JPH08246904A - Torque up device of centrifugal governor of diesel engine - Google Patents

Abstract

PURPOSE: To restrain rotating speed of an engine from shifting to the high speed side since a torque up case is dislocated to the fuel quantity increasing side when a spring side lever inclines by a sudden change in an engine load. CONSTITUTION: A case tip surface 13a of a torque up case 10 of a torque up device 7 is formed into a concentric shape and a small circular shape with the torque up case 10, and this diameter d1 is set in a diameter remarkably smaller than a diameter D of the torque up case 10. Therefore, when a spring side lever 4 inclines, a dimension in which the torque up case 10 is dislocated and moved to the fuel quantity increasing side R is shortened to C2 from a conventional technology C1. Therefore, an excessive quantity of a fuel injection quantity is reduced, and rotating speed of an engine is restrained from shifting to the high speed side.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a centrifugal governor for a diesel engine, and a torque for increasing a fuel injection amount of a fuel injection pump to a torque-up amount exceeding a full load amount when the engine is overloaded. Up device.

[0002]

Prerequisite Structure The torque increasing device for a centrifugal governor of a diesel engine according to the present invention is intended for those having the following prerequisite structure as shown in FIGS. 1 to 6, for example. ○ Prerequisite structure That is, the fuel metering device (2) for adjusting the fuel discharge amount of the fuel injection pump (1) of the diesel engine has a weight side lever (3), a torque increasing device (7) and a spring side lever (4). Through the order, the spring tension (GS) of the governor spring (5) is used to elastically press the fuel increase side (R).
The governor force (GF) by the centrifugal force of the governor weight (6) is pressed to the fuel reduction side (L) via the weight side lever (3), and the governor force (GF) and the spring tension (GS) It is configured so that it can be adjusted and moved in the fuel increasing / decreasing direction by the differential force.

The spring side lever (4) is used as a fuel metering tool.
The fuel limiter (8) is received at the full load position (F) in (2) to limit the further movement toward the fuel increase side (R). The weight side lever (3) is configured so as to elastically press the fuel increasing side (R) by the spring tension (SS) of the starting spring (9).

In the torque increasing device (7), the torque pin (11) is connected to the torque spring (1) in the torque increasing case (10).
By pinching with 2), the tip of the pin of the torque pin (11)
(11a) is made to project from the pin insertion hole (14) of the opening to the case front end wall (13) of the torque-up case (10), and the weight side lever (3) is moved to the fuel increase side with respect to the spring side lever (4).
It is configured to suppress the pressure on (R).

The torque-increasing case (10) is fixedly mounted on one of the weight-side lever (3) and the spring-side lever (4), and the case contact transmission surface ( 15) is fixed, and the case tip end face (13a) of the case tip end wall (13) of the torque up case (10) and the pin tip end (11a) of the torque pin (11) are attached to the case contact transmission surface (15). Get in touch with. The case tip end surface (13a) and the case contact transmission surface are located outside the axial center of the swing pivotally supporting portion (16) of the weight side lever (3) in the axial direction (16a). It is constructed by displacing the center point (17a) of the contact transmission portion (17) with (15).

The fuel metering device (2) is for adjusting the fuel discharge amount of the fuel injection pump (1). For example, in the Bosch fuel injection pump, it means a control rack, and the deckle fuel injection device. The pump means a regulator needle valve, the distribution type Bosch VE type fuel injection pump means a spill ring, the distribution type CAV type fuel injection pump means a metering valve, and the distribution type silt type fuel injection pump means a throttle valve.

Operation of premise structure (A) At engine start-up. See FIG. 5 (A). Before the engine is started, the governor force (GF) of the governor weight (6) is not generated, so the spring side lever (4) is the governor spring (5) and the fuel increase side
It is pulled to (R) and received at the full load position (F) by the fuel limiter (8), and the fuel metering device (2) is increased by the starting spring (9) via the weight side lever (3). (ST). In this state, move the speed control lever (21) to the high-speed rotation position.
When set to (Hi) to increase the spring tension (GS) of the governor spring (5) and start the engine to rotate,
The fuel discharged from the fuel injection pump (1) becomes an increased amount for starting, and the engine is started strongly with a particularly large torque.

As the engine speed increases, the governor force (GF) increases and the fuel metering device (2) is moved to the fuel reducing side via the weight side lever (3).
Push it to (R) and push it to the torque up position (TU) against the starting spring (9).
Against 2), push to full load position (F), and further against governor spring (5) to fuel reducing side (L), and when rotation has risen sufficiently, move to no load position (N). Push it up.

(B) During no load or full load operation. See Fig. 5 (B). The fuel metering device (2) is adjusted to the no-load position (N) during engine no-load operation, the full-load operation position (F) during full-load operation, and the no-load position during partial-load operation. Adjusted between (N) and full load position (F). Between the no-load position (N) and the full-load position (F), the torque lever (7) and the lever (4) on the spring side are in contact with each other, and the lever on the weight side is in contact.
(3) and the lever (4) on the spring side move as a unit.

(C) During overload operation. Refer to FIG. 5 (C) When the engine is overloaded, the speed of the engine decreases and the governor force (GF) becomes weaker, so the spring side lever (4) is at the full load position (F) and the fuel limiter (8). Then, the fuel metering device (2) is adjusted and moved to the torque-up position (TU) at maximum through the weight-side lever (3) by the tension of the torque spring (12).

[0011]

2. Description of the Related Art In the above-described prerequisite structure, the contact transmission portion (17) between the case tip surface (13a) of the torque-up case (10) and the case contact transmission surface (15) has a conventional structure. Then, there are those shown in FIGS. 10 (A) and 10 (B). That is, the case tip surface (1
The shape of 3a) is formed in a circular shape having the same diameter (D ₁ ) as the diameter (D) of the torque-up case (10). Then, the width (15b) of the case contact transmission surface (15) is the torque increase case.
It is formed in a size larger than the diameter (D) of (10).

[0012]

[Problems to be Solved by the Invention]

○ Inclination of the spring-side lever (4) in the premise structure In the above-mentioned premise structure, the spring-side lever (4) is normally kept in the correct posture shown in Fig. 4 in plan view, but when the load suddenly changes. May tilt forward or backward as shown in FIGS. 6 (B) and 6 (D).

That is, when the load on the engine suddenly increases, the rotational speed sharply decreases and the governor force (GF) suddenly weakens. Therefore, as shown in FIG. 6 (A), the spring side lever (4) is suddenly pulled by the spring tension (GS) of the governor spring (5), and the center point (16a) of the swinging pivotal support (16) is pulled. ) As the center of rotation (M ₁ ) causes it to be tilted toward the front side (lower side in the figure) as shown in FIG. 6 (B). And after this, the spring side lever (4)
However, the control operation may continue in this tilted posture.

Similarly, the spring tension (GS) of the governor spring (5) suddenly increases even when the speed governor lever (21) is rapidly accelerated toward the high speed side, and the spring side lever (5) becomes stronger.
(4) may be tilted forward as shown in FIG. 6 (B).

When the load on the engine suddenly decreases,
The rotation speed of the engine suddenly increased, and the governor force (G
F) suddenly becomes stronger. Therefore, as shown in FIG. 6 (C), the spring side lever (4) is suddenly pushed by the governor force (GF), and the center point (16a) of the swinging pivotally supporting portion (16) is set as the center of rotation. Due to the moment (M ₂ ), it is tilted backward (upper side in the figure) as shown in FIG. 6 (D). Even after this, the spring side lever (4) may continue to controlly operate in this tilted posture. Similarly, when the speed control lever (21) is rapidly decelerated to the low speed side,
The spring tension (GS) of the governor spring (5) suddenly weakens, and the governor force (GF) relatively suddenly becomes stronger as shown in FIG. 6 (D). It may be tilted.

Problems of Prior Art In the above prior art, as shown in FIGS. 6 (B) and 6 (D), when the spring-side lever (4) continues to perform control operation while being tilted, The rotation speed of the engine shifts to a considerably high side. The reason is that, as shown in FIG. 10 (B), the spring side lever (4) is tilted, and the torque increase case (10) is excessively biased toward the fuel increase side (R) by the clearance dimension (C ₁ ). However, the fuel injection amount becomes excessive.

This clearance dimension (C ₁ ) is measured from the center point (17a) of the contact transmission section (17) to the case contact transmission surface (15) and the case tip surface.
It is determined by the distance (L ₁ ) to the contact point with (13a), and since this distance (L ₁ ) is long, the above-mentioned clearance dimension (C ₁ ) becomes large and the above-mentioned amount of fuel injection becomes excessive. Therefore, the rotation speed of the engine deviates to a side considerably higher than the set rotation speed.

OBJECT OF THE INVENTION The object of the present invention is to provide the above-mentioned clearance dimension (C ₁ ) in FIG. 10 (B).
Is to reduce the amount by which the fuel injection amount becomes excessive, and to suppress a large shift to the higher engine speed side.

[0019]

In the torque increasing device for a centrifugal governor of a diesel engine of the present invention, in order to solve the above-mentioned problems in the above-mentioned precondition, the case front end surface of the torque increasing case (10) ( It is characterized in that the following characteristic configuration is added as a configuration of the contact transmission section (17) between the case 13a) and the case contact transmission surface (15).

Invention 1 (See FIG. 1 or FIG. 7) The width (13b) of the case tip surface (13a) of the torque-up case (10) is formed to be smaller than the diameter (D) of the torque-up case (10). Width of tip surface (13a) (1
It is characterized in that the center of 3b) substantially coincides with the center of the pin tip portion 11a of the torque pin 11.

○ Invention 2. (See FIG. 8 or FIG. 9) The width (15b) of the case contact transmission surface (15) is formed to be smaller than the diameter (D) of the torque-up case (10), and the case contact transmission surface (15) is formed. ) Width (15b) at the center of the torque pin
It is characterized in that it is configured so as to substantially coincide with the center of the pin tip portion (11a) of (11).

[0022]

The present invention operates as follows. ○ Invention 1. (See FIG. 1 (B)) As described above, as shown in FIGS. 6 (B) and 6 (D),
When the spring side lever (4) continues to perform control operation while being tilted, as shown in FIG. 1 (B), the spring side lever (4) is tilted so that the torque increase case (10) increases the fuel quantity. The dimension that is excessively biased to the side (R) is the clearance dimension (C ₂ ). This clearance dimension (C ₂ ) is measured from the center point (17a) of the contact transmission section (17) to the case contact transmission surface (15).
Is determined by the distance (L ₂ ) to the contact point between the front end surface (13a) of the case and the case.

Case end surface (1) of the torque-up case (10)
3a) width (13b), torque up case (10) diameter
From the characteristic structure formed to have a size smaller than (D), the distance (L ₂ ) is the distance (L) in the case of the conventional technique shown in FIG. 10B.
_Since it is shorter than ₁ ), the gap size (C ₂ ) is smaller than the gap size (C ₁ ) in the case of the prior art. As a result, the fuel metering device (2) is biased to the fuel increase side (R) via the weight side lever (3) and the amount of excess fuel injection amount is reduced, and the engine speed is set to the set speed. It is possible to suppress a large shift to a higher side.

Invention 2. In the second aspect of the present invention, the gap dimension (C ₂ ) becomes smaller than the gap dimension (C ₁ ) of the prior art due to the same reason as in the first aspect of the invention, and the fuel meter (2)
Is deviated to the fuel increase side (R) and the amount of excess fuel injection amount is reduced, and it is possible to prevent the engine speed from largely deviating to a side higher than the set engine speed.

[0025]

EFFECTS OF THE INVENTION Since the invention 1 and the invention 2 are constructed and operate as described above, they have the following effects. (A) Suppressing a large shift of the engine rotation speed to the high side As shown in FIGS. 6B and 6D, the spring side lever (4) continues to controlly operate in a tilted posture. In this case, if the spring side lever (4) tilts,
The dimension by which the torque-up case (10) is excessively biased toward the fuel increase side (R) is a small clearance dimension (C ₂ ) as shown in FIG. 1 (B), which is shown in FIG. 10 (B). It is smaller than the gap size (C ₁ ) in the case of the conventional technique. This allows
The amount by which the fuel metering device (2) is biased to the fuel increase side (R) via the weight side lever (3) and the fuel injection amount becomes excessive decreases, and the engine rotation speed becomes higher than the set rotation speed. It is possible to suppress the collapse.

[0026]

Embodiments of the present invention will be described below with reference to the drawings. ○ Example 1. (See FIGS. 1 to 6) FIGS. 2 to 4 show the entire centrifugal governor of a vertical multi-cylinder diesel engine, FIG. 2 is a front view, FIG. 3 is a right side view, and FIG. 4 is a plan view.

In these drawings, reference numeral (1) is a Bosch fuel injection pump (1) for a diesel engine.
The fuel metering device (control rack pin) (2) for adjusting the fuel discharge amount of the fuel injection pump (1) is provided with a weight side lever (3), a torque increasing device (7) and a spring side lever (4) in order. Then, while the spring tension (GS) of the governor spring (5) elastically presses the fuel increase side (R),
The governor force (GF) by the centrifugal force of the governor weight (6) is pressed to the fuel reduction side (L) via the weight side lever (3), and the governor force (GF) and the spring tension (GS) It is configured so that it can be adjusted and moved in the fuel increasing / decreasing direction by the differential force.

The spring side lever (4) is used as a fuel metering tool.
The fuel limiter (8) is received at the full load position (F) in (2) to limit the further movement toward the fuel increase side (R). The weight side lever (3) is configured so as to elastically press the fuel increasing side (R) by the spring tension (SS) of the starting spring (9). The torque up device (7) is configured such that the torque pin (11) is elastically pressed by the torque spring (12) in the torque up case (10) so that the pin tip portion (11a) of the torque pin (11) is in the torque up case (10). ) Is made to project from the pin insertion hole (14) of the case front wall (13), and the weight side lever (3) is elastically pressed against the spring side lever (4) toward the fuel increase side (R). To do.

The torque-up case (10) is fixed to the weight-side lever (3), and a case contact transmission surface (15) is formed on the spring-side lever (4). Case end surface (1) of the case end wall (13) of the above torque-up case (10)
3a) and the pin tip (11a) of the torque pin (11) are brought into contact with the case contact transmission surface (15). The case tip end surface (13a) and the case contact transmission surface are located outside the axial center of the swing pivotally supporting portion (16) of the weight side lever (3) in the axial direction (16a). Contact point with (15) (17) Center point (17)
Displace a).

Each of the above components is specifically assembled as follows. 2 to 4, reference numeral (22)
Is a left side wall of a cylinder block of a vertical multi-cylinder diesel engine. (The left side of this diesel engine is
Corresponds to the front of a centrifugal governor. ) Attach the pump housing (2) to the front upper wall of the left side wall (22) of this cylinder block.
3) is cast integrally. This Pump Housing (23)
A governor housing (24) is fixed to the front surface of the engine, and the governor housing (24) is cast integrally with a gear case of the engine.

The fuel injection pump (1) and the fuel injection cam shaft (25) are housed in the pump housing (23). Inside the governor housing (24), the weight side lever (3), the spring side lever (4), the governor spring (5), the governor weight (6), the torque increasing device (7), the fuel limiter (8), and the starting spring. (9) The fuel injection cam gear (26) is housed. The bosses (16) and (27), which serve as swinging pivotal support portions of the spring-side lever (4) and the weight-side lever (3), are lined up in the front-rear direction with the fulcrum shaft (28) and the bearing member (29) interposed. It is swingably supported by the right side wall (30) of the pump housing (23).

The boss (27) of the weight lever (3) is a fulcrum shaft.
It is fixed to the center of (28) with bolts (31). Both ends of the fulcrum shaft (28) are rotatably supported by the bearing member (29) and positioned in the axial direction by the positioning bolts (32). The boss (16) of the spring side lever (4) is rotatably supported by the front portion of the fulcrum shaft (28), and the boss (27) of the weight side lever (3) and the bearing tool (29) are connected to each other. It is sandwiched between and is positioned in the axial direction. The bearing (29) is fixed to the right side wall (30) of the pump housing (23) with a bolt (33).

The governor weight (6) is made up of a large number of steel balls, and is housed side by side in an annular shape in an annular weight chamber (34) recessed in the left end surface of the pump drive gear (26). By the governor force (GF) by the centrifugal force of this governor weight (6), the weight side lever (3) is moved to the fuel reduction side (L) via the governor sleeve (35) / ball bearing (36) and the passive pin (37). Press to. The fuel injection cam gear (26) is externally fitted and fixed to the fuel injection cam shaft (25). The fuel injection cam shaft (25) is rotatably supported by a pair of left and right ball bearings (38).

The governor spring (5) has a spring for constant operation (5a) and a spring for resting at low speed (5b) connected in parallel across the spring side lever (4) and the speed control lever (21). It consists of what was done. When the speed control lever (21) is set to the high speed setting position (Hi), both springs (5a) and (5b) press the spring side lever (4) toward the fuel increase side (R). On the other hand, when the speed control lever (21) is set to the low speed setting position (Low), the low speed resting spring (5b) becomes free length and does not pull, and the left end hook of the spring is stopped. Since (40) floats in the spring floating long hole (39) of the spring side lever (4), only the normal operation spring (5a) elastically presses the spring side lever (4) to the fuel increase side (R). .

As a result, the spring tension (GS) of the governor spring (5) is reduced in accordance with the change rate of the governor force (GF) of the governor weight (6) that decreases in a two-hour curve during low speed operation of the engine. This prevents the governor difference (settling speed fluctuation rate) from becoming too large compared to during high speed operation. The shaft (21a) of the speed control lever (21) is rotatably supported by vertically penetrating the governor chamber lid (41). The governor chamber lid (41) is fixed to the governor housing (24) by covering the window hole (42) on the upper surface of the governor chamber.

FIG. 1 is a perspective view of a portion of the torque increasing device (7) and the case contact transmission surface (15). In FIG. 1, the case tip surface (1
3a) is formed in a small circle concentric with the torque-up case (10), and its diameter (d ₁ ) is the torque-up case (10).
The diameter is much smaller than the diameter (D). As a result, the case tip surface (13a) of the torque-up case (10) is
The width (13b) of the torque-up case (10) is smaller than the diameter (D) of the torque-up case (10), and the center of the width (13b) of the case end surface (13a) is the center of the pin (11) of the torque pin (11). It is configured so as to be substantially coincident with the center of 11a).

○ Example 2 (See FIG. 7) In the second embodiment, a part of the first embodiment is modified as follows. FIG. 7 is a diagram corresponding to FIG. In FIG. 7, the case tip end surface (13a) of the torque-up case (10) is concentric with the torque-up case (10) and is formed in a vertically long and narrow flat shape.
b) is formed to have a size significantly smaller than the diameter (D) of the torque-up case (10). This case tip surface (13a)
The center of the lateral width (13b) of the torque pin (11)
It is configured so as to be substantially aligned with the center of a).

○ Example 3. (See FIG. 8) In the third embodiment, a part of the first embodiment is modified as follows. FIG. 8 is a diagram corresponding to FIG. In FIG. 8, the case contact transmission surface (15) is
It is formed in a small circle concentric with the torque-up case (10), and this diameter (d ₂ ) is the diameter of the torque-up case (10).
It has a much smaller diameter than (D). As a result, the width (15b) of the case contact transmission surface (15) is formed to be smaller than the diameter (D) of the torque-up case (10),
The center of the lateral width (15b) of the case contact transmission surface (15) is substantially aligned with the center of the pin tip portion (11a) of the torque pin (11).

○ Example 4. (See FIG. 9) In the fourth embodiment, a part of the first embodiment is modified as follows. FIG. 9 is a diagram corresponding to FIG. In FIG. 9, the case contact transmission surface (15) is
Concentric with the torque-up case (10), it is formed into a vertically long and narrow flat shape, and this width (15b) is the torque-up case.
It is formed in a size significantly smaller than the diameter (D) of (10). The center of the lateral width (15b) of the case contact transmission surface (15) is substantially aligned with the center of the pin tip portion (11a) of the torque pin (11).

Other Embodiments In the configurations of the above-described first embodiment, second embodiment, third embodiment, or fourth embodiment, the torque increasing device (7) is transferred to the spring side lever (4) and the case contact is made. This transmission surface (1
Move 5) to the weight lever (3).

[Brief description of drawings]

1A and 1B show a torque increasing device for a centrifugal governor of a diesel engine showing Embodiment 1 of the present invention, FIG. 1A is an external perspective view, and FIG. 1B is a cross-sectional plan view showing the operation.

FIG. 2 is a partial vertical sectional front view of the entire centrifugal governor of the diesel engine showing the first embodiment of the present invention.

FIG. 3 is a right side view of a partial longitudinal section of the centrifugal governor.

FIG. 4 is a plan view of a main part of the centrifugal governor.

FIG. 5 is a front view showing the action of the centrifugal governor,
FIG. 5 (A) shows the state when the engine is started, FIG. 5 (B) shows the state at high speed full load, and FIG. 5 (C) shows the state at high speed overload.

FIG. 6 is a plan view showing the operation of the torque up device for the centrifugal governor, FIG. 6 (A) is a force acting when the engine is under a heavy load, and FIG. 6 (B) is a force shown in FIG. 6 (A). Inclination of the lever on the spring side due to
FIG. 6D shows the inclination of the spring side lever due to the force of FIG. 6C.

FIG. 7 is an external perspective view of a torque increase device for a centrifugal governor showing a second embodiment of the present invention.

FIG. 8 is an external perspective view of a torque increase device for a centrifugal governor showing a third embodiment of the present invention.

FIG. 9 is an external perspective view of a torque increasing device for a centrifugal governor showing a fourth embodiment of the present invention.

10A and 10B show a torque increasing device for a centrifugal governor according to the prior art, FIG. 10A is an external perspective view, and FIG. 10B is a cross-sectional plan view showing the operation.

[Explanation of symbols]

1 ... Fuel injection pump, 2 ... Fuel metering device, 3 ... Weight side lever, 4 ... Spring side lever, 5 ... Governor spring, 6 ... Governor weight, 7 ... Torque increasing device, 8 ... Fuel limiter, 9 ... Starting spring ,
10 ... Torque up case, 11 ... Torque pin, 11a ...
Pin tip portion, 12 ... Torque spring, 13 ... Case tip wall, 13a ... Case tip surface, 13b ... Width, 14 ... Pin insertion hole, 15 ... Case contact transmission surface, 15b ... Width, 16 ... Swing pivot support portion, 16a ... Center point, 17 ... Contact transmission part, 17a ... Center point, D ... Torque up case diameter, F ... Full load position, GF ... Governor force, GS ... Spring tension, L ... Fuel reduction side, R ... Fuel Increase side, SS ... Spring tension.

Claims (2)

[Claims] 1. A fuel injection pump for a diesel engine
The fuel metering device (2) for adjusting the fuel discharge amount of (1) is a spring of the governor spring (5) via the weight side lever (3), the torque increasing device (7) and the spring side lever (4) in this order. While tension is applied to the fuel increase side (R) with tension (GS), the governor weight is applied via the weight side lever (3).
(6) Governor force (GF) due to centrifugal force reduces fuel consumption
The spring side lever (4) is pressed to (L) and is adjusted to move in the fuel increasing / decreasing direction by the difference between the governor force (GF) and the spring tension (GS). The fuel limiter (8) is received at the full load position (F) of 2) to limit the movement to the fuel increase side (R) beyond this, and the weight side lever (3) is started. The spring tension (SS) of the spring (9) is configured so as to elastically press the fuel increase side (R), and the torque increase device (7) includes a torque increase case (10).
By elastically pressing the torque pin (11) with the torque spring (12), the pin tip portion (11a) of the torque pin (11) is opened in the case tip wall (13) of the torque up case (10). 14) so that the weight side lever (3) is elastically pressed against the spring side lever (4) toward the fuel increase side (R), and the weight side lever (3) and the spring side lever (4) The torque-up case (10) is fixed to one of the levers and the case contact transmission surface (15) is fixed to the other lever, and the case of the torque-up case (10) is fixed. Case end surface (13a) of the end wall (13) and torque pin
The pin tip portion (11a) of (11) is brought into contact with the case contact transmission surface (15), and the center point (16a) in the axial direction of the swinging pivot support portion (16) of the weight side lever (3). Diesel that is configured by displacing the center point (17a) of the contact transmission portion (17) between the case front end surface (13a) and the case contact transmission surface (15) to the outside of one side in the axial direction of the diesel engine In the torque-up device for a centrifugal governor of an engine, the width (13b) of the case tip surface (13a) of the torque-up case (10) is formed to be smaller than the diameter (D) of the torque-up case (10). , The width of the tip surface (13a) of this case (1
A torque up device for a centrifugal governor of a diesel engine, characterized in that the center of 3b) is substantially aligned with the center of the pin tip portion 11a of the torque pin 11. 2. The torque up device for a centrifugal governor of a diesel engine according to claim 1, wherein the lateral width (13b) of the case tip surface (13a) of the torque up case (10) is the same as that of the torque up case (10). Instead of forming the size smaller than the diameter (D), the width (15b) of the case contact transmission surface (15) is formed smaller than the diameter (D) of the torque-up case (10), Set the center of the width (15b) of the case contact transmission surface (15) to the torque pin.
A torque-up device for a centrifugal governor of a diesel engine, which is configured so as to substantially coincide with the center of the pin tip (11a) of (11).