JPH0526059A - Fuel injection timing controller - Google Patents

Abstract

PURPOSE:To perform advancing/delaying operation with a small force by making the force necessary for the advancing/delaying operation independent of the driving torque of a fuel injection pump. CONSTITUTION:A controller 18 for regulating the rotating phase between a driving shaft 2 and a driven shaft 3 to regulate fuel injection timing is provided between the driving shaft 2 connected to the output shaft of an engine and the driven shaft 3 connected to the cam shaft of a fuel injection pump 17. In the fuel injection timing controller 18, a radial driving claw 6 provided on the shaft end of the driving shaft 2 and a radial driven claw 7 provided on the shaft end of the driven shaft 3 are mutually paired, and a spacer 8 is interposed between the both. The spacer 8 is formed successively stepwise in the axial direction, guided and moved by a ring guide groove 11. The guide groove is formed with a part being separated from the shaft center, and a phase changing means 14 is provided on the farthest position to move the spacer 8, regulating the spacer width. The advancing and delaying operation is conducted by the phase changing means 14 regardless of driving torque, and an extremely small force suffices for this operation.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a fuel injection timing adjusting device for a fuel injection pump used in a diesel engine or the like.

[0002]

2. Description of the Related Art Diesel engine output shaft (crank shaft)
Between the drive shaft connected to the drive shaft and the driven shaft connected to the cam shaft of the row-type fuel injection pump, the rotational phases of the drive shaft and the driven shaft are adjusted to adjust the fuel injection timing of the fuel injection pump. A fuel injection timing adjusting device (timer) is provided.

20 (a) and 20 (b) schematically show a flyweight type centrifugal timer a. As shown in the figure, the centrifugal timer a includes a drive rotating portion b provided on a drive shaft that interlocks with a crankshaft, a driven rotating portion c provided on a driven shaft, and a drive rotating portion b and a driven rotating portion b. It is composed of an interposed weight d and a spring e for biasing the weight d in the axial direction. According to this structure, when the engine rotates at a low speed, the weight d is pressed by the urging force of the spring e to enter the non-advanced state shown in FIG. 20 (a), and when the engine rotates at a high speed, the weight d springs due to the centrifugal force. The urging force of e is overcome to move radially outward, and the advance angle state shown in FIG. That is, when the engine rotates at a high speed, the weight d that receives the centrifugal force overcomes the drive torque of the fuel injection pump to generate an advance torque in the weight d, which causes the timer a to advance.

That is, in order to advance the above-mentioned timer a, it is necessary to generate a large advance torque in the weight d that overcomes the drive torque of the fuel injection pump.

[0005]

By the way, in recent years, high-pressure injection of fuel injection pressure has been promoted for purification of exhaust gas, and along with this, the drive torque of the fuel injection pump has increased. Therefore, in order to operate the timer a, a very large advance torque that overcomes the increased fuel injection pump drive torque is applied to the weight d of the timer a.
Must be caused to. That is, the weight d must be heavy and the radius of the center of gravity must be large, which causes a problem that the entire timer a becomes large and heavy.

On the other hand, a hydraulic electronic timer is known (for example, Japanese Patent Application Laid-Open No. 60-261939 "Fuel injection timing adjusting device"). This type of electronic timer has a piston that is operated by the hydraulic pressure supplied to the inside thereof, and a spring attached to the piston so as to oppose the supplied hydraulic pressure. When the hydraulic pressure supplied to the inside of the timer is small, the piston lags the fuel injection pump by the biasing force of the spring, and when the hydraulic pressure is large, the supplied hydraulic pressure overcomes the biasing force of the spring to cause the piston to pump the fuel injection pump. Is advanced.

Even in such a hydraulic electronic timer, it is necessary to increase the output of the hydraulic piston in the timer substantially in proportion to the driving torque of the fuel injection pump.
If high-pressure injection of the fuel injection pump is advanced, it is necessary to increase the size of the hydraulic piston and raise the minimum hydraulic pressure of the hydraulic source.
That is, the problem of increasing the size of the timer cannot be avoided, and the problem of having to secure a larger hydraulic pressure source arises.

The object of the present invention devised in view of the above circumstances is to make the force necessary for the advance / retard operation independent of the drive torque of the fuel injection pump, and to advance / retard with a small force. An object of the present invention is to provide a fuel injection timing adjusting device that can be operated.

[0009]

To achieve the above object, the present invention is provided between a drive shaft connected to an output shaft of an engine and a driven shaft connected to a cam shaft of a fuel injection pump. A device for adjusting a fuel injection timing by adjusting a rotational phase of a shaft and a driven shaft, wherein a radial drive pawl provided at a shaft end of the drive shaft and a radial driven claw provided at a shaft end of the driven shaft. Claws, spacers respectively provided between the driving claws and the driven claws, and formed in a stepwise manner in the axial direction, and formed so as to guide the movement of the spacers and partly move away from the shaft center. An annular guide groove and a phase change means for adjusting the spacer width by moving the spacer in the axial direction are provided at positions where the guide groove is farthest from the shaft center.

[0010]

According to the above construction, since the spacer is provided between the drive claw of the drive shaft and the driven claw of the driven shaft, the rotation of the drive shaft is transmitted to the driven shaft through this spacer. Therefore,
By changing the spacer width of the spacer (stepped), the rotation phases of the drive shaft and the driven shaft are changed.

The spacer width of the spacer is adjusted as follows.

The spacer rotates while being guided by the annular guide groove while being sandwiched between the driving pawl and the driven pawl while the drive / driven shaft is rotating. Here, since the guide groove is formed in an annular shape in which a part of the guide groove is away from the shaft center, the distance between the drive claw and the driven claw becomes the widest at the position where the guide groove is the farthest from the shaft center.・ The spacer that is sandwiched between the driven claws is free (the state where no drive torque is applied). Therefore, at this position, the spacer having the step-shaped spacer is adjusted by axially moving the spacer in which the phase changing means is free. As a result, the rotation phase of the drive / driven shaft changes.

As described above, since the phase changing means moves the spacer which is free (the state where no driving torque is applied) to change the rotational phase of the drive / driven shaft, the advance angle can be advanced with a small force regardless of the driving torque. -Can be operated with a retard angle.

[0014]

An embodiment of the present invention will be described below with reference to the accompanying drawings.

FIG. 2 is a schematic side view of the fuel injection timing adjusting device 1 (timer), and FIG. 1 is a schematic view taken along the line AA of FIG. As shown in the figure, a drive shaft 2 connected to the crankshaft of the diesel engine and a driven shaft 3 connected to the cam shaft of the row-type fuel injection pump are opposed to each other and coaxially arranged. A disk-shaped drive rotor 4 is provided at the shaft end of the drive shaft 2, and a disk-shaped drive rotor 5 is provided at the shaft end of the driven shaft 3. Driving claws 6 are radially provided on the outer circumference of the drive rotor 4, and driven claws 7 are radially provided on the outer circumference of the driven rotor 5. The driving pawl 6 and the driven pawl 7
Are provided in the same number (four in this embodiment) so as to form a pair with each other.

Spacers 8 are provided between the driving claw 6 and the driven claw 7, respectively. These spacers 8 are
As shown in FIGS. 3 and 4, the wide portion 8a having a wide spacer width and the narrow portion 8b having a narrow spacer width are integrally formed in a step shape along the axial direction. Then, either the wide portion 8a or the narrow portion 8b is arranged between the driving pawl 6 and the driven pawl 7. In FIG. 3 and FIG. 4, the narrow portion 8b is the driving / driven pawl 6,7.
The state where it is arranged between is shown. Further, the front and rear surfaces 9 and 10 of the spacer 8 that are in contact with the claws 6 and 7 are formed in a tapered surface shape that narrows toward the axial center in both the wide width portion 8a and the narrow width portion 8b. This taper angle is adjusted to the angle formed by the claws 6 and 7 at the position where the front and rear surfaces 9 and 10 of the spacer 8 are most strongly sandwiched between the claws 6 and 7 (position A in FIG. 1 described later). The tapered surface may not be a flat surface, but may be a curved surface having a long radius curvature so that it can follow a slight angle variation of the claws 6, 7.

The spacer 8 having the above structure is engaged with the guide groove 11 formed in a ring shape around the shaft,
Along with the rotation of 3, it is guided by the guide groove 11 and is rotated while being sandwiched between the driving claw 6 and the driven claw 7. The guide groove 11 is formed in a perfect circle shape, and its center 12 is the axis 13 of the drive / driven shafts 2 and 3.
It is more eccentric downward. For this reason, the guide groove 11 has a gap between the driving claw 6 and the driven claw 7 and the shaft center 13
1 becomes the widest at the position farthest from the position C in FIG. 1, and the guide groove 11 becomes the narrowest at the position A which is the latest from the shaft core 13,
Positions B and D are in the middle of these widths.

Here, as shown in FIG. 1, when the narrow portion 8b of the spacer 8 is sandwiched at the position A where the distance between the claws 6 and 7 is narrowest, the claws at the respective positions B, C and D are shown. The 6 and 7 intervals are as follows. At the position C where the distance between the claws 6 and 7 is widest, the distance between the claws 6 and 7 is wider than that of the wide portion 8 a of the spacer 8. The distance between the claws 6 and 7 at the intermediate positions B and D is wider than the narrow portion 8b of the spacer 8 and narrower than that of the wide portion 8a. Therefore, at positions A, B, and D, when a force is applied to each spacer 8 in the axial direction to cause the spacers 8 to slide, the spacers 8 have a narrow portion 8b and a wide portion 8a.
The stepped portion with and gets caught by the claws 6 and 7 and stops, but at position C
Only the wide part 8a of the spacer 8 can be slid between the claws 6 and 7.

As described above, in order to move the spacer 8 in the axial direction, as shown in FIG. 2, the spacer 8 is moved in the axial direction to the position C where the guide groove 11 is farthest from the shaft core 13. Phase changing means 14 for adjusting the spacer width is provided. The phase changing means 14 is provided with a shoe 15 for pressing the end portion of the spacer 8 in the axial direction. The shoe 15 is operated by an air cylinder (not shown) or the like to move the spacer 8 in the axial direction. It is designed to let you.

The manner of retarding and advancing the timer having the above-described configuration is shown in FIGS. FIG. 5 shows the retarded state. At this time, the narrow portion 8b of the spacer 8 is sandwiched at the position A where the distance between the claws 6, 7 is the smallest, and the claws 6, 7 are
The mutual angle is θ ₁ °. On the other hand, FIG. 6 shows the advanced angle state. At this time, the wide portion 8a of the spacer 8 is sandwiched at the position A where the distance between the claws 6 and 7 is the smallest, and the angle between the claws 6 and 7 is θ ₂ ° (θ ₂ > θ ₁ ). There is. Therefore, in FIG. 6, the angle is advanced by θ ₂ −θ ₁ ° as compared with FIG. That is, the rotational phase angle between the drive shaft 2 and the driven shaft 3 is the position A where the distance between the claws 6 and 7 is the smallest, in other words, the transmission of the substantial rotational torque from the drive shaft 2 to the driven shaft 3 is achieved. It is determined by the spacer width of the spacer 8 sandwiched between the positions A to be formed.

The rotation phase angle is changed from FIG. 5 to FIG. 6 or from FIG. 6 to FIG. 5 as follows. Drive
During rotation of the driven shafts 2 and 3, the spacer 8 rotates while being sandwiched between the pawls 6 and 7 and engaging with the guide groove 11. Here, at the position C in FIG. 1 where the distance between the claws 6 and 7 becomes the widest, the phase changing means 14 slides the spacer 8 in the axial direction to cause the spacer 8 to have a desired thickness (the wide portion 8a or the wide portion 8a). Narrow part 8b) nails 6,7
Put in between. Then, after a half rotation, the spacer 8 reaches the position A where the distance between the claws 6 and 7 becomes the smallest, and at this position, the driving claw 6 and the driven claw 7 have a desired thickness (wide width) of the spacer 8. The portion 8a or the narrow portion 8b) is sandwiched, and the driving torque is transmitted at a phase angle corresponding to the spacer width. In addition, when advancing the angle, as described above, the claws 6, 7
The spacer 8 can be moved only at the position C where the distance is the narrowest, but when retarding, the thinner spacer 8 is used.
Since it is sufficient to insert the narrow portion 8b between the claws 6 and 7, the spacer 8 can be moved at any position A, B, C or D. In this way, the phase angle can be changed while transmitting the rotational torque while the drive / driven shafts 2 and 3 are rotating.

FIG. 7 shows a concrete embodiment based on the above-described principle example. Since this embodiment has substantially the same configuration as the above-described principle example, only different parts will be described. As shown in the drawing, a sprocket 16 that is interlocked with the crankshaft is attached to the end of the drive shaft 2. On the other hand, the driven shaft 3 is connected to the cam shaft of the column fuel injection pump 17. Further, in the figure, reference numeral 18 is a timer main body, 19 is a timer case, and 20 is a bearing that supports the drive / driven shafts 2 and 3. This bearing 20 is a drive / driven shaft 2,
3, the guide groove 11 in the case 19 also supports the reaction force received from the spacer 8. Reference numeral 21 is an oil seal for sealing the lubricating oil in the timer body 18. Reference numeral 14 is a phase changing means, and 15 is a shoe for moving the spacer 8 in the axial direction. This phase changing means 14
The shoe 15 is provided at a position C where the spacing between the claws 6 and 7 shown in FIG. 1 is the widest.
Is shown in. As shown in the drawing, the shoe 15 has a fulcrum 22 on the upstream side in the rotation direction of the claws 6, 7 and an operating point 23 on the downstream side. The fulcrum 22 rotatably supports the shoe 15 on the timer case 19, and the operating point 23 is a piston rod 24 for the shoe 1.
5 is moved in the axial direction. The piston rod 24 is operated by an air cylinder 25 shown in FIG.

The operation of this embodiment having the above configuration will be described.

(1) Advancement operation Now, in the spacer 8, the narrow portion 8b having a small thickness is provided on each of the claws 6, 6.
It is sandwiched between 7 and the phase is on the delay side (state shown in FIG. 7). First, the air cylinder 25 is operated to move the piston rod 24 rightward in the drawing. Then, the shoe 15 is pushed to the right, hits the spacer 8, and pushes it to the right. As a result, the spacer 8 moves to the right, and the space between the claws 6 and 7 is replaced with the wide portion 8a from the narrow portion 8b. At this time, the shoe 15 on the right side in the drawing
Restricts the spacer 8 from overshooting.

The movement of the spacer 8 is carried out at the position C in FIG.
Done in. Thus, when the spacer 8 moved from the narrow portion 8b to the wide portion 8a is rotated about 1/4 turn from the position C to the position D, the pair of claws 6 and 7 sandwiching the spacer 8 are paired with other claws 6,7. Unlike this, since the wide portion 8a of the spacer 8 is only sandwiched between them, the spacer 8 and the two claws 6, 7 are located in this vicinity.
The spaces will come into close contact. Once they come into close contact with each other and rotate a little further, the pair of claws 6 and 7 that tightly sandwich the spacer 8 is only here. Therefore, the rotational torque from the drive shaft 2 to the driven shaft 3 is transmitted by the pair of claws 6 and 7. Will be done.

After that, when the next spacer 8 comes to the position C in FIG. 1, the same procedure as above is repeated. In this way, when all the four pairs of claws 6 and 7 come to sandwich the wide portion 8a of the spacer 8, the operation for advancing ends there, and this advancing state continues until the retarding operation starts thereafter. Maintained.

(2) Retardation operation Now, it is assumed that the spacer 8 has the wide portion 8a with a large thickness sandwiched between the respective claws, and the phase is on the advance side (FIG. 7).
Different state). The air cylinder 25 is operated to move the piston rod 24 leftward in the drawing. Then, the shoe 15 is pushed to the left, hits the spacer 8, and pushes it to the left. As a result, the spacer 8 moves to the left, and the portion between the claws 6 and 7 is replaced by the wide portion 8a of the spacer 8 by the narrow portion 8b. At this time, the shoe 15 on the left side of the drawing restricts the spacer 8 from overshooting.

Thereafter, the spacer 8 between the claws 6 and 7 is sequentially replaced by the wide portion 8a and the narrow portion 8b by performing the operation opposite to the advance operation. In this way, when all four pairs of claws 6 and 7 come to sandwich the narrow portion 8a of the spacer 8, the operation for retarding the angle ends there.

As described above, by moving the spacer 8 at the position C in FIG. 1 in which the phase changing means 14 is free (the state in which the driving torque is not applied), the spacer width is changed and the drive / driven shaft 2, Since the rotational phase of No. 3 is changed, the advance / retard operation can be performed with a small force regardless of the drive torque. That is, since the reaction force of the driving torque of the fuel injection pump 17 is not directly applied to the phase changing means 14, the spacer 8 can be moved with an extremely small force. Therefore, conventionally, when the injection pump 17 was made to have a high-pressure injection, the size, weight, and driving source of the timer had to be necessarily increased because of the increase in the power required for the timer operation. According to this, the power required for the timer operation is not limited to the driving torque and thus may be limited, and the timer body 18 can be made smaller and lighter than the conventional timer. Further, in this embodiment, the air cylinder 25 is used as the drive source of the phase changing means 14, but the present invention is not limited to this, and a step motor, a hydraulic cylinder or the like may be used, so that the timer drive source can be diversified. ..

Modified Embodiment FIG. 10 shows a modified spacer 8 of the previous embodiment. The spacer 8 of the previous embodiment is simply provided between the claws 6 and 7. With this configuration, when the rotational torque is relatively constant, the spacer 8 is pressed against the drive pawl 6 side by a slight friction caused by the sliding in the guide groove 11. Therefore, when the spacer 8 is moved in the axial direction when the space between the claws 6 and 7 becomes the widest, the spacer 8 has a stepped portion (a stepped portion between the narrow portion 8b and the wide portion 8a) which is the driven pawl. It moves normally without getting caught in 7.

However, when the fluctuation of the rotation torque is large, when the fluctuation of the friction is large due to the processing roughness of the sliding surface in the guide groove 11, or when the rotation is very slow and the influence of gravity cannot be ignored. , The spacer 8 is always the driving claw 6
It is not always close to the side. In these cases, when the spacer 8 moves, the step portion between the narrow portion 8b and the wide portion 8a may be caught by the claw 6 or 7 and may not be moved normally.

As a countermeasure, the corners of the claws 6 and 7 are rounded or the stepped portion of the spacer 8 is provided with an inclined surface so that the spacer 8 is forcibly pushed between the claws 6 and 7 by the strong force of the shoe 15. Although it may be pushed in, it is not preferable in consideration of increase in shoe driving force, operation stability, corner wear, and the like.

The modification shown in FIG. 10 solves this problem, and has a construction in which a spacer 8 is axially slidably inserted into either the driving claw 6 or the driven claw 7. The sliding width of the spacer 8 in the axial direction is such that the wide portion 8a and the narrow portion 8b of the spacer 8 can be slid between the claws 6 and 7. According to this configuration, the nails 6,
At a position where the space between the spacers 7 is wider than the width of the spacer 8, the spacer 8 can be easily moved anywhere without any catch.

Modified Example FIG. 11 shows another modified example. As shown, in this modification, the spacer 8 is formed in a multi-step (four steps) stepped shape, and the degree of advance angle can be switched to four steps.

Modified Example In the modified example shown in FIGS. 12 and 13, the length per axial step of the plurality of steps of the spacer 8 is shortened to shorten the overall length, and the side of the claw 7 on which the spacer 8 is sandwiched is shortened. Also, a step surface 26 that is combined with this is provided. According to this configuration, it is possible to increase the advance angle and shorten the axial length of the spacer 8. Furthermore, when transmitting rotational torque,
Since several stages are in contact at the same time, the surface pressure per stage does not increase. In these modified examples,
A multi-stage air cylinder or the like capable of controlling a plurality of stroke positions is used as a drive source (air cylinder 25 shown in FIG. 7) for moving the spacer 8.

Modified Example In a modified example shown in FIG. 14, rollers 27 are provided at both ends of the spacer 8 in the axial direction, whereby the spacer 8 and the guide groove 11 are provided.
It is intended to reduce the sliding resistance between and.

Modified Example In a modified example shown in FIG. 15, each stepped surface 28 (torque transmitting surface 28) of the spacer 8 is provided with an inclination in a direction of decreasing the thickness. This is spacer 1 shoe 1
After changing the position in the axial direction with 5, there is a possibility that the position in the axial direction will be slightly shifted until it is separated from the guide of the shoe 15 and is strongly clamped by the claws 6 and 7 on both sides. It was invented. That is, the step surface 2 of the spacer 8
By forming an inclination in the direction of decreasing the thickness on each of the 8 (torque transmitting surface 28), when the spacer 8 begins to be sandwiched by the claws 6 and 7 on both sides, it naturally slides down toward the bottom of the inclination, By stopping at the adjacent step portion, the spacer 8 is naturally and accurately corrected in its axial position.

Modified Example The modified example shown in FIGS. 16 and 17 is intended to prevent uneven contact of the step surface 28 (torque transmitting surface 28) of the spacer 8 and reduce wear. In the examples so far, the step surface 28 (torque transmission surface 28) of the spacer 8 is formed at a constant angle in advance. Therefore, when the spacer 8 rotates while being sandwiched by the claws 6 and 7, the spacer 8 changes the position in the radial direction along the claws 6 and 7 by the guide groove 11 to thereby form an angle between the claws 6 and 7. Changes, and the stepped surface 28 (torque transmission surface 28) of the spacer 8 hits the pawls 6 and 7 one-sided. To prevent this one-sided hit,
Step surface 28 (torque transmission surface 28) of spacer 8 and claw 6,
At least one of the contact surfaces with 7 may have a structure in which the angle can be freely changed. In this modification, the spacer 8 is divided into a mounting portion 8c for attaching to the claw 6 and a contact portion 8d that comes into contact with the step 29 of the mating claw 7, and these are rotatably coupled to a pin 30. A cylindrical self-aligning mechanism 31 is provided in the. As a result, when the contact portion 8d of the spacer 8 hits the step 29 of the claw 7 on the other side with a one-sided contact, the contact angle is automatically adjusted.

Modified Embodiments In the above-mentioned embodiments, the guide groove 11 has a perfect circular shape. Although this is sufficient for the function, the durability can be improved by changing the shape of the guide groove 11. In the guide groove 11 of the modified example shown in FIG. 18, only the range 11a on the circumference of which the force of the claws 6 and 7 is applied to the spacer 8 to transmit the rotational torque is an arc 32 concentric with the rotary shaft core 13. The circular arc 32 and the remaining circular arc 33 of the guide groove 11 are connected by a smooth curve or straight line. As a result, relative sliding between the spacer 8 and the pawls 6, 7 is eliminated in a range where a strong load is applied between the spacer 8 and the pawls 6, 7, and the reaction force of the guide groove 11 for sliding is reduced, and the spacer 8 It is possible to reduce friction loss on the contact surface between the claws 6 and 7 and the contact surface between the spacer 8 and the guide groove 11, and to reduce wear.

Modified Embodiments In the above-described embodiments, the rotational torque is transmitted only at one location on the circumference of the guide groove 11. On the other hand, in the modification shown in FIG. 19, the rotational torque is transmitted at two points 11b and 11c on the opposite side of the guide groove 11 by 180 ° on the circumference. That is, the guide groove 11 of this modification has an elliptical shape that is long in the horizontal direction in the drawing. According to this configuration,
Two places 11 on the opposite side of the guide groove 11 in the vertical direction 180 °
Rotational torque is transmitted by b and 11c. In the figure, reference numeral 12 is a rotary shaft core. According to this structure, the transmission of the rotational torque is 180 ° on the circumference of the guide groove 11 at the two opposite positions.
Since it is carried out by 1b and 11c, the load and the surface pressure applied to each claw 6, 7 and the spacer 8 are halved, and the reaction force in one direction applied to the bearing 20 of the drive shaft 2 and the driven shaft 3 is balanced on the circumference. Therefore, the load reaction force related to the transmission of the rotational torque applied to the bearing 20 can be canceled to make it zero.

[0041]

As described above, according to the fuel injection timing adjusting device of the present invention, the following excellent effects can be exhibited.

(1) Since the force required for the advance / retard operation is independent of the drive torque of the fuel injection pump,
It can be advanced / retarded with extremely small force.

(2) Therefore, it is possible to promote the reduction in size and weight of the device.

(3) Further, it is possible to diversify the drive source for advancing / retarding.

[Brief description of drawings]

FIG. 1 is a schematic front view of a fuel injection timing adjustment device for explaining the principle of the present invention.

FIG. 2 is a schematic side view of the fuel injection timing adjusting device.

FIG. 3 is a perspective view showing an engagement state of a spacer and a claw of the fuel injection timing adjusting device.

FIG. 4 is a top view showing an engaged state of the spacer and the claw.

FIG. 5 is a schematic diagram showing a retarded state of the fuel injection timing adjustment device.

FIG. 6 is a schematic view showing an advanced state of the fuel injection timing adjusting device.

FIG. 7 is a side sectional view of a fuel injection timing adjusting device as an embodiment of the present invention.

FIG. 8 is a cross-sectional view showing a shoe portion of the fuel injection timing control device (cross-sectional view cut parallel to the axis).

FIG. 9 is a cross-sectional view of the shoe portion (a cross-sectional view taken perpendicular to the axis).

FIG. 10 is a view showing a modified example, and is a perspective view of a claw and a spacer.

FIG. 11 is a view showing another modified example, and is a perspective view of a claw and a spacer.

FIG. 12 is a view showing another modification, and is a perspective view of a claw and a spacer.

FIG. 13 is a top view of FIG.

FIG. 14 is a view showing another modification, and is a perspective view of a claw and a spacer.

FIG. 15 is a view showing another modified example, and is a top view of a claw and a spacer.

FIG. 16 is a view showing another modification, which is a side view of a claw and a spacer.

FIG. 17 is a top view of FIG.

FIG. 18 is a view showing another modified example and is a front view of a guide groove.

FIG. 19 is a view showing another modified example and is a front view of a guide groove.

FIG. 20 is a schematic view showing a fuel injection timing adjusting device (flyweight type centrifugal timer) of a conventional example.

[Explanation of symbols]

 1 Fuel Injection Timing Adjustment Device 2 Drive Shaft 3 Driven Shaft 6 Drive Claw 7 Driven Claw 8 Spacer 11 Guide Groove 14 Phase Change Means 17 Fuel Injection Pump

Claims (1)

1. A drive shaft connected to an output shaft of an engine and a driven shaft connected to a cam shaft of a fuel injection pump,
In a device for adjusting the fuel injection timing by adjusting the rotational phase of the drive shaft and the driven shaft, a radial drive pawl provided at the shaft end of the drive shaft and a radial drive pawl provided at the shaft end of the driven shaft. Driven pawls, spacers respectively provided between the drive pawls and the driven pawls, and formed stepwise in the axial direction, and formed so as to guide the movement of the spacers and partly move away from the shaft center. And an annular guide groove, and a phase changing means for adjusting the spacer width by moving the spacer in the axial direction, the guide groove being provided at a position farthest from the shaft core. Fuel injection timing adjustment device.