JPH044251Y2 - - Google Patents

Description

[Detailed Description of the Invention] <Industrial Field of Application> The present invention relates to a flyweight device for a centrifugal engine governor, and the present invention relates to a flyweight device for a centrifugal engine governor. To provide a device that can counteract the thrust forces simultaneously acting on the rotary wheel from a governor sleeve to smoothly rotate the rotary wheel, thereby increasing the response sensitivity of the governor.

Further details of the field of application of the technology that is the premise of the present invention include, for example, Figure 1 or 6.
As shown in the figure, the rotation center B of the weight holder 1
A flyweight 2 is swingably supported via a fulcrum shaft 3 at a position deviating from the center, an output arm 6 of the flyweight 2 is extended toward the holder rotation center B, and a pivot pin 18 is attached to the output arm 6. The rotary ring 7 is rotatably supported at a position laterally apart from the holder rotation center B through the holder rotation center B.

<Prior art> In a conventional weight device, as shown in FIG. 6, the arm length K between the fulcrum shaft 3 and the pivot pin 18 is the eccentric distance between the holder rotation center B and the fulcrum shaft 3. It was formed approximately equal to H.

<Problems to be solved by the invention> However, in this conventional device, since the rotating wheel 7 rotates around the rotation center B of the weight holder 1, centrifugal force is applied in the direction away from the rotation center B. It receives R ₀ and is pressed against the inner wall of the output arm 6.

For this reason, the roller 7 is subjected to a sliding resistance force and cannot press the governor sleeve 5 smoothly, resulting in a problem that the response sensitivity of the governor is reduced.

<Means for Solving the Problems> The present invention is intended to solve the above problems, and is capable of smoothly rotating the rotating wheels even when a thrust component is applied to the rotating wheels that are pivotally supported by the output arm. This was proposed for the purpose of increasing the response sensitivity of the governor by maintaining the same level of control, and a configuration for achieving this purpose will be described below with reference to FIGS. 1 to 5, which correspond to embodiments.

That is, the arm length K between the fulcrum shaft 3 and the pivot pin 18 is set longer than the eccentric distance H between the holder rotation center B and the fulcrum shaft 3, and the arm length K between the fulcrum shaft 3 and the pivot pin 18 is set to be longer than the eccentric distance H between the holder rotation center B and the fulcrum shaft 3. The pivot pin 18 is deviated to the upper side in the rotational direction M of the weight holder 1 than the parallel imaginary straight line L, and the displacement dimension N of the pivot pin 18 from the imaginary straight line L is determined by the rotation wheel 7 The rotating wheel 7 is pushed along the pivot pin 18 in the opposite direction to the attraction force F by the centrifugal force _R0 due to the attraction force F that is drawn toward the holder rotation center B along the pivot pin 18 due to friction with the pivot pin 18. The dimensions are set so that the pushing force R can be equally balanced against each other.

<Function> Therefore, to describe the function and effect of the present invention brought about by the above configuration, the arm length K is set longer than the eccentric distance H, and the rotation direction M of the weight holder 1 is set to be longer than the imaginary straight line L. Pivot pin 1 on the upper side
8 is displaced, even if centrifugal force R ₀ acts on the rotating ring 7 away from the center of rotation, the rotating ring 7 is rotating relative to the governor sleeve 5.
The sleeve 5 simultaneously receives an extrusion force F ₀ in a direction tangent to the rotation locus.

Therefore, out of the centrifugal force R ₀ , there is a pushing force R that tries to press the rotating wheel 7 against the inner wall of the output arm 6
is counteracted by the horizontal component of the extrusion force F ₀ that attempts to attract the weight holder, that is, the pulling force F.

At this time, in the present invention, the dimension N by which the pivot pin 18 is displaced from the virtual straight line L is determined by the pushing force R
Since the pulling force F is _set to have the same magnitude as As a result, the rotating wheel 7 is no longer pressed against the inner wall of the output arm 6.

Furthermore, in the present invention, since the arm length K of the output arm 6 is set longer than the eccentric distance H, the swing dimension of the input portion of the governor lever via the governor sleeve 5 can be increased.

<Effects of the invention> Therefore, according to the invention, the rotating wheel can rotate smoothly while ensuring a long swinging dimension of the input part of the governor lever, thereby greatly improving the response sensitivity of the governor. be able to.

<Example> Hereinafter, an example of the present invention will be described based on the drawings.

Fig. 1 is a longitudinal sectional front view of the main parts around the output arm of the weight device, Fig. 2 is an exploded perspective view of the oscillating weight device of the mechanical governor, and Fig. 3 is a longitudinal sectional side view of the vicinity of the same weight device in a diesel engine. , 4th
The figure is a longitudinal front view of the same engine, and FIG. , an injection cam shaft 22 extending from the front and back of the pump chamber 20;
The injection pump chamber 21 is interlocked with the injection pump chamber 21.

Further, a governor shaft 8 is disposed below the pump chamber 20, and the weight device 10 is mounted after the governor shaft 8 is mounted parallel to the injection cam shaft 22.
0, the fuel adjustment rack 23 of the fuel injection pump 21 is interlocked via the governor lever 24.

That is, as shown in FIG.
A substantially rectangular parallelepiped weight holder 1 and a governor sleeve 5 are fitted in sequence, and two fly weights 2 are pivoted to the weight holder 1 via a fulcrum shaft 3 so as to be swingable in the centrifugal direction.

The weight holder 1 has a shape in which left and right side walls 13 and 12 of a disc-shaped body are smoothly cut out, and a governor shaft insertion hole 14 is provided in the center thereof in the front and back direction, and a governor shaft insertion hole 14 is formed in the center part of the left and right side walls 13 and 12. , 12 (that is, the support shaft insertion hole 15 is located perpendicularly apart from the governor shaft insertion hole 14 in the vertical direction), and in this state. It is fixed to the holder base 11 and fitted onto the governor shaft 8, and a governor sleeve 5 is slidably disposed in front of the governor shaft 8.

Each of the flyweights 2 has an output arm 6 extending vertically behind both ends of a semi-cylindrical body 16, a pivot hole 17 is formed above both output arms 6, and a pivot hole 17 is formed below one of the output arms 6. supports the pivot pin 18;
A radial bearing, more specifically a radial ball bearing 7, is rotatably supported at the inner end of the radial bearing.

Then, by aligning the pivot hole 17 of the power and power arm 6 with the support shaft insertion hole 15 of the weight holder 1, and inserting the support shaft 3 into both holes 15 and 17, the two fly weights 2 can be used as weights. They are pivotably supported above and below the holder 1, respectively.

The output arm 6 passes through the holder rotation center B by setting the arm length K between the fulcrum shaft 3 and the pivot pin 18 to be longer than the eccentric distance H between the holder rotation center B and the fulcrum shaft 3. The pivot pin 18 is configured to be deviated to the upper side in the rotational direction M of the weight holder 1 than the imaginary straight line L parallel to the fulcrum shaft 3. The extrusion displacement is large, and the sliding displacement of the governor sleeve 5 is ensured to be large, and the swing dimension of the input portion of the governor lever 24 is set large.

The displacement dimension N of the pivot pin 18 from the virtual straight line L is determined by the thrust component F of the extrusion force F0 that the radial bearing ₇ receives from the governor sleeve and the centrifugal force that the radial bearing 7 receives due to its own rotational movement. By setting the distance so that the horizontal component R of R ₀ is equal, the radial bearing 7 is prevented from being pushed in the direction of the output arm 6 by the centrifugal force R ₀ .

On the other hand, a bifurcated governor lever 24 is disposed in front of the governor sleeve 5 fitted into the governor shaft 8, and the bifurcated base 25 is pivotably pivoted on a support shaft 26 which is horizontally supported in the pump chamber 20. A roller 28 supported by a bifurcated tip 27 is configured to be able to come into contact with a front flange 29 of the governor sleeve 5.

In the governor device constructed in this way, when the engine speed increases, the rotation speed of the governor shaft 8 also increases, and the weight 2 receives centrifugal thrust and rotates the upper and lower ends of the weight holder 1 about the fulcrum shaft 3. It opens in the direction.

Then, the weight 2 swings its output arm 6 toward the front of the governor shaft 8, and the radial bearing 5
0 presses and slides the rear flange portion 30 of the governor sleeve 5 in the forward direction.

The governor sleeve 5 that has slid forward pushes the bifurcated tip 27 of the governor lever 24 forward with its front flange 29, and the governor lever 24 that has swung around the support shaft 26 injects fuel against the tension of the governor spring. The fuel adjustment rack 23 of the pump 21 is moved to the fuel reduction side to reduce the engine speed to a predetermined speed.

Furthermore, when the engine speed decreases, the tension of the governor spring causes the governor lever 24 to move the fuel adjustment rack 23 toward the fuel reduction side, thereby increasing the engine speed to a predetermined speed.

As described above, in a governor device that adjusts the engine speed to a constant range, the present invention is designed to rotate the rotating ring of the weight part, which is one of the elements constituting the governor device, in response to the rotation of the weight holder in a specific direction. Since it is pivoted while maintaining a predetermined arm length, the rotating ring is not limited to the radial ball bearing as described above, but may also be other bearings such as double row spherical roller bearings, or rollers.

[Brief explanation of the drawing]

Figures 1 to 5 show an embodiment of the present invention. Figure 1 is a longitudinal sectional front view of the main parts around the output arm of the weight device, and Figure 2 is an exploded view of the swinging weight device of the mechanical governor. FIG. 3 is a longitudinal sectional side view of the weight device in the diesel engine, FIG. 4 is a longitudinal sectional front view of the engine, FIG. 5 is a front view of the weight device, and FIG. 6 is a conventional weight device. It is a schematic front view shown. 1... Weight holder, 2... Fly weight, 3... Fulcrum shaft, 5... Governor sleeve, 6...
...Output arm, 7...Rotating wheel, 18...Pivot pin, B
...center of rotation of 1, F...attraction force, H...eccentric distance between B and 3, K...arm length between 3 and 18, L...passing through B and parallel to 3 A virtual straight line, M...
...rotation direction of 1, N...deviation dimension of 18 from L, R ₀ ... centrifugal force, R ... pushing force.

Claims (1)

[Scope of utility model registration request] A flyweight 2 is swingably supported via a fulcrum shaft 3 at a position offset from the rotation center B of the weight holder 1, and the output arm 6 of the flyweight 2 is extended toward the holder rotation center B, and the output arm 6 to pivot pin 1
In a flyweight device for a centrifugal engine governor, which is constructed by rotatably supporting a rotary wheel 7 at a position laterally away from the holder rotation center B via a holder shaft 8, between the fulcrum shaft 3 and the pivot pin 18. The arm length K is the eccentric distance H between the holder rotation center B and the fulcrum shaft 3.
The weight holder 1 is set longer than the imaginary straight line L passing through the holder rotation center B and parallel to the fulcrum shaft 3.
The pivot pin 18 is deviated upward in the rotational direction M, and the displacement dimension N in which the pivot pin 18 is displaced from the virtual straight line L is caused by the friction between the rotating wheel 7 and the governor sleeve 5, The rotating wheel 7 can equally counteract the pulling force F along the pivot pin 18 with the centrifugal force _R0 against the pulling force F that pulls the holder toward the center of rotation B along the pivot pin 18. A flyweight device for a centrifugal engine governor, which is characterized by having dimensions set to a certain value.