-4 of FIG. 1 in the first embodiment.

FIG. 5 is a partial sectional view taken along line 5-5 in FIG. 4 in the first embodiment.

FIG. 6 is a partial cross-sectional view taken along line 6-6 of FIG. 1 in the first embodiment.

FIG. 7 is a diagram corresponding to FIG. 1 in the second embodiment.

FIG. 8 is a diagram corresponding to FIG. 1 in the third embodiment.

9 is a cross-sectional view taken along line 9-9 of FIG. 8 in the third embodiment.

FIG. 10 is a partial view of the third embodiment taken along line 10-10 of FIG. 8;

11 is a cross-sectional view taken along line 11-11 of FIG. 10 in the third embodiment.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Engine 6 Intake port (lubricated part) 19 Lubricating oil 20 Lubricating oil supply device 22 Pump case 25 Shaft 26 Distributor 36 Plunger 37 Stopper 38 Pump room 43 Oil chamber 58 Blade (interlocking body) 67 Sphere

Claims (2)

(57) [Claims] A cylindrical distributor is rotatably supported around an axis of a pump case, and a plunger is fitted into the distributor so as to be reciprocally movable in the axial direction.
A space surrounded by the inner surface of the distributor and the fitting end of the plunger is used as a pump chamber, and the distributor rotates and the plunger reciprocates as the engine is driven. in the lubricating oil to be supplied to the lubricated portion of the engine, the lubricating oil supply device for an engine provided with a stopper for adjusting the stroke of the reciprocating motion of the plunger in contact with the plunger to be discharged from the upper Symbol An oil chamber is formed around the axis of the distributor in the pump case, and an interlocking body that rotates in the oil chamber in conjunction with the distributor is provided, and the interlocking body is stirred by the rotation from the lubricating oil in the oil chamber. in response to resistance so as to relative displacement with respect to the distributor, the communication
The lubricating oil supply device for an engine according to claim 1 , wherein the stopper is interlocked with a moving body . 2. A cylindrical distribution in a pump case.
The rotor is rotatably supported around its axis.
A plunger is inserted into the viewer so that it can reciprocate in the axial direction,
The inner surface of these distributors and the fitting end of the plunger
The space enclosed by and is used as the pump room,
The above distributor turns and the above plan
The plunger reciprocates, and the plunger reciprocates
As a result, the lubricating oil discharged from the pump chamber
So that it is supplied to the lubrication section,
Adjust the reciprocating stroke of the lever plunger
In the lubricating oil supply device for an engine provided with a stopper, an oil chamber is formed around the axis of the distributor in the pump case, and a sphere is freely rotatably accommodated in the oil chamber and can be engaged with the sphere. And an interlocking body that rotates in the oil chamber in conjunction with the distributor, receives resistance from the sphere that rotates in the oil chamber by engaging with the interlocking body, and the interlocking body is displaced relative to the distributor. And the stopper is interlocked with the interlocking body.
Lubricating oil supply device for an engine that has.