JP3060165B2 - Link mechanism of fuel injection 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 link mechanism used for linking movable members of a fuel injection device. One link member has two planes parallel to each other, and the other link member has the two planes. The present invention relates to a link mechanism including an engagement pin that is engaged between flat surfaces and has a contact portion formed on a curved surface.

[0002]

2. Description of the Related Art For example, a control sleeve which is externally fitted to a plunger of a fuel injection pump and adjusts an injection amount and the like is slidably adjusted in the axial direction of a plunger by a governor. See
As shown in Japanese Patent Application Laid-Open No. 1-61959, a ball pin is eccentrically provided at a shaft end of an electromagnetic governor, the ball pin is engaged with an engagement concave portion of the control sleeve, and the control sleeve is rotated by rotating the governor shaft. The type in which the plunger is displaced in the axial direction is widely used.

[0003] In the engaging recess of the control sleeve, two parallel planes extending in the direction perpendicular to the axial direction of the plunger are formed, and the ball pin is engaged between the two planes. The peripheral surface of the contacting ball pin is a curved surface, and conventionally, the radius of curvature of this curved surface is 2.
It was almost half the distance between the planes. That is, the conventional ball pin has a substantially spherical shape or a shape obtained by cutting a spherical non-contact portion.

[0004] Such a link mechanism using a ball pin is used in a link portion between various actuators and members connected to the actuators. In addition, regardless of the type of pump, a distribution type fuel injection pump (VE) is used. Pumps, VR-type pumps) and row-type injection pumps.

[0005]

However, since the ball pin and the two planes sandwiching the ball pin are in point contact with each other, the surface of the ball pin is easily worn and the backlash between the ball pin and the plane is increased. Originally, a play is provided between the ball pin and the flat surface to ensure smooth sliding, as long as the control accuracy is not impaired. Electrically controlled products such as an electromagnetic governor have a large influence, and are automatically corrected to obtain a predetermined injection state.

Since the wear of the ball pin cannot be completely avoided, in order to reduce the above-mentioned inconveniences, the ball pin is enlarged to suppress the progress of the wear, or the ball pin is formed into a cylindrical shape and the abutting portion is pointed. It is also conceivable to change the line to a line and disperse the force applied to the ball pin. But,
In many cases, it is not possible to increase the size of the ball pin due to the structure of the link.If the pin is made cylindrical, even if the axis of the pin is slightly inclined, the edge of the pin will hit the flat surface, and wear will concentrate on this edge, and rather wear The amount will increase.

In view of the above, the present invention provides a link mechanism of a fuel injection device which can secure stable control by suppressing deterioration of injection control over time due to wear without increasing the size of a conventional ball pin. The challenge is to do.

[0008]

In order to solve the above-mentioned problems, a link mechanism of a fuel injection device according to the present invention has a first plane having two planes parallel to each other at a predetermined interval.
And the engagement member slidably engaged between the two planes.
A second movable member having a mating pin;
Means that the axis is formed parallel to the two planes
Both portions that are in contact with the two planes are formed as curved surfaces.
When transmitting the motion of the movable member to the other movable member,
In the case where the portion abutting on the two planes is displaced in the circumferential direction, the curved surface of the engaging pin is made equal in distance from the axis in the circumferential direction, and the radius of curvature in the axial direction is 1 / th of the distance between the two planes. It is set to be larger than 2 (claim 1).

As a link mechanism constituted by the first and second movable members, an engagement recess is formed in a control sleeve of a VE type injection pump or a VR type injection pump, and a ball pin provided on a governor is connected to the recess. A link point for engaging the cam ring of the VR type injection pump and the control sleeve with a predetermined phase relationship, a timing rod for controlling the pre-stroke of the row type injection pump, and an actuator for rotating the timing rod. And a link between an injection amount adjusting rod for adjusting the effective stroke of the row injection pump and an actuator for moving the rod forward and backward.

The two planes parallel to each other of the first movable member are the inner surfaces of the holes in which the engaging pins are engaged, even if the inner walls of the recesses or grooves have a plane covering the engaging pins. Alternatively, it may be constituted by the inner periphery of a rectangular notch provided in the plate-shaped member.

Therefore, since the radius of curvature of the curved surface of the engaging pin in the axial direction is set to be larger than that of the spherical surface between the engaging pin and the two planes, the contact caused by slight deformation or wear at the contact point. The area is larger than in the case of a spherical surface, and the dimensional change in the radial direction due to wear can be reduced.

In order to suppress wear, the radius of curvature may be increased. However, the larger the radius of curvature, the closer the engagement pin becomes to a columnar shape, which induces an edge contact between the plane and the edge of the engagement pin. Would. For this reason, it is necessary to determine the radius of curvature which can reduce the dimensional change in the radial direction due to the wear over time and can avoid the edge contact. Preferably, the radius of curvature is 3/2 times to 10 times the distance between the two planes.
It is desirable to set within the range of / 2 times (claim 2).

[0013]

Embodiments of the present invention will be described below with reference to the drawings. FIG. 1 shows a main part of a VR-type fuel injection pump. In the fuel injection pump 1, fuel is introduced into a chamber 2 via a feed pump (not shown). The distal end of the distribution member 3 is rotatably inserted into a barrel 5 arranged and fixed to the pump housing 4. The distribution member 3 has a base end 3a connected to a drive shaft 6 via a coupling so that only rotation is allowed in synchronization with the engine. Also, at the base end 3a of the distribution member 3,
The plunger 7 is slidably inserted in the radial direction (radial direction).

In this embodiment, two plungers 7 are provided at an interval of, for example, 180 degrees on the same plane, and the tip of each plunger 7 is provided at the center of the base end of the distribution member 3. And the base end of the plunger 7 is connected to the shoe 9 and the roller 1.
The inner surface of the ring-shaped cam ring 11 is slidably contacted through the “0”. This cam ring 11 is used for the distribution member 3.
, And cam lobes corresponding to the number of cylinders of the engine are formed inside, and when the distribution member 3 rotates, each plunger 7 reciprocates in the radial direction (radial direction) of the distribution member 3, The volume of the compression chamber 8 is made variable.

The distribution member 3 has a vertical hole 12 formed in the axial direction thereof and leading to the compression chamber 8, an inflow / outflow port 13 communicating with the vertical hole 12, and opening to the peripheral surface of the distribution member 3, and a barrel. 5 and distribution passage 14 formed in pump housing 4
And a distribution port 15 for allowing communication between the vertical hole 12 and the vertical hole 12. A control sleeve 16 disposed in the chamber is provided in the distribution member 2 with an inflow / outflow port 13.
Is slidably inserted so as to cover.

As shown in FIG. 2, an engaging recess 17 extending in a direction perpendicular to the axis of the distributing member 3 is formed on the upper portion of the control sleeve 16, and the lower end of the engaging recess 17 is formed with respect to the axis of the distributing member 3. And a vertical groove 18 extending in parallel. The control sleeve 16 has a suction / cutoff hole (not shown) that can communicate with the inflow / outflow port 13 of the distribution member 3.

The control sleeve 16 has an engagement pin 22 provided eccentrically at the tip of the shaft 21 of the electric governor 20 and is engaged with the engagement recess 17. When the shaft 21 is rotated by an external signal, the control sleeve 16 is rotated. The distribution member 3 is displaced in the axial direction.
The engaging recess 17 of the control sleeve 16 has two planes 17a which are parallel to each other with a width substantially equal to the diameter of the engaging pin 22.
And the engagement pin 22
It is engaged so as to contact the flat surface 17a.

A slide pin 24 connected to a timer piston 23 of a timer device provided below the cam ring 11 is formed integrally with the cam ring 11, and a locking piece 25 extending toward the center of rotation of the cam ring 11 is formed on the lower inner peripheral edge. Are fixed by screws or the like. The timer piston 23 is slidably housed in a cylinder 26 formed in the housing, and moves the timer piston 23 in the cam ring 11
, And changes the injection timing.

At one end of the timer piston 23, there is formed a high-pressure chamber into which high-pressure fuel in the chamber is introduced, and at the other end, a low-pressure chamber communicating with the suction path of the feed pump.
A timer spring is elastically mounted in the low-pressure chamber to constantly urge the timer piston 23 toward the high-pressure chamber. Therefore,
The timer piston 23 stops at a position where the spring pressure of the timer spring and the oil pressure in the high-pressure chamber are balanced, and when the high-pressure chamber pressure increases, the timer piston 23 moves toward the low-pressure chamber against the timer spring, and the cam ring 11 Are rotated in a direction to advance the injection timing, and the injection timing is advanced. When the high-pressure chamber pressure becomes low, the timer piston 2
3 moves to the high-pressure chamber side, the cam ring 11 is rotated in a direction to delay the injection timing, and the injection timing is delayed.
The pressure in the high-pressure chamber is adjusted by a timing control valve (TCV) so as to obtain a required timer advance angle.

A link member 27 rotatably held by the barrel 5 is provided below the control sleeve 16 described above.
Are provided, and the cam ring 11 is
And the control sleeve 16 are connected. The link member 27 is pivotally supported by the barrel 5 and extends in parallel with the distribution member 3, a first arm portion 29 extending radially from one end of the base shaft 28 on the cam ring side,
Second arm portion 30 extending radially from the center of base shaft portion 28
It is composed of The first arm portion 29 is provided at its tip with an engagement pin 31 projecting in parallel with the axis of the base shaft portion 28, and this engagement pin 31 is engaged with the cutout recess 32 of the locking piece 25. I have.

The notch recess 32 is formed in the cam ring 11.
And has two parallel flat surfaces 32a radially extending with a width substantially equal to the diameter of the engagement pin 31. The engagement pin 31 has a predetermined play and has a predetermined play. 32a.

The second arm 30 is connected to the base shaft 28.
When the base shaft 28 rotates, the base shaft 28 rotates integrally therewith. When the base shaft 28 rotates integrally therewith, the end extending in the same direction as the first arm portion 29 extends parallel to the axis of the base shaft 28. A mating pin 33 is provided, and the engaging pin 33 is engaged with the vertical groove 18 of the control sleeve 16. This second
The vertical groove 18 with which the arm portion 30 engages also has two flat surfaces 18a formed in the width substantially equal to the diameter of the engagement pin 33 and extending in parallel with the axis, and the engagement pin 33 has a predetermined play. And comes in contact with the two planes 18a.

The link mechanism between the electric governor 20 and the control sleeve 16 and the cam ring 1
As shown in FIG. 3, the engaging pins 22, 31, 33 used in the link mechanism between the control sleeve 1 and the control sleeve 16 have flat surfaces 17a, 18a,
The axis is parallel to 2a, and the planes 17a, 1
The portions that come into contact with 8a and 32a are displaced in the circumferential direction. Each of the engaging pins 22, 31, and 33 has a barrel shape in which the distance from the axis in the circumferential direction is equal, and the distance from the axis in the axial direction is small at both ends, and has a radius of curvature in the axial direction. (= R) is 1 / the distance between the two planes
2 (= r), and in this embodiment, each link member is made of steel, the distance between the two planes is 6 mm, and the radius of curvature of the engaging pins 22, 31, 33 in the axial direction. Is set to about 7 times (R ≒ 7r) r (= 3 mm).

In the above configuration, when the distribution member 3 rotates, the plunger 7 is moved by the cam ring 11 to the distribution member 3.
In the suction step in which the plunger 7 reciprocates in the radial direction and moves in a direction away from the center of the cam ring 11,
Inflow / outflow port 13 and control sleeve 16
The cut-off holes are aligned with each other, and the fuel in the chamber 2 is sucked into the compression chamber 8. Thereafter, the plunger 7 is moved to the cam ring 1
When the pumping process moves toward the center of the pump 1, the communication between the inflow / outflow port 13 and the chamber 2 is cut off, the distribution port 15 is aligned with one of the distribution passages 14, and the compressed fuel is supplied to the distribution passage 14. The fluid is discharged to the delivery valve via the valve 14. The fuel delivered from the delivery valve is sent to an injection nozzle via an injection pipe (not shown), and is injected from the injection nozzle into a cylinder of the engine. Then, when the next inflow / outflow port 13 communicates with the chamber 2 through the suction / cutoff hole of the control sleeve 16 during the pressure feeding process, the compressed fuel flows out to the chamber 2 at a stretch, and the injection ends.

At the timing when the inflow / outflow port 13 and the chamber 2 communicate with each other, that is, at the end of injection, the electric governor 20 controls the distribution of the control sleeve 16 by the distribution member 3.
Can be controlled by displacing in the axial direction. Therefore, the engagement pin 22 is worn and the engagement recess 17
When the backlash with the inner surface 17a becomes large, the control of the end of the injection, that is, the control of the injection amount becomes unstable, but the radius of curvature in the axial direction of the peripheral surface of the engagement pin 22 is set to be large. Because the contact point is slightly deformed,
In the case of slight wear, the contact area between the engagement pin 22 and the two flat surfaces 17a becomes larger than in the case of the spherical body shown by the broken line in FIG. The dimensional change of the engagement pin can be made smaller than before.

Therefore, the rattling at each link point is prevented from increasing with time, and the electric governor 2
In the link structure between the cam ring 11 and the control sleeve 16, it is possible to maintain stable control of the injection amount, and in the link structure between the cam ring 11 and the control sleeve 16, it is possible to suppress a temporal shift in the injection timing control. Can be.

In the configuration of R # 7r described above, as a result of various endurance tests (durability test of the link mechanism itself, endurance test of the injection pump alone, endurance test of the actual vehicle by mounting the injection pump on the vehicle, etc.), the engagement pin It has been confirmed that the abrasion loss of the bearing has been reduced to 1/3 or less of the conventionally used spherical engaging pin, and it is possible to realize stable injection control that is sufficiently acceptable for long-term use. Becomes In order to reduce the influence of wear, theoretically, the radius of curvature should be larger than half the distance between the two planes. However, as a practical range that comprehensively considers the results of the durability test and the like. Preferably satisfies R ≧ 3r.

As the radius of curvature is increased, the effect of reducing wear is reduced. However, since the link mechanism has a certain amount of play, the edge of the engagement pin may hit the plane when the radius of curvature is increased. I am concerned. This edge contact has been confirmed for those having an R of 16r or more. Since it is actually necessary to set R in anticipation of wear over time, a practical range in which the edge contact can be avoided is R It is preferable that ≦ 10r. In the end, if an optimal range that can reduce wear and avoid edge contact is planned, R should be 3 times r to 1 time.
It has been found that it is desirable to be within the range of 0 times.

The above-described link structure for engaging the engagement pin between the two planes is not unique to the VR type injection pump, but is often used in a VE pump, a row type injection pump, and the like. Examples of row injection pumps are shown in FIGS.

In the row type injection pump 40, a vertical hole 42 is formed in a pump body 41, and a plunger 44 is slidably inserted into a plunger barrel 43 provided in the vertical hole 42. The upper end of the plunger 44 is inserted into a valve housing 45 fixed to the main body 41, and a delivery valve 46 is provided in the valve housing 45.
A high-pressure chamber 47 is formed between the fuel cell and the delivery valve 46, and a fuel outlet 48 is formed in the main body 41 above the delivery valve 46. The lower end of the plunger 44 is in contact with a cam 50 formed on a cam shaft 49 via a tapet 51. The cam 50 is, for example, a tangential cam, and cooperates with the return spring 52 to reciprocate the plunger 44 along the contour of the cam 50.

The plunger 44 has a face 53.
The face portion 53 is engaged with a rotary sleeve 54 fitted on the plunger barrel 43. An engaging pin 55 is fixed to the flange of the rotary sleeve 54, and the engaging pin 55 is engaged with a notch 57 formed in a rod 56 for adjusting the injection amount (see FIG. 6B). The plunger 44 is rotated in response to the movement of the injection amount adjusting rod 56, so that the relative position in the circumferential direction between the plunger 44 and a control sleeve 58 described below can be changed. .

The control sleeve 58 is slidably fitted on the plunger 44 by a fuel reservoir 59 communicating with a fuel inlet (not shown) formed in the main body 41. A timing rod 60 is inserted into the main body 41, and the timing rod 60 is engaged with the control sleeve 58 so that the control sleeve 58 can be moved up and down.

The control sleeve 58 has a spill port 6
A fuel passage 64 communicating with the high pressure chamber 47 and the fuel reservoir 59 is formed in the plunger 44 in the axial direction and the radial direction of the plunger 44, and has an intake port 65 and opens to the fuel reservoir 59. doing. In addition, plunger 44
A lead 66 is formed obliquely on the outer periphery of the device. This lead 66 is connected to a suction port 65 via a vertical groove 67 formed in the plunger 44.

In the above configuration, when the camshaft 49 rotates by receiving a torque from the internal combustion engine, the plunger 44 reciprocates along the contour curve of the cam 50. Plunger 44
When the pressure rises from the bottom dead center, the high-pressure chamber 47 communicates with the fuel reservoir 59 via the fuel passage 64 of the plunger 44 and the suction port 65, so that the fuel is not pumped. Then, the plunger 44 rises to move the suction port 6
When 5 is closed by the lower edge of the control sleeve 58 (the position of the plunger 4 at this time has begun to be pumped), the fuel in the high-pressure chamber 47 is trapped, the pressure increases, and the delivery valve 46 is closed. Open to start pumping actual fuel. The distance from the bottom dead center of the plunger 44 to the start of pumping is a pre-stroke, and the pre-stroke is a control sleeve 58.
It is adjusted by changing the vertical position of.

When the plunger 44 further rises, the lead 66 of the plunger 44 is connected to the spill port 63 of the control sleeve 58 (the position of the plunger 4 at this time is the end of the pressure feeding), and the high pressure is reached. The chamber 47 is the fuel passage 6
4, communicating with the fuel reservoir 59 through the suction port 65, the vertical groove 67, the lead 66, and the spill port 63;
Is returned to the fuel reservoir 59, the pressure of the fuel in the high-pressure chamber 47 is rapidly reduced, and the pumping of the fuel is terminated. The distance of the plunger 44 from the start of the pumping to the end of the pumping is the effective stroke, and the effective stroke is the plunger 44.
It is adjusted by changing the position in the rotation direction of.

The timing rod 60 extends in a direction perpendicular to the axis of the plunger 44 and is rotatably supported by the pump body 41. The timing rod 60 and the control sleeve 58 are engaged with the timing rod 60. An engaging pin 61 protruding in the radial direction is fixed to the engaging pin 6.
1 is an engaging recess 62 formed on the peripheral surface of the control sleeve 58.
Is configured to be engaged. The contact portion of the engaging pin 61 with the engaging concave portion 62 is spherical, and when the timing rod 60 rotates, the engaging pin 61 also rotates about the axis of the rod, and the control sleeve 58 is moved to the plunger 44.
In the axial direction.

One end of the timing rod 60 protrudes from the pump main body 61.
As shown in FIG. 2, a U-shaped link 70 having a U-shape is fixed. Inside the U-shaped link 70, two surfaces 70a facing each other in parallel are formed, and an engaging pin 73 provided eccentrically at the tip of the output shaft 72 of the prist actuator 71 between the two planes. Is engaged.
The engagement pin 73 is formed to be substantially equal to the groove width of the U-shaped link 70, and when the output shaft 72 is rotated by driving the prist actuator 71, the engagement pin 73 is rotated about the axis of the output shaft 72. Then, the U-shaped link 70 is rotated to rotate the timing rod 60 by the rotation angle of the U-shaped link 70. .

An electromagnetic governor 74 shown in FIG. 6A is mounted on the pump body 41.
4, the advance / retreat amount of the injection amount adjusting rod 56 is adjusted. This injection amount adjusting rod 56 is
The linear actuator 78 extends in a direction perpendicular to the axis of the plunger 44 and projects into a casing 75 of the electromagnetic governor 74 via a link member 77 rotatably fixed to a support portion 76 formed in the casing 75. Is connected to the movable body 79.

That is, the linear actuator 78 is fixed in the casing, and the coil 81 is placed inside the cylindrical magnet 80.
Is arranged so as to be movable up and down, and the amount of movement of the movable body 79 is adjusted by energizing the coil 81. The link member 77 has two arms 82 and 83 integrally formed, and an engaging pin 84 provided at a free end of one arm 82 extends in a horizontal direction formed on the movable body 79. The engagement pin 86 is engaged with the hole 85 and is formed at the free end of the other arm 83.
6 is engaged with a long groove 87 formed at the end.

In the long hole 85 and the long groove 87, a parallel plane for engaging the engaging pins 84 and 86 with a predetermined play is formed inside, and the engaging pins 84 and 86 are rotated by the rotation of the link member 77. It moves while being guided on this plane. Therefore, when the movable body 79 moves up and down, the link member 77 rotates, and the injection amount adjusting rod 56 advances and retreats in the horizontal direction.

The link mechanism used in the link mechanism between the above-described pre-stroke control and the timing rod 60 and the link mechanism between the linear actuator 78 and the injection amount adjusting rod 56 which control the effective stroke. The mating pins 73, 84, and 86 have the shape shown in FIG. 3 that is in contact with the two planes, and the contact points with the planes are displaced in the circumferential direction of the engagement pins. In this configuration example, each link member is made of steel, and a groove width (U-link 70) is formed at a link portion between the prist actuator 71 and the timing rod 60.
The distance between the two planes is set to 6 mm, the radius of curvature of the engagement pin 73 in the axial direction is set to R ≒ 7r, and the two link portions connecting the linear actuator 78 and the injection amount adjusting rod 56 have two planes. The distance between them (the width of the long hole 85 and the long groove 87) is set to 5 mm, and the radius of curvature of the engaging pins 84 and 86 in the axial direction is set to R = 4r.

Even in such a configuration, the engagement pin 7
The rattling of the link portions does not increase due to the wear of 3, 84, 86 over time, stable stroke control can be performed, and the edge of the engaging pin does not contact, and the durability is improved. And high control accuracy can be maintained.

The shape of the above-described engaging pin is a link structure in which the axis of the engaging pin is parallel to the two planes regardless of the movement of the link mechanism, that is, the sliding contact point with the plane of the engaging pin is the axial line. The present invention is applied to a link structure displaced in the circumferential direction around the center, and is particularly effective in a link portion where the influence of wear is large, but can be similarly used in a portion where the influence of wear is small. For example, the same configuration can be applied to a link between the notch 57 of the injection amount adjusting rod 56 and the engaging pin 55 of the rotating sleeve 54 as shown in FIGS. 4 and 6B. .

[0044]

As described above, according to the present invention,
Since the radius of curvature of the engagement pin in the axial direction is larger than 1/2 of the distance between the two planes on which the engagement pin engages, the radial dimensional change due to wear over time is smaller than that of the conventional engagement pin. It is possible to reduce the variation of the injection amount and the injection timing due to wear, and to stabilize the injection control.

Although the shape of the peripheral surface of the engagement pin is changed, the size of the engagement pin is not changed.
It can be compatible with the conventional link mechanism, and since the engaging pin is usually formed by grinding with a grindstone, it can be handled only by increasing the radius of curvature of the grindstone shape, and the conventional manufacturing There is no need to change the process.

In particular, by setting the radius of curvature of the engaging pin in the axial direction to be 3/2 to 10/2 times the distance between the two planes, it is possible to achieve both reduction of wear and avoidance of edge contact.

[Brief description of the drawings]

FIG. 1 is a cross-sectional view showing a main part of a VR type fuel injection pump using a link mechanism according to the present invention.

FIG. 2 is a perspective view showing a link portion used in the distribution type fuel injection pump of FIG. 1;

FIG. 3 is an explanatory view showing an engagement pin engaged between two planes.

FIG. 4 is a sectional view showing a row type fuel injection pump using the link mechanism according to the present invention.

FIG. 5 is a view showing a link mechanism between a prist actuator and a timing rod for controlling the control sleeve shown in FIG. 4;

6 (a) shows a link mechanism between a linear actuator for controlling the rotary sleeve shown in FIG. 4 and an injection amount adjusting rod 16, and FIG. 6 (b) shows an injection amount adjusting rod 16; FIG. 5 is a perspective view showing a state in which an engagement pin 15 of a rotating sleeve is engaged with the notch of FIG.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 11 Cam ring 16 Control sleeve 17 Engagement concave part 18 Vertical groove 20 Electric governor 22, 31, 33, 55, 73, 84, 86 Engagement pin 25 Locking piece 32 Notch concave part 56 Injection amount adjusting rod 57 Notch 60 Timing Rod 70 U-link 71 Pristo actuator 77 Link member 78 Linear actuator 79 Movable body 85 Long hole 87 Long groove

──────────────────────────────────────────────────続 き Continuation of the front page (51) Int.Cl. ⁷ identification code FI F02M 59/28 F02M 59/28 G (58) Investigated field (Int.Cl. ⁷ , DB name) F02D 1/02 F02M 41 / 14 F02M 59/28

Claims (2)

(57) [Claims] 1. A plurality of parts which are parallel to each other at a predetermined interval.
A first movable member having a plane and a sliding contact between the first movable member and the two planes;
A second movable member having an engagement pin engaged therewith.
The axis of the engagement pin is flat with respect to the two planes.
A part formed in a row and in contact with the two planes is a curved surface
And the movement of one movable member to the other
The part that contacts the two planes during transmission is displaced in the circumferential direction
In the link mechanism of the fuel injector to the curved surface of the engaging pin, the are distance equal formed from the axis in the circumferential direction, greater than half the distance between the radius of curvature the two planes in the axial direction A link mechanism for a fuel injection device, comprising: 2. The fuel injection device according to claim 1, wherein the radius of curvature in the axial direction is set within a range of 3/2 to 10/2 times the distance between the two planes. Link mechanism.