JPH044252Y2 - - Google Patents

Description

[Detailed explanation of the idea]

<Industrial Application Field> The present invention relates to a flyweight device for a centrifugal engine governor, and the output arm is lengthened.
To provide a governor capable of increasing response sensitivity by preventing sliding resistance from being applied to a roller pivotally supported on an output arm. Further details of the field of application of the technology on which the present invention is based include, for example, Figure 1 or Figure 7.
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 the conventional weight device, as shown in FIG. 7, a roller is used as the rotating wheel 7, and the arm length K between the fulcrum shaft 3 and the pivot pin 18 is set to the holder rotation center B. It was formed to be approximately equal to the eccentric distance H between it and the fulcrum shaft 3.

[Problems with conventional technology]

However, in this conventional device, since the roller 7 performs rotational movement around the rotation center B of the weight holder 1, it receives centrifugal force R ₀ in a direction away from the rotation center B and is applied to the inner wall of the output arm 6. Being pushed. For this reason, the roller 7 is subjected to a sliding resistance force and cannot press the governor sleeve 5 smoothly, resulting in a disadvantage that the response sensitivity of the governor is reduced.

[Prior art]

On the other hand, prior to the present invention, the applicant had developed a system for increasing the precision of the governor by increasing the swinging dimension of the input portion of the governor lever 24 via the governor sleeve 5, as shown in FIGS. 6 and 4. We considered setting the length K to be longer than the eccentric distance H. <Problem to be solved by the invention> However, in this prior invention, the roller rotating around the governor shaft is subjected to an extrusion force in a direction tangent to its rotational trajectory by the governor sleeve 5.
Since F ₀ is received, out of this extrusion force F ₀ , the component force in the direction of the pivot pin 18, that is, the thrust component force E
This manifests itself as a sliding resistance force that tries to press the roller 7 against the inner wall of the output arm 6. For this reason, the roller 7 cannot press the governor sleeve 5 smoothly, resulting in the problem that the accuracy of the governor cannot be substantially increased. <Means for solving the problems> The present invention solves the above problems by increasing the length of the output arm, and even when centrifugal force or thrust force from the governor sleeve is applied to the rotating wheels, the rotating wheels are not affected. This was proposed for the purpose of maintaining smooth rotation and increasing the response sensitivity of the governor.The configuration for achieving this purpose is described below using FIGS. 1 to 5 corresponding to the embodiment. explain. 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 lower side in the rotation direction M of the weight holder 1 than the parallel imaginary straight line L, and the inner race 51 is externally fitted onto the pivot pin 18 using a radial bearing 50 as the rotating ring 7. ,
The outer end surface 53 of the inner race 51 on the side far from the holder rotation center B is received by the output arm 6, and the outer end surface 54 of the outer race 52 is spaced apart from the output arm 6 with a gap 55. It is. <Function> Therefore, to describe the function of the present invention brought about by the above configuration, the radial bearing 5 is used as a rotating ring.
0, the outer end surface 54 of the outer race 52
is separated from the output arm 6, so that the thrust component _F1 of the pushing force _F0 from the governor sleeve 5 is applied to the outer race 52 of the radial bearing 50.
Alternatively, when centrifugal force is applied (that is, since the substantial portion of the radial bearing that contacts the governor sleeve 5 is the outer race 52, this outer race 52 receives external force), the governor sleeve 5
Even if the weight holder 1 is pressed in the direction of the rotation center B, the gap 55 between the weight holder 1 and the output arm 6
Thrust movement takes place inside. Therefore, the outer end surface 54 of the outer race 52 is no longer pressed against the inner wall 56 of the output arm 6. Moreover, since the inner race 51 rotates through the rolling motion of the balls 60 with respect to the outer race 52 which is pressed in the direction of the rotation center B by the sliding component F, the rotation of the outer race 52 is not hindered, and the radial bearing 50 connects the governor sleeve 5 to the governor shaft 8
It is possible to move horizontally smoothly along the <Effect of the invention> Therefore, according to the invention, the output arm can be lengthened to lengthen the swinging dimension of the input part of the governor lever, and the governor force can be accurately and smoothly transferred to the governor sleeve via the radial bearing. Therefore, the response sensitivity of the governor can be greatly improved. <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 21 is interlocked. 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 formed above both output arms 6, and a pivot hole 17 formed below one output arm 6. supports the pivot pin 18;
A rotary ring 7 is rotatably supported at the inner end of the rotary ring 7. 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 lower side in the rotational direction M of the weight holder 1 than the imaginary straight line L parallel to the fulcrum shaft 3, so that the output arm 6 is The pushing displacement is large, the sliding displacement of the governor sleeve 5 is large, and the swinging dimension of the input part of the governor lever 24 is set large. Further, the rotating ring 7 uses a radial bearing, more specifically a radial ball bearing 50, and an inner race 51 thereof is fitted onto the pivot pin 18, and the inner race 51 is fitted onto the pivot pin 18. Then, the outer end surface 53 of the inner race 51 on the side far from the holder rotation center B is connected to the inner wall 5 of the output arm 6 via the collar 57.
Let 6 accept it. By interposing the collar 57, the bearing 5
The outer end surface 54 of the outer race 52 of No. 0 is separated from the inner wall 56 of the output arm 6 with a gap 55,
Even if the outer race 52 receives an extrusion force from the governor sleeve 50, the thrust movement is limited to this gap 55.
Set it so that it is done inside. 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 support 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 increase side, thereby increasing the engine speed to a predetermined speed. As described above, the present invention is a governor device that adjusts the engine speed within a certain range, in which the rotating ring of the weight part, which is one of the elements that make up the governor device, is made into a radial bearing and is mounted at a predetermined position. Therefore, the radial receiver is not limited to the radial ball bearing as described above, but may also be, for example, a double row spherical roller bearing. Furthermore, since the rotary wheel is unique, it goes without saying that the shape of the weight and the manner in which the weight is pivoted to the support shaft do not matter.

[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. 3 is a vertical sectional side view of the vicinity of the weight device in a diesel engine, FIG. 4 is a vertical sectional front view of the same engine, FIG. 5 is a front view of the weight device, and FIG. 6 is a front view of the weight device of the prior art. FIG. 7 is a schematic front view showing a conventional example.
It is a figure equivalent figure. 1... Weight holder, 2... Fly weight, 3... Fulcrum shaft, 6... Output arm, 7... Rotating ring, 18... Pivot pin, 50... Radial bearing,
51... Inner lace, 52... Outer lace,
53... Outer end surface of 51, 54... Outer end surface of 52,
55... Gap between 54 and 6, B... Center of holder rotation, H... Distance between B and 3, K... Arm length between 3 and 18, L... Passing through B and parallel to 3 The rotation direction of the virtual straight line, M...1.

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 to the downstream side in the rotation direction M, and the inner race 51 is fitted onto the pivot pin 18 using a radial bearing 50 as the rotating ring 7, and the inner race 51 is moved from the holder rotation center B. The outer end surface 53 on the far side is received by the output arm 6, and
This flyweight device for a centrifugal governor for an engine is characterized in that the outer end surface 54 of the outer race 52 is separated from the output arm 6 with a gap 55.