JPH0511326Y2 - - Google Patents

Description

[Detailed Description of the Invention] <Industrial Field of Application> The present invention relates to a speed governor for a diesel engine, and a desired governor difference can be selected by shifting the speed governor lever fulcrum using a position adjustment means.
To provide a device that can automatically adjust low speed and high speed stoppers in conjunction with adjusting the fulcrum position of a speed control lever.

<Prior art 1> The basic structure of the speed governor of a diesel engine, which is the object of the present invention, is as shown in FIG.
One end of the governor spring 2 is engaged with the driven side engagement point 6 with the governor lever 1, and the other end is engaged with the driving side engagement point 7 with the speed regulating lever 3 to interlock the governor lever 1 with the speed regulating lever 3. It is in a connected format.

As shown in FIG. 9, this type of prior art 1 relates to the upper and lower spaces in which the longitudinal direction of the governor spring separates the fulcrum 4 of the speed regulating lever 3 when the governor lever 1 is located at the no-load position A. The governor lever of the governor spring 2 is located on the same side as the fulcrum 5 of the governor lever 1 and is formed by the included angle between the central axis of the governor spring 2 and an imaginary line connecting the governor lever fulcrum 5 and the driven side engagement point 6. There is one in which the pulling angle θ for pulling 1 is set to approximately 90 degrees from the low-speed operating position B to the high-speed operating position C.

<Problems with Prior Art 1> Generally, the governor force has the rotational speed on the horizontal axis.
In addition, when the force is applied to the vertical axis, as shown in Fig. 10, it changes in a quadratic curve, but one governor spring changes only in a linear manner, so
A spring that matches the rate of change on the high-speed side of the governor force curve is selected to increase the response sensitivity of the governor on the high-speed rotation side.

Therefore, on the low speed side, a deviation occurs between the rate of change of the governor force curve and the slope of the spring straight line,
When the load is reduced from a predetermined operating state, the tension of the governor spring becomes too strong with respect to the governor force, increasing the rate of speed fluctuation.

Conversely, when the load increases, the tension of the governor spring with respect to the governor force becomes too weak, resulting in a large drop in rotation and an inability to produce sufficient output.

<Prior Art 2> FIG. 11 shows a prior art 2 that can suppress an increase in speed fluctuation rate on the low speed side.

That is, when the governor lever 1 is located at the no-load position A, the fulcrum 4 of the governor lever 3 is set to the fulcrum 5 of the governor lever 1 with the governor spring 2 inside.
Position it on the opposite side.

Then, the governor spring 2 is connected to the governor lever 1.
The above-mentioned pull angle θ is set to be an acute angle, and the value of the pull angle θ is set to increase as the regulating lever 3 approaches the high speed operation position C from the low speed operation position B.

The distance l between the fulcrum 4 of the governor lever 3 and the engagement point 6 on the driven side between the governor spring 2 and the governor lever 1 is defined as the distance l from the fulcrum 4 of the governor lever 3 to the engagement point on the driving side between the governor spring 2 and the governor lever 3. The size is set to be considerably smaller than the arm length r up to 7.

The governor lever fulcrum 4 is perpendicular to the imaginary straight line P connecting the governor lever fulcrum 4 and the driven side engagement point 6.
Assuming a virtual reference line S that passes through the imaginary reference line S, the speed control swing region T between the low speed operation position B and the high speed operation position C of the speed control lever is located in an area on the high speed side than the virtual reference line S. be.

According to this structure, the tension of the governor spring 2
Of F ₀ , the component force F ₁ that acts on the rocking motion is expressed using the included angle θ between the governor lever 1 and the governor spring 2 on the side of the governor lever fulcrum 5, as follows: F ₁ =F ₀ sin θ.

Therefore, this oscillating force F ₁ changes in a sinusoidal curve with respect to the set rotational speed of the governor lever 3, and approximates a quadratic curve-like change in the governor force.

Therefore, regardless of whether the speed governor lever 3 is in the high-speed or low-speed operation position, the rate of change of the swinging force _F1 approximates the rate of change of the governor force, so the swinging force _F1 is narrower than the governor force. Balance can be achieved in the rotational range, and it is possible to suppress an increase in speed fluctuation rate during low-speed operation, which was a problem with Prior Art 1.

<Problems with Prior Art 2> On the other hand, of the tension F ₀ of the governor spring 2, the centripetal force F ₂ perpendicular to the swing component F ₁ is F ₀ cosθ
Since the governor lever is pressed against the fulcrum 5 with a value of , a frictional resistance is generated that prevents the governor lever 1 from swinging.

In the above-mentioned prior art 2, since the separation distance l is small and the speed-governing swing region T is biased toward the high-speed side with respect to the virtual reference line S, the governor spring 2 is located between the low-speed operation position B and the high-speed operation position C. Since the width of change in length is small, the change in tension is small.

As a result, during low-speed operation, the tension F ₀ of the governor spring 2 becomes a large value similar to that during high-speed operation.

Accordingly, the centripetal force F ₂ increases accordingly, and the governor lever 1 receives a large frictional resistance at its fulcrum 5, making it difficult to swing.

As a result, variations in the number of rotations become large and hunting becomes more likely to occur.

<Prior Art> Therefore, prior to the invention of the present invention, a technology was developed to reduce variations in the rotational speed and to make hunting less likely to occur.

That is, to explain below using FIGS. 7 and 8, when the governor lever 1 is located at the no-load position A, the above-mentioned driven side engagement point 6 and the governor lever fulcrum 4
The separation distance l from the governor lever fulcrum 4 is set equal to the arm length r from the driving side engagement point 7, and an imaginary straight line P connecting the governor lever fulcrum 4 and the driven side engagement point 6 is set. and perpendicular to the speed control lever fulcrum 4
Assuming an imaginary reference line S that passes through the It was placed in a horizontal position.

In this prior art, the separation distance l is increased to be equal to the arm length r, and the speed control swing region T is located so as to straddle both the low speed side and the high speed side of the virtual reference line S. Therefore, the range of change in length of the governor spring 2 between the low-speed operation position B and the high-speed operation position C becomes large, and the change in tension thereof becomes large.

Furthermore, if the separation distance l is set to be too large compared to the arm length r, there is a disadvantage that the governor device will become larger, and the overall length of the governor spring 2 will become longer, resulting in lower speed operation position B and higher speed operation position C. However, in this prior art, the separation distance l and the arm length r are made equal to each other. As a result, although the governor device is configured compactly, the rate of change in the length of the governor spring 2 becomes large, and the change in tension thereof becomes large.

As a result, during low-speed operation, the tension F ₀ of the governor spring 2 becomes a much weaker and smaller value than during high-speed operation.

Accordingly, since the centripetal force F ₂ becomes smaller, the frictional resistance between the governor lever 1 and the fulcrum 5 is reduced, and the governor lever 1 can be easily swung.

As a result, variations in the number of rotations become smaller, and hunting becomes less likely to occur.

<Problems to be solved by the invention> In general, in actual engines, for example, for a motor generator, it is necessary to reduce the Hertz fluctuation, so it is necessary to use an engine with a small speed fluctuation rate, that is, a small governor difference. On the other hand, with agricultural machinery such as tillers, if the governor's response sensitivity is high, subtle wobbles will occur as the governor attempts to rapidly adjust the rotation speed, so it is better to emphasize stability and use a governor with a somewhat larger difference. preferable.

Therefore, in the above-mentioned prior art, the fulcrum 4 of the speed governor lever 3 is made adjustable by the position adjustment means 8 in the direction in which the pull angle θ changes, thereby changing the speed fluctuation rate in the low speed rotation range, and thereby generating electricity. It is conceivable to increase productivity by using a common speed governor for each engine for aircraft and agricultural machinery.

However, by changing the pulling angle θ, the regulating lever 3
When the fulcrum 4 is adjusted forward or backward, the low-speed stopper 71 and high-speed stopper 72 on the engine body side become misaligned with respect to the speed control lever 3, and the fuel restriction position of the fuel adjustment rack of the fuel injection pump changes.

In order to correct this positional deviation, the positions of the low-speed stopper 71 and the high-speed stopper 72 must be separately adjusted on the engine body side each time the speed governor lever fulcrum 4 is adjusted forward or backward, and this adjustment work is cumbersome. .

The technical objective of the present invention is to solve the above problems.

<Means for Solving the Problems> Means for solving the above problems will be described below using FIGS. 1 to 6, which correspond to embodiments.

That is, the fulcrum support 60 of the speed regulating lever 3 is supported by the fixed wall 70 so as to be adjustable forward and backward in the direction in which the pull angle θ changes by the position adjusting means 8, and the low speed stopper 71 and the high speed stopper 72 of the speed regulating lever 3 are supported as fulcrums. This is provided on the support 60.

<Function> First, when the speed governor lever fulcrum 4 is changed along the forward/backward adjustment direction, the driving side engagement point 7 of the spring can largely shift in direction with respect to the driven side engagement point 6 depending on before and after the change. Therefore, the pulling angle θ at which the governor spring 2 pulls the governor lever 1 can be changed.

For example, as shown in FIG. 6, when the speed governor lever fulcrum 4 is moved forward or backward along the position adjustment means 8, the pull angle θ increases or decreases depending on before or after the change, and the lower position
When the fulcrum 4 is set at H ₁ , the pull angle θ ₁ becomes smaller, the slope of the tension curve of the governor spring becomes smaller at the low speed motion position, the deviation from the governor force curve becomes smaller, and the governor difference becomes smaller.

Furthermore, when the fulcrum 4 is set at the upper position H ₂ , the pull angle θ ₂ increases, and the slope of the tension curve of the governor spring conversely increases, and the difference between the governor force and the tension of the governor spring increases.
The governor difference becomes larger and the stability of operation improves.

On the other hand, since the speed regulating lever 3 and both low-speed and high-speed stoppers 71 and 72 are attached to the fulcrum support 60, the fulcrum support 60 can be pulled forward or backward by the position adjustment means 8 with respect to the fixed wall 70. Since the angle θ can be changed and the positional relationship between the speed regulating lever 3 and the stoppers 71, 72 does not change, there is no need to readjust the stoppers 71, 72.

<Effects of the invention> The present invention solves the problem of prior art 1 by changing the swing component force in a sinusoidal manner as shown in Fig. 1, suppressing the speed fluctuation rate during low-speed operation. can.

Then, the distance between the governor lever fulcrum and the driven side engagement point is set to a dimension equal to the arm length from the governor lever to the driving side engagement point, and the governor swing area of the governor lever is set to the low speed of the virtual reference line. Since the governor spring is located across both the side and the high speed side, the length of the governor spring during low speed operation is considerably smaller than that during high speed operation, and as a result, the governor device does not need to be enlarged. It is possible to reduce the tension of the governor spring at the low speed operating position to suppress rocking resistance and to reduce variations in rotational speed, thereby solving the problems of prior art 2.

Second, by adjusting the speed governor lever fulcrum forward or backward using the position adjustment means, the governor difference can be increased or decreased, so it can be used for generators that require a small governor difference, and power tillers where stability is important. It is possible to use a common speed governor for both engines for agricultural machinery and increase productivity.

Thirdly, when adjusting the governor lever fulcrum forward or backward to increase or decrease the governor difference, the positional relationship between the governor lever and both the low speed and high speed stoppers does not change, so both the low speed and high speed stoppers must be adjusted. There is no need to perform any corrections.

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

FIG. 5 is a schematic perspective view of the diesel engine, and FIG. 8 is a longitudinal sectional front view of the vicinity of the governor of the diesel engine. A fuel injection pump accommodating chamber 10 is provided nearby, and a fuel injection camshaft 11 and a governor shaft 12 are mounted on the pump accommodating chamber 10 in an upper and lower parallel manner, and each is interlocked with the crankshaft via a gear.

A cylinder head 82 and a head cover 83 are sequentially fixed above the cylinder block 80, and a fuel injection nozzle 84 is attached to the cylinder head 82 for each cylinder. Connected to the injection nozzle 84.

A governor sleeve 18 includes a weight base 15 fixed to the governor shaft 12, a fly weight 16 swingably supported on the weight base 15, and an output end 17 of the fly weight slidably inserted into the governor shaft 12. It comes into contact with the left end surface 19.

A governor lever 1 is swingably supported in a fuel injection pump chamber 10 via a fulcrum 5, and is composed of a main lever 1a and a sub-lever 1b. A roller 22 is rotatably supported at the tip of the U-shaped portion 21 so that the roller 22 can come into contact with the right end surface 23 of the governor sleeve 18 .

An engagement groove 24 is cut out in the upper end of the main lever 1a, a rack pin 25 of the fuel injection rack of the fuel injection pump 14 is fitted into the engagement groove 24, and a starting spring 27 is suspended on the right end of the upper end 26. , a contact portion 28 is provided at the left end thereof, and the contact portion 29 of the sub-lever 1b is brought into contact with the contact portion 28.

The sub-lever 1b has its base end 30 pivotally supported on the fulcrum 5, has an engagement hole 32 in its upper end 31, and suspends one end of the governor spring 2 in the engagement hole 32 (this suspension is driven side engagement point 6), and a speed regulating lever 3 whose other end is pivoted to the fuel injection pump chamber 10.
(This suspension part is connected to the driving side engagement point 7.
).

In this case, the fulcrum 4 of the governor lever 3 is located on the opposite side of the governor spring 2 from the fulcrum 5 of the governor lever 1, and the pull angle at which the governor spring 2 pulls the governor lever 1 (i.e., the pull angle at which the governor spring 2 pulls the governor lever 1 (i.e., The included angle (θ) formed by the virtual line segment connecting the above driven side engagement point 6 and the central axis of the governor spring 2 is set to an acute angle, and the speed governor lever 3 is moved from the low speed operation position B to the high speed operation position C. The value of the pulling angle θ is set to increase as the distance approaches.

Also, the fulcrum 4 of the speed regulating lever 3 is at the driven side engagement point 6.
The distance l away from the fulcrum 4 of the regulating lever 3 is
be equal to the arm length r from to the driving side engagement point 7,
The low speed operation position B of the speed governor lever 3 and the high speed operation Controlling swing area T between position C
to straddle.

A cylindrical fulcrum 4 protrudes from one end of the speed regulating lever 3, and is attached to the fixed wall 7 of the fuel injection pump chamber 10.
The adjustment window 50 opened at 0 protrudes outward from the diesel engine.

On the other hand, a longitudinal plate-shaped fulcrum support 60 is fixed on the adjustment base 51, and the adjustment window 50 is covered with the adjustment base 51.

That is, a pin-fitting hole 53 is formed near the center of the right end of the fulcrum support 60, and the pin-fitting hole 53 is formed at each of the four corners of the pin-fitting hole 53.
A short arc-shaped long groove 54 centered at is formed, and a fulcrum insertion hole 52 is formed in the center thereof.

Long holes 55 are formed along the vertical direction in the upper center and lower center of the adjustment base 51, and screw holes 56 are cut at four points corresponding to the long grooves 54 of the fulcrum support 60.

In addition, the reference numeral 58 is a knock pin protruding from the adjustment base 51, and the reference numeral 57 is a tilt fine adjustment screw of the fulcrum support 60.

Then, with the dowel pin 58 inserted into the pin insertion hole 53 of the fulcrum support 60, the long groove 54 and the screw hole 56 are aligned, and the fixing bolt 63 is attached to the fulcrum support 60.
0 is fixed to the adjustment base 51.

Screw holes 64 are carved at the top and bottom of the adjustment window 50,
After aligning the long hole 55 of the adjustment base 51 with this screw hole 64, the adjustment bolt 65 is screwed into the screw hole 64, and the adjustment base 51 is slid up and down on the outer fixed wall 70 of the fuel injection pump chamber 10. Fixed and adjustable.

On the other hand, insert the fulcrum 4 of the regulating lever 3 into the fulcrum insertion hole 52 of the fulcrum support 60, and
A speed limiter 66 is attached to the tip of the fulcrum protruding outward from the
and the external speed regulating lever 67 are installed one after another.

In this case, a high speed limit screw 72 is fixed to the left side of the fulcrum support 60 so that it can move up and down, and a low speed limit screw 71 is fixed to the top side so that it can move left and right. It is limited by high speed limiters 71 and 72.

In the speed governor thus constructed, the adjustment base 5
The combination of the elongated hole 55 and the adjustment bolt 65 of 1 is made by sliding the entire adjustment base 51 downward along the adjustment bolt 65 so that the upper end of the elongated hole 55 comes into contact with the position adjustment means 8 of the speed regulating lever 3. When you move,
The pull angle θ at which the governor spring 2 pulls the governor lever 1 when the fulcrum 4 of the speed governor lever 3 moves downward
can change.

Thereby, the appropriate speed device can be switched to a predetermined governor difference suitable for the motor generator or the agricultural machine.

Further, in this case, the fulcrum support 60 is the adjustment base 5
1, the adjustment base 51 is fixed on the fixed wall 7.
0, the high-speed limiter 72 and low-speed limiter 71 provided on the fulcrum support 60 keep the speed regulating lever 3
The upper and lower limit swing ranges of the speed regulating lever 3 can be automatically set without changing the positional relationship with respect to the speed control lever 3.

Therefore, there is no need to separately adjust the positions of the high speed and low speed limiters 72 and 71 to set the rotation range of the speed governor lever 3 each time the speed governor lever fulcrum 4 is adjusted forward or backward.

[Brief explanation of the drawing]

Figure 1 is a front view of the fulcrum support and adjustment base showing the state in which the speed regulating lever is in contact with the low speed stopper, Figure 2 is a view equivalent to Figure 1 showing the state in which the speed regulating lever is in contact with the high speed stopper; Figure 3 is an exploded perspective view of the fulcrum support and adjustment base, Figure 4 is a vertical left side view of the speed governor, Figure 5 is a schematic perspective view of the diesel engine, and Figure 6 is when adjusting forward and backward movement. 7 is a schematic explanatory diagram of the governor according to the prior art, FIG. 8 is a longitudinal sectional front view of the vicinity of the governor of a diesel engine, and FIG. 9 is a diagram 7 showing the prior art 1. The corresponding diagram, FIG. 10 is a governor force curve diagram, and FIG. 11 is a seventh diagram showing prior art 2.
It is a figure equivalent figure. 1... Governor lever, 2... Governor spring, 3... Speed governor lever, 4... Speed governor lever fulcrum,
5... Governor lever fulcrum, 6... Driven side engagement point of governor spring, 7... Drive side engagement point of governor spring, 8... Position adjustment means, 60... Fulcrum support, 70... Fixed wall, 71... ...Low speed stopper (low speed limiter screw), 72...High speed stopper (high speed limiter screw), A...No-load position of governor lever, B...Low speed operating position of governor lever, C...High speed operating position of governor lever , E... Diesel engine, G... Governor, P... Virtual straight line connecting the governor lever fulcrum and driven side engagement point, S... Virtual reference line,
T...Governing swing area, l...Separation distance between the governor lever fulcrum and driven side engagement point, r...Arm length from the governor lever fulcrum to the driving side engagement point, θ...Governor spring The pull angle to pull the governor lever.

Claims (1)

[Claims for Utility Model Registration] One end of the governor spring 2 of the governor G of the diesel engine E is engaged with the driven side engagement point 6 with the governor lever 1, and the other end is engaged with the driving side engagement point 7 with the speed governor lever 3. In a diesel engine speed governor device in which the governor lever 1 is interlocked and connected to the speed governor lever 3 by engaging with the speed governor lever 3, the fulcrum 4 of the speed governor lever 3 is placed on the opposite side from the fulcrum 5 of the governor lever 1 with the governor spring 2 inside. The governor spring 2 is located at the central axis of the governor spring 2 and is formed by the included angle between the imaginary line segment connecting the governor lever fulcrum 5 and the driven side engagement point 6 and the central axis of the governor spring 2.
The pulling angle θ for pulling the governor lever 1 is set to an acute angle, and the speed governor lever 3 is moved to the low speed operation position B.
The pull angle θ is set to increase as it approaches the high-speed operation position C, and the distance between the driven side engagement point 6 and the governor lever fulcrum 4 when the governor lever 1 is at the no-load position A is set. The distance l is set equal to the arm length r from the governor lever fulcrum 4 to the driving side engagement point 7, and is perpendicular to the imaginary straight line P connecting the governor lever fulcrum 4 and the driven side engagement point 6. In addition, assuming a virtual reference line S passing through the governor lever fulcrum 4, the governor swing region T between the low-speed operation position B and the high-speed operation position C of the governor lever 3 is set to the lower speed side and the higher speed side than the virtual reference line S. The fulcrum support 60 of the speed governor lever 3 is supported by the fixed wall 70 so as to be adjustable forwards and backwards in the direction in which the pull angle θ is changed by the position adjusting means 8. A speed governor for a diesel engine, characterized in that a low speed stopper 71 and a high speed stopper 72 are provided on a fulcrum support 60.