JPS6032018B2 - Centrifugal force governor for diesel engines - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a centrifugal force regulator for a diesel engine that has both high and low distance type and full speed type functions, and a Botsch RQV-K type regulator that has only the full speed type function. The aim is to make it possible to obtain high-speed and low-speed functions with simple improvements based on the basic machine.

The present invention will be described below with reference to embodiments shown in the drawings. In FIG. 1, a flyweight 3 guided by a weight guide 2 is attached to a camshaft 1 of a fuel injection pump (not shown), and the movement of the flyweight 3 is caused by rotating an intermediate portion of the flyweight 3 to a crank holder 4 integrated with the camshaft. A governor sleeve 6 is moved by a movably supported bell crank lever 5.
can be conveyed to. An idle spring 7 with an attached load is installed between the weight guide 2 and the fly weight 3, and an idle spring 7 with no attached load is installed between the weight guide 2 and a spring seat 8 fitted with a loose iron to the weight guide 2. A spring 9 is installed. A large-diameter stepped portion 6a is formed in the middle portion of the governor sleeve 6, and a spring capsule 10 forming a sliding portion is assembled on the right side of the stepped portion 6a.
A holding spring 1 for urging the capsule 10 toward the stepped portion 6a is provided, one end of the spring 11 is received by a spring seat 12, and a W nut 13 screwed onto the right end of the governor sleeve 6 is provided. , spring capsule 1
0 and the spring seat i2, that is, the stroke a of the capsule 10 is adjusted. Further, a groove 10a is provided on the outer circumference of the spring capsule 10, and this groove 1
The slider blade 4 is aligned with 0a, and the slider 14 is guided by a screw 5 fixed to the case. The slider 14 has a symmetrical pin 14a as shown in FIG.
The lower part of the floating lever 16 is freely connected to the pin turtle 4a. The floating lever 16 has a long hole 16a in the middle. The lever 18 integrated with the first adjusting lever 17 for the full speed type is replaced with the lever 19.
A pin 20 provided at the tip of the bracket lever 19 is slidably inserted into the elongated hole 16a of the floating lever 16. The second adjusting lever 21 for high and low distance type is the same as the first adjusting lever.
17 and a cancel spring 22. 2
One end of the two adjusting levers 17, 21 is supported by a pin 23 fixed to the governor case,
Both levers 17 and 21 rotate about this pin 23 as a fulcrum.

The cam plate 24, which has a cam groove 24a into which the pin 20 is inserted, is supported at one end by the case so as to be freely extendable, and the other end is urged toward the stopper 26 by a spring 25. The upper part of the floating lever 16 is the shirtcle 27
The torque control cam 30 is connected to the control rack 28 via the pawl 29 near the connection part.
It protrudes opposite the cam surface 30a. A plate 31 that can be moved left and right as shown in the figure is attached to the top of the case, a shaft 32 that can be moved up and down as shown in the figure is attached to the plate 31, and a torque control cam 30 is rotated around a pin 33 provided at the lower end of this shaft 32. The left end of a lever 35 is rotatably connected to a pin 34 provided on this cam 30, and the upper end of a lever 36 is rotatably connected to the right end of this lever 35. The lever 36 is rotatably supported by a pin 37 fixed to the governor case.
The lower end of the governor sleeve 6 is opposed to the left end of the stepped portion 6a of the governor sleeve 6. The pin 37 is rotatably connected to the other end of the switching lever 38, one end of which protrudes outside the case.
One end rotatably connects the other end of a set lever 39 facing the spring capsule 10. This lever 39
The set spring 401 applies a force to rotate counterclockwise, and the stopper 41 integrated with the switching lever 38
This prevents the lever 39 from rotating counterclockwise. Therefore, the gap between the lower end of the lever 39 and the bottom of the spring capsule 10, ie, the stroke b, can be adjusted by the switching lever 38. Reference numeral 42 denotes an adjustment screw 43 which is provided outside the speed governor and restricts the counterclockwise rotation of the switching lever 38. A spring 44 provides a force to rotate the lever bar 36 in the counterclockwise direction. Asia stain lever
A full stopper that restricts the counterclockwise rotation of 17.
45 is a full stopper that restricts the counterclockwise rotation of the second adjusting lever 21; 46 is a lever that rotates together with the second adjusting lever 21; When the lever 21 is rotated clockwise and set to the idling position, it comes into contact with the lever 36 and rotates the lever 36 clockwise. In the above configuration, the full speed type operation will first be explained. In this case, rotate the switching lever 38 clockwise,
This rotates the set lever 39 clockwise and fixes the lever 39 in a state unrelated to the operation of the speed governor. and the first adjusting lever for full speed.
Turn 7 counterclockwise in all directions to make a full stopper. If you set it to 44 and fix it, that is, set it at full load,
When the engine is stopped, the flyweight 3 is closed, so the lower end of the floating lever 16 is located farthest to the right, and the pawl 29 of the floating lever 16 comes into contact with the cam surface 30a of the torque control cam 30, causing the floating lever to close. -16 is determined, and a gap C is generated between the cam plate 24 and the stopper 26. The position of the control rack 28 at this time is represented by point g in FIG. When the number of rotations increases, the flyweight 3 overcomes the load of the idle spring 7 and expands, and from a certain number of rotations it also overcomes the main spring 9 and takes over the ship, moving the governor sleeve 6 to the left.

As the governor sleeve 6 moves to the left, the lever 36 rotates clockwise, the torque control cam 30 rotates counterclockwise about the pin 33, and the pawl 29 follows the cam surface 30a of the control rack. 28 positions are controlled. Here, since the middle part of the cam surface 30a is convex, the position of the control rack 28 is controlled as shown by gh-i-1, -12-i in FIG.
A so-called reverse Angleich characteristic is obtained. In addition, since the gap c is set to disappear when the first adjuster stay lever 17 is supported by the full stopper 44 and reaches the point j in FIG. Rotating clockwise about the pin 20, the control rack 28 moves to the right, that is, in the weight reduction direction, to point k in FIG. 3. When the first adjusting lever 17 is rotated clockwise, the gap c becomes smaller and the rotational speed at which the control rack position becomes zero becomes lower, and the point k in Fig. 3 falls to kl, k2, k3 and reaches full speed. characteristics are obtained.

When the first adjusting lever 17 is further rotated, the gap c disappears, and a state in which the claw 29 of the floating lever 16 is separated from the cam surface 30a of the torque control cam 30 occurs from the rotation stopped state.

In other words, the rack position at this time is the dotted line in FIG. Since the idle spring 7 has a mounting load, the rack position does not change, i.e., as shown in FIG. Rotate as m-1
obtain the characteristics of 1-k4 characteristics are main spring 9
This occurs due to compression of the data.

Next, the high and low distance type characteristics will be explained.

At this time, the switching lever 38 is rotated counterclockwise and fixed against the adjustment screw 42, and the second
Use the adjusting lever 21. Figure 1 shows
This shows a state in which the rotation is stopped when all members are supplemented, which will be explained next. The position of the control rack 28 at this time is point g in FIG. As the rotation increases, the gap c decreases, but if the stroke b is adjusted using the adjustment screw 42 so that there is some gap c when the set lever 39 and the bottom of the spring capsule 10 come into contact, the stroke b can be reduced. Until it disappears, rack characteristics similar to those of the full-speed type are obtained, and g- in Fig. 4 is obtained.
It is displaced as h−i. Lever 39 is spring capsule 1
When the rotation reaches the bottom of 0, the lower ends of the spring capsule 10 and the floating lever 16 will not be displaced even if the rotation increases further.

That is, the governor sleeper 6 is pulled to the left, but is prevented from moving by the spring capsule 10 set lever 39.
Since the spring 40 has an equivalent load larger than that of the spring 11, the spring 11 is compressed, and only the governor leaf 6 moves leftward by a stroke a, leaving the spring capsule 10 behind. As the governor sleeve 6 moves, the torque control cam 30 is rotated via the lever 36, and as shown in FIG.
As shown by -j, the displacement is similar to that at full speed. Then point i
Double nut 13 so that the stroke a leading to disappears.
Since the thrust force is directly applied to the spring 40 via the lever 39, the spring 40 is expanded by the thrust force and the lever 39 rotates, causing the lower end of the floating lever 16 to move to the left along with the spring capsule 10. , the slight remaining gap c disappears, and pin 2
The floating lever 16 rotates clockwise around 0, and high-speed control starts until point k in FIG. 4 is reached. Now, move the first adjusting lever 17 to the full stop position.
44, since the pin 20 is located above the floating lever long hole 16a, the lever ratio becomes smaller and the so-called speed fluctuation rate becomes larger than during full speed control. Next, the partial load during high/low distance control will be explained.

When the second adjusting lever 21 is moved slightly clockwise, the gap c becomes slightly smaller. 4, the flowing lever 16 moves to the left around its lower end, so that the gap c is, for example, the fourth
It disappears at point i3 in the figure. Therefore, up to i3, the same characteristics as when everyone is loaded are obtained, but even if the rotation increases further, the pawl 29 does not come into contact with the cam surface 30a of the torque control cam 30, so the high speed control starting rotation speed, that is, the stroke The position of the control rack 28 does not change until the stroke a disappears, drawing a trajectory i3-L in FIG. 4, and after the stroke a disappears, high-speed control shown as i3-k in FIG. 4 is performed. When the second adjusting lever 21 is further rotated clockwise, the gap c disappears, for example at point i4 in FIG. 4, before the stroke b disappears.

Therefore, up to i4, the same characteristics as at full load are obtained, and the point i
4, the floating lever 16 rotates clockwise about the pin 20 until the stroke b disappears, and the characteristic i4-1 in FIG. 4 is obtained. Thereafter, even if the rotational speed increases, the control rack position remains unchanged until the stroke a disappears. When the rotational speed reaches the high-speed control start speed, high-speed control starts, and the trajectory of 1,1i2-k2' in Fig. 4 follows. Become. Further, when the second adjusting lever 21 is rotated clockwise, the gap c disappears even when rotation is stopped at a position corresponding to a light load, and the torque control cam 30
The pawl 29 does not come into contact with the cam surface 30a of the control rack 28', and the control rack 28' is in the position shown in FIG. Then, due to the installation load of the idle spring 7, the flat characteristic g
, 1 m, is obtained, and by the time the idle spring is compressed and the stroke b disappears, m, 12 m in Figure 4 is obtained.
The following characteristics are obtained. Then, the control rack position does not shift until the stroke a disappears, and the stroke a
When disappears, high-speed control is started, and [2-Top-] in Fig. 4
The characteristic of k3' is obtained. Furthermore, when the second adjusting lever 21 is set at the no-load equivalent position, the characteristics obtained by moving the characteristics in the light-load equivalent position table in parallel &-m2-3-
k4', and the speed fluctuation rate increases by the difference in lever ratio.

Here, at one angle of the adjusting lever with no load or equivalent to no load, the lever 46 integrated with the second adjusting lever 21 hits the lever 36 and presses it, so the lever 36 presses the pin 37 in the center. This rotates clockwise, and the governor sleeve 6 and torque control cam 30 are no longer interlocked, reducing IJ friction loss at low speeds and improving low speed control performance.

In the above embodiment, the cam surface 30a of the torque control cam 30 is
Although the shape is set, the present invention is not limited to this.

FIG. 6 shows another embodiment, which differs from the previous embodiment only in the first adjusting lever 17;
The first adjusting lever 21 is eliminated, the lever 46 is integrated with the first adjusting lever 17, and an arm 38a is provided integrally with the switching lever 38.
A screw 47 is screwed into "a" to prevent the lever 46 from rotating in the counterclockwise direction.

With the above configuration, when the switching lever 38 is set for high and low distance as shown in the figure, the screw 47
The full load position of the adjusting lever 17 is determined.
Then, when the switching lever 38 is set to full speed, the screw 4 rotates clockwise together with the switching lever 38, and does not come into contact with the lever 46, causing the first adjusting lever 17 to move counterclockwise. Rotation is regulated by a full stopper 44 attached to the outside of the case. As is clear from the above description, the present invention has been developed by adding a slight configuration to the Botsch RQV-K type governor, which has only full-speed type characteristics, so that it can be used as a full-speed type as well as in high and low speeds by switching the switching lever. A speed governor that can also be used as a mold can be obtained.

It has this excellent effect.

[Brief explanation of the drawing]

FIG. 1 is a schematic cross-sectional view showing one embodiment of the speed governor according to the present invention, FIG. 2 is a view of the main parts as seen from direction A in FIG. 1, and FIGS. 3 and 4 are Its characteristic diagram, FIG. 5, is a schematic sectional view showing another embodiment. 3...Fly weight L6...Governor sleep, 7,9
...Idle spring and main spring for regulating speed. 10...Spring capsule forming a sliding member, 11
...Retaining spring, 16...Floating lever, 16a...Elongated hole, 17...Adjustment lever, 20...Pin, 24...Cam plate, 24a...
...Cam groove, 25...Spring, 26...Stopper,
28...Comte. Lurak, 29...color, 30...control cam,
38...Switching lever, 39...Set lever, 40...Set spring. Figure 1 Figure 2 Figure 3 Figure 4 Figure 5

Claims (1)

[Claims] 1 The regulating springs 7 and 9 directly oppose the centrifugal force of the flyweight 3 rotating in synchronization with the engine, and the movement of the governor sleeve 6 interlocked with the flyweight 3 is controlled by a flow control system having a long hole 16a in the middle. is transmitted to the control rack 28 of the fuel injection pump via the control lever 16;
A pin 20 that interlocks with the adjusting lever 17 is fitted into the elongated hole 16a of the floating lever 16, and one end of the pin 20 is rotatably supported, and the other end is biased toward the stopper 26 by a spring 25. cam plate 2
4 is formed with a cam groove 24a into which the pin 20 is fitted, and the floating lever 16 is provided with a pawl 29, and furthermore, the floating lever 16 is provided with a claw 29 in the direction in which the control rack 28 moves toward the fuel increase side. In a centrifugal force governor in which a torque control cam 30 for regulating the rotation of is installed opposite the claw 29, the torque control cam 30 is attached to the governor sleeve 6 and is movable by a predetermined stroke a with respect to the governor sleeve 6. A sliding member 10, a holding spring 11 that normally holds the sliding member 10 in a predetermined position, and a governor sleeve 6 that faces the sliding member 10 and moves as the flyweight 3 expands. a set lever 3 that can prevent the sliding member 10 from moving when
9, a set spring 40 that applies a force to the set lever 39 that exceeds the force of the retaining spring 11, and a switching lever 38 that defines the position of the set lever 39. communication via the sliding member 10, and when the switching lever 38 is placed in the first position, the set lever 39
is set outside the movement range of the sliding member 10, while
A centrifugal speed governor for a diesel engine, characterized in that when the switching lever 38 is set to a second position, the set lever 39 is set to a position where it comes into contact with the sliding member 10 in a predetermined rotation range. .