JPH0234441Y2 - - Google Patents

Description

[Detailed description of the invention] <Industrial application field> The present invention relates to a speed governor for a diesel engine, and provides a device that reduces speed fluctuation rate during low-speed operation and also reduces variation in rotation. .

<Prior art 1> The basic structure of the speed governor of a diesel engine, which is a feature of the present invention, is as shown in FIGS. 1, 3, or 5, for example, as shown in FIG. It is of a type in which it is interlocked and connected to the speed regulating lever 3 via the speed regulating lever 3.

As shown in FIG. 3, in this type of prior art 1, when the governor lever 1 is located at the no-load position A, the upper and lower spaces are separated by the longitudinal direction of the governor spring 2 and the fulcrum 4 of the speed regulating lever 3. with respect to the fulcrum 5 of the governor lever 1,
There is one in which the pull angle θ at which the governor spring 2 pulls the governor lever 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> In general, 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 Figure 4, it changes in a quadratic curve, but one governor spring changes only linearly, so the rate of change on the high-speed side of the governor force curve Matching springs are 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. 5 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.
While setting the pulling angle θ to be acute,
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 of the governor lever 3 and the driven side engagement point 6 between the governor spring 2 and the governor lever 1 is calculated from the fulcrum 4 of the governor lever 3 to the main drive side engagement point 7 between the governor spring 2 and the governor lever 3. Set the dimension to be considerably smaller than the arm length r up to.

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

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 3, 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 of the governor spring 2,
Since the centripetal force F ₂ orthogonal to the swinging force F ₁ presses the governor lever against the fulcrum 5 with a value of F ₀ cosθ, it becomes a frictional resistance 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 control 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.

The technical objective of the present invention is to reduce this variation in rotational speed and to make hunting less likely to occur.

<Means for solving the problems> Means for solving the above problems will be explained below using FIG. 1 and FIG. 2 corresponding to the embodiment.

That is, in addition to the basic structure of the prior art 2, the separation distance l between the fulcrum 4 of the governor lever 3 and the driven side engagement point 6 between the governor spring 2 and the governor lever 1 is changed from the fulcrum 4 of the governor lever 3 to the governor. The length is set to be approximately equal to the arm length r between the spring 2 and the regulating lever 3 up to the engagement point 7 on the driving side, and perpendicular to the imaginary straight line P connecting the regulating lever fulcrum 4 and the engagement point 6 on the driven side. , virtual reference line S passing through the regulating lever fulcrum 4
Assuming that, 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 3 is positioned so as to straddle both the low speed side and the high speed side with respect to the virtual reference line S. It is something.

<Function> In the present invention, in addition to increasing the separation distance l, the governor spring 2 is positioned so as to straddle both the low speed side and the high speed side of the virtual reference line S. The range of change in length between the low-speed operation position B and the high-speed operation position C becomes large, and the change in tension 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.

Therefore, the centripetal force F ₂ decreases accordingly,
By reducing the frictional resistance between the governor lever 1 and the fulcrum 5, the governor lever 1 can be lightly swung.

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

<Effect of the invention> The invention changes the swing component force in a sinusoidal manner,
By suppressing the speed fluctuation rate during low-speed operation, and reducing the tension of the governor spring at the low-speed operation position to reduce rocking resistance and the variation in rotation speed, all of the problems of the conventional technology have been solved. It is possible to eliminate all points at once and obtain a highly accurate governor.

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

FIG. 1 is a schematic explanatory diagram of the governor, and FIG. 2 is a longitudinal sectional front view of the vicinity of the governor of the diesel engine, in which the fuel injection camshaft 11 and the governor shaft 12 are placed in the fuel injection pump housing chamber 10 of the diesel engine E. The shafts are mounted in parallel at the bottom, and each is linked to the crankshaft via a gear.

A fuel injection pump 14 is linked to the fuel injection camshaft 11, and the pump 14 is connected to a fuel injection nozzle facing the combustion chamber.

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 speed regulating lever 3 is located on the opposite side from the fulcrum 5 of the governor lever 1 with the governor spring 2 inside, and the pull angle θ at which the governor spring 2 pulls the governor lever 1 is set to an acute angle. ,
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.

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 adjustment lever 3
A virtual reference line that is approximately equal to the arm length r from to the driving side engagement point 7, is perpendicular to the imaginary straight line P connecting the speed governor lever fulcrum 4 and the driven side engagement point 6, and passes through the speed governor lever fulcrum 4. S is made to straddle 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 3.

In the governor configured in this way, when the engine speed increases, the flyweight 16 swings outward under centrifugal force, slides the governor sleeve 18 to the right, and causes the governor lever 1 to engage the governor force.
Grant GF.

The governor lever 1, which receives the governor force GF, swings counterclockwise about the fulcrum 5, and slides the rack pin 25 of the fuel injection pump 14 toward the fuel reduction side.

Conversely, when the rotation speed decreases, the fly weight decreases to 16
The governor force GF decreases, the tension of the governor spring 2 overcomes, and the governor lever 1 is swung clockwise, causing the rack pin 25 to slide toward the fuel increase side.

When the governor lever 3 is moved from the low-speed operation position B to the high-speed operation position C, the governor force changes quadratically with respect to the engine speed.
In line with GF, the tension of governor spring 2 is also sin
The governor spring 2 changes in a curve to keep the governor difference small, and the governor spring 2 at the low speed operating position.
By suppressing the tension, variations in rotation can be suppressed.

[Brief explanation of drawings]

1 and 2 show an embodiment of the present invention, FIG. 1 is a schematic explanatory diagram of the governor, FIG. 2 is a longitudinal sectional front view of the vicinity of the governor of a diesel engine, and FIG. 3 is a diagram showing the prior art 1. 1 is a diagram corresponding to FIG. 1, FIG. 4 is a governor force curve diagram, and FIG. 5 is a diagram corresponding to FIG. 1 showing Prior Art 2. 1...Governor lever, 2...Governor spring, 3...Governing lever, 4...3's fulcrum, 5...
1 fulcrum, 6... Driven side engagement point between 2 and 1, 7...
...Movement side engagement point between 2 and 3, A...1 no-load position, B...1 low speed operating position, C...1 high speed operating position, E...diesel engine, G...governor, P ...Virtual straight line connecting 4 and 6, S...Virtual reference line, T...Speed control swing area, l...Separation distance between 4 and 6, r...Arm length from 4 to 7, θ ...2
is the pulling angle that pulls 1.

Claims (1)

[Scope of utility model registration request] The governor lever 1 of the governor G of the diesel engine E is connected to the speed regulating lever 3 via the governor spring 2.
In the speed governor of a diesel engine, the fulcrum 4 of the speed governor lever 3 is located on the opposite side of the fulcrum 5 of the governor lever 1 with the governor spring 2 inside, and the governor spring 2 pulls the governor lever 1. The tightening pull angle θ is set to an acute angle, and the value of the pull angle θ is set to increase as the governor lever 3 approaches the high speed operation position C from the low speed operation position B, and the governor lever 1 is set to the no-load position A. In the state where the regulating lever 3
The fulcrum 4 is the governor spring 2 and the governor lever 1.
The separation distance l from the driven side engagement point 6 with the governor spring 2 and the speed regulating lever 3 is set to be approximately equal to the arm length r from the fulcrum 4 of the governor spring 2 to the driving side engagement point 7 of the governor spring 2 and the speed regulating lever 3. , is orthogonal to the virtual straight line P connecting the regulating lever fulcrum 4 and the driven side engagement point 6, and
Assuming a virtual reference line S passing through the regulating lever fulcrum 4,
Low speed operation position B and high speed operation position C of speed regulating lever 3
A speed governor for a diesel engine, characterized in that a speed governing swing region T between the two is located across both a low speed side and a high speed side from a virtual reference line S.