JPH0425418B2 - - Google Patents

Description

Detailed Description of the Invention (Industrial Application Field) The present invention provides a governor weight that slides in the axial direction under the influence of the tilting displacement force of the governor weight, although its tilting angle changes depending on the engine speed. The thruster of the centrifugal weight device has a thruster that can be displaced, and a metering operation rod that controls the increase or decrease of the fuel injection amount of the fuel injection device by being displaced forward and backward in the axial direction, is connected to the regulator lever shaft. The regulator lever, which is rotatably operated by the regulator lever, is linked to the regulator lever by a floating lever whose intermediate portion is connected, and the displacement of the thruster of the centrifugal weight device is transmitted to the metering operation rod via the floating lever. This invention relates to a so-called minimum/maxim speed governor that controls the maximum and minimum engine speeds.

(Prior art) In this type of minimum/maximum speed governor, the lever ratio of the floating lever is usually variable, and the lever ratio is increased during high-speed operation to improve control sensitivity, thereby improving speed governing performance ( In particular, we aim to improve the settling speed fluctuation rate.
Furthermore, during low-speed operation, the lever ratio is reduced to increase the operating force on the metering operation rod to suppress hunting as much as possible and improve low-speed stability.

As a known document regarding such a minimum/maximum speed governor, for example, there is "Introduction to Fuel Injection Devices" by Yoshio Okubo, published by Sankaido (1982 edition) (see pages 202 to 210). In this known example, both ends of the floating lever are pin-coupled to a metering operation rod and a thruster of a centrifugal weight device, and the intermediate portion of the floating lever is slid along the axial direction of the floating lever. A configuration in which the lever ratio of the floating lever is variable by connecting to the regulator lever via a sliding member that is displaced and changing the relative connection position between the floating lever and the regulator lever. Therefore, the operating characteristics of the floating lever tend to change greatly due to frictional wear of the sliding member located at the center of rotation of the floating lever, and the structure is also complicated.

Furthermore, since the non-rotating floating lever and the thruster, which constantly rotates around its axis, are connected via relatively expensive bearing bolts, there is also the problem of high costs.

(Object of the Invention) The present invention has been made in an attempt to solve or improve the problems pointed out in the above-mentioned section of the prior art. It is an object of the present invention to provide a governor for an internal combustion engine that can be maintained well over a long period of time.

(Means for Achieving the Object) As a means for achieving the above object, the present invention provides a governor weight whose tilting angle changes according to the rotational speed of the engine, and a governor weight whose tilting angle is changed in the axial direction by receiving the tilting displacement force of the governor weight. The thruster of the centrifugal weight device has a thruster that is slidably displaced, and a metering operation rod that controls increase/decrease of the fuel injection amount of the fuel injection device by being moved forward and backward in the axial direction. A regulator lever that is rotatably operated by a lever shaft is linked to a floating lever whose intermediate portion is connected, and the displacement of the thruster of the centrifugal weight device is controlled by a metering operation lever via the floating lever. In the governor for an internal combustion engine, the direction of displacement of the thruster and the direction of displacement of the metering operation rod are substantially parallel, and the floating lever and the regulator lever are connected by a connecting pin. one end of the floating lever is sandwiched between the thruster and an idle spring disposed opposite thereto, and the floating lever is supported with respect to the thruster. is slidably engaged in a direction substantially perpendicular to the displacement direction of the thruster via a slider mounted so as to be slidable in the axial direction of the thruster and a thrust bearing member that abuts and supports the thruster so as to be relatively rotatable; Further, the other end is slidably engaged with the metering operation rod in a direction substantially orthogonal to the displacement direction thereof, and the regulator lever is moved into the floating position by rotating the regulator shaft. It is characterized by being constructed so that the lever can be moved in its axial direction.

(Function) In the present invention, the following effects can be obtained by the above means.

(1) Since the floating lever and the regulator lever are not of a sliding structure but have a pin connection that allows them to rotate relative to each other, frictional wear at the center of rotation of the floating lever is suppressed as much as possible. Ru.

(2) Both ends of the floating lever are slidably engaged with the metering lever and the thruster in a direction substantially perpendicular to the axial direction thereof, and on the thruster side, the floating lever is Since the other end is sandwiched between the thruster and the idle spring and is engaged via the slider, when the floating lever is moved in its axial direction by the regulator lever, the Although both ends of the floating lever are displaced in a direction perpendicular to the axial direction of the metering lever and the thruster, and the other end of the floating lever is sandwiched between the thruster and the idle spring, Smooth displacement is achieved without being affected by this, and as a result, it is as easy as possible to change and adjust the lever ratio of the floating lever to the metering operation rod and thruster, as well as the sliding movement of the slider. Be trained.

(3) The sliding action of the slider prevents the moving force of the floating lever from acting on the thruster as a prying force, thereby maintaining the operating characteristics of the thruster better.

(4) Since the other end of the floating lever is sandwiched between the thruster and the idle spring, the swinging of the floating lever is appropriately restricted at the other end, and the flow There is no rattling when changing the lever ratio of the ching lever, which helps maintain stable driving conditions.

(5) Since the thrust bearing member is interposed in the engagement portion between the thruster and the floating lever, the rotational force of the thruster is prevented from being transmitted to the floating lever side (Example) Hereinafter, preferred embodiments of the present invention will be described with reference to FIGS. 1 to 4.

1 to 3 show a governor according to an embodiment of the present invention, in which reference numeral 1 denotes a governor case, and 2 denotes governor weights 11, 11 whose tilt angle changes according to the engine speed. and a thruster 12 that is moved forward and backward in the axial direction (direction of arrow A-B) by the tilting force of the governor weights 11, 11, 3 is moved forward and backward in the direction of arrow E-F. Fuel is injected by rotating the control lever 5a of the unit injector 5 (corresponding to the fuel injection device recited in the claims) in the direction of the arrow G-H. It is a metering operation rod that acts to adjust the amount, and the metering operation rod 3 and the thruster 12 of the centrifugal weight device 2 are connected to a linkage mechanism P, which will be described later.
are interconnected by. The injection amount of the unit injector 5 is increased when the metering lever 3 is moved in the direction of arrow F and the control lever 5a is rotated in the direction of arrow H.

The linkage mechanism P is a leg disposed at an intermediate position between the centrifugal weight device 2 and the metering operation rod 3 and facing in a direction perpendicular to the axial direction of the centrifugal weight device 2 and the metering operation rod 3. A regulator lever 22 is pivotally attached to a proper position on the regulator lever shaft 6, and an axially intermediate portion 21c thereof is supported relative to the tip 22a of the regulator lever 22 by a connecting pin 24 so as to be relatively rotatable. It is composed of a floating lever 21 and a floating lever 21.

The regulator lever 22 is moved between the highest speed position (the position shown by the solid line in FIG. 1) and the idle position (the first position) by rotating the regulator lever shaft 6.
In the figure, the position indicated by the chain line, 22')
Rotated between positions. Also, when rotating the regulator lever 22 from the idle position in the direction of arrow C to position it at the maximum speed position,
The connecting pin 24 is set to move horizontally by a dimension l when facing the centrifugal weight device 2 side, and vertically by a dimension s when facing the protruding direction of the thruster 12 of the centrifugal weight device 2. There is.

The floating lever 21 has one end 21a formed into a fork shape to serve as a rack engagement portion 26, and the other end 21b formed into a flat plate shape to serve as a thruster engagement portion 27 (see FIG. 4). Of the rack engaging portion 26 and the thruster engaging portion 27 of the floating lever 21, the rack engaging portion 26 is slidably engaged with an engaging protrusion 38 protruding from the metering operation rod 3, and the thruster The engaging portion 27 is brought into abutment engagement with the thruster 12 of the centrifugal weight device 2 so as to be slidable in the axial direction of the thruster 12.

That is, as shown in FIG.
1, a saddle-shaped slider 18 has tongue-shaped guide protrusions 33, 33, . It is fitted and seated on the ching lever 21 so as to be slidable relative to it in the axial direction. At this time, the through hole 34 formed in the slider 18 and the thruster engaging portion 27
The elongated holes 28 formed in the upper and lower holes 28 are overlapped and communicated with each other in the vertical direction.

On the other hand, the thruster 12 has a governor weight 1
1 and 11, and a shaft part 13 coaxially continuous with the guide cylinder part 14, which is slidably fitted on the outside of the guide shaft 17 that rotates integrally with the guide cylinder parts 1 and 11. A ring-shaped shifter 15 is attached to the shaft portion 13 via a thrust ball bearing (corresponding to a thrust bearing member in the scope of the claims) 16.

The thruster 12 is attached to the slider 18 with the shifter 15 in contact with a contact portion 31 formed on the upper surface 18a of the slider 18. At this time, the shaft portion 13 of the thruster 12 that protrudes downward from the shifter 15 passes through the through hole 34 of the slider 18 and the elongated hole 28 of the thruster engaging portion 27, as shown in FIGS. 1 and 3. It protrudes from the lower surface side of 27.

Therefore, floating lever 21 and thruster 1
2 and 2 in the axial direction of the floating lever 21, the slider 18 slides on the thruster engaging portion 27 of the floating lever 21, so that even though the thruster 12 is rotating, First, the thruster 12 and floating lever 21 can be smoothly displaced relative to each other.

Furthermore, since the shifter 15 is interposed via the thrust bearing member 16 between the thruster 12, which is always rotating at high speed, and the slider 18, which is in a stationary state, even though the thruster 12 is always rotating, Only the thrust force from the thruster 12 is transmitted to the slider 18 side. Therefore, a frictional force acts between the slider 18 and the shifter 15 in the rotational direction, causing the abutment portion to wear out, or the rotational torque applied to the slider 18 causes the slider 18 and the floating lever 2 to become damaged.
There is no possibility that the smooth relative sliding between the two parts is obstructed.

Both ends of the floating lever 21, which is pivotally supported by the regulator lever 22 as described above, are connected to the metering operation rod 3 and the thrust 12 of the centrifugal weight device 2, respectively, so as to be relatively displaceable in the axial direction of the thruster 12. When combined, the lever ratio of the floating lever 21 when transmitting the displacement force of the thruster 12 to the metering operation rod 3 is different when the regulator lever 22 is set to the idle position and when it is set to the maximum speed position. It will change.

That is, as shown in FIG.
2 is positioned at the idle position, the ratio of the lever length on the metering operation rod 3 side to the lever length on the thruster 12 side is a/b), but when the regulator lever 22 is at the highest speed position. Once positioned, the lever ratio changes to (a'/b') (lever ratio changing function).

On the other hand, the operation of the floating lever 21 (in other words, the displacement of the thruster 12 of the centrifugal weight device 2) is controlled by two spring mechanisms, a high-speed control spring mechanism 8 and a low-speed control spring mechanism 9, which will be described later. It is regulated.

The high-speed control spring mechanism 8 includes a first governor spring 45 fitted in a first spring case 47 and a second governor spring fitted in a second spring case 48, as shown in FIGS. 1 and 2. It consists of a pair of springs with 46. Of these two springs, the first governor spring 45 is activated when the regulator lever 22 is switched from the idle position to the maximum speed position, as will be described later.
It has a small spring force that regulates the displacement of 7,
On the other hand, the second governor spring 46 regulates the maximum rotational speed of the engine, and is reduced only by the thrust force of the thruster 12 when the engine rotational speed exceeds the maximum rotational speed, as will be described later. It has a large spring force that makes it difficult to move.

Further, between the first spring case 47 of the high-speed control spring mechanism 8 and the thruster 12 of the centrifugal weight device 2, there is a substantially “L”-shaped structure rotatably supported by the governor lever shaft 7. A cover lever 51 is arranged. A first engagement ball 53 provided at one end 51a of this governor lever 51
A second engagement ball 54 provided at the tip 12a of the thruster 12 (i.e., the tip of the shaft portion 13) and the other end 51b is arranged so as to be able to abut against the first spring case 47, respectively. thruster 1
The second thrust force is transmitted to the first governor spring 45 or the second governor spring 46 of the high-speed control spring mechanism 8 via the governor lever 51.

The distance between the pair of engagement balls 53 and 54 of the governor lever 51 is such that the tilt angle of the governor weight 11 of the centrifugal weight device 2 is at its minimum (that is, when the engine is stopped), and First governor spring 45 and second governor spring 46
are both in the fully extended state, and when the second engagement ball 54 is brought into contact with the first spring case 47 due to the rotational moment due to the weight of the governor lever 51, the first engagement ball 53 and the thruster 12 are An appropriately sized 〓
The dimensions are set so that a gap is formed. This interval becomes the operating range of the idle spring 41 (that is, the idle control range), which will be described later.

As shown in FIGS. 1 and 4, the low speed control spring mechanism 9 has an idle spring 41 disposed so as to face the lower surface side of the thruster engaging portion 27 of the floating lever 21. The thruster engaging portion 27 of the lever 21 is always urged in the direction of pushing the thruster 12 in the direction of arrow B by the spring force of the idle spring 41 via the engager 42.

On the other hand, on the side of the metering operation rod 3, a stop lever shaft 65 is provided with a stop lever 66 and is always urged by a return spring 49 so as to rotate in the direction of arrow K. It is attached rotatably through the
By rotating the stop lever 66 in the direction of arrow J, the stop lever 66 engages with a stop pin 67 protruding from the metering operation lever 3, and the metering operation lever 3 is activated by the metering rack biasing spring 7.
The unit injector 5 is forcibly moved in the direction of the arrow E by the force of the spring 1, and the unit injector 5 is positioned at the no-injection position, and the operation of the engine is stopped.

Next, the operation of this governor will be briefly explained.

First, when starting the engine, the regulator lever 22 is positioned at the highest speed position (the position shown by the solid line in FIG. 1). At this time, the governor weight 11 of the centrifugal weight device 2 has not yet opened (in other words, no thrust force is acting on the thruster 12), so the thruster engaging portion 27 of the floating lever 21 is engaged with the spring of the idle spring 41. The force pushes it toward the thruster 12 side. Therefore, the floating lever 21 is tilted largely in the direction of arrow D with the connecting pin 24 as the center, as shown by the chain line (reference numeral 21'') in FIG.
position to the maximum injection amount position. By operating a starter device (not shown) in this state, the engine can be easily started.

When the engine starts, the regulator lever 22
is again switched from the maximum speed position to the idle position (FIG. 1, dashed line reference numeral 22'). When the regulator lever 22 is set to the idle position, the position of the connecting pin 24 moves in the vertical direction by a distance s, so that the regulator lever 22 is moved as shown by the chain line (reference numeral 22') in FIG. It rotates about the connecting pin 24 in the direction of arrow C, and moves the metering operation rod 3 in the direction of fuel reduction (direction of arrow E). Fuel control during this idle operation is controlled by balancing the thrust force of the thruster 12 of the centrifugal weight device 2 with the spring force of the idle spring 41 of the low speed control spring mechanism 9. At this time, the thruster 12 and the first spring case 47 of the high-speed control spring mechanism 8 are not in contact with each other (that is, idle control is performed only by the spring force of the idle spring 41). .

Next, the regulator lever 22 is rotated from the idle position to the highest speed position to perform load operation. In this case, at the beginning of rotation of the regulator lever 22, the displacement of the thruster engaging portion 27 of the floating lever 21 is regulated by the thruster 12 and the idle spring 41. As the floating lever 21 is rotated, the floating lever 21 operates to move the metering operation rod 3 toward the fuel increasing side, thereby increasing the engine speed.

However, the first governor spring 45 of the high-speed control spring mechanism 8 that regulates the operation of the thruster 12 is moved to the fully retracted position by the thrust force acting on the thruster 12 when the rotation speed of the engine 64 slightly exceeds the idle rotation speed. (Fig. 3, state shown). Therefore, the thruster 12 is thereafter held at the same position until the engine speed reaches the maximum speed. For this reason,
In this state, the metering action is not performed by the centrifugal weight device 2, and the metering action is performed only by rotating the regulator lever 22 (medium/low speed control).

On the other hand, when the engine speed increases beyond the maximum speed, the thrust force acting on the thruster 12 overcomes the spring force of the second governor spring 46 and the second governor spring 46 is compressed. is rotated in the direction of arrow C by the thruster 12 regardless of the lever position of the regulator lever 22,
The metering operation rod 3 is rotated in the fuel decreasing direction (in the direction of arrow E) to reduce its rotational speed to the maximum rotational speed (maximum speed control).

Furthermore, the lever ratio of the floating lever 21 (i.e., the ratio of the lever length on the metering operation rod 3 side from the connecting pin 24 to the lever length on the thruster 12 side from the connecting pin 24) is small in the low speed range, and is small in the high speed range. As the thrust force of the centrifugal weight device 2 is small, the operating force applied to the metering operation rod 3 increases, which reduces the low-speed stability of the engine. In addition, even if rotational fluctuation occurs, this does not greatly affect the operation of the metering operation rod 3, so hunting can be effectively prevented without providing a damper spring. On the other hand, in the high speed range, the control sensitivity is sensitive, so the settling speed fluctuation rate is improved and the speed control performance is improved.

(Effects of the Invention) As is clear from the above description, the governor for an internal combustion engine of the present invention has the following features: (1) The lever ratio of the floating lever is small in the low speed operating range of the engine and becomes large in the high speed operating range. Since it is configured to be automatically set according to the engine speed, it improves low-speed stability in low-speed operating ranges, and improves control sensitivity in high-speed operating ranges. (2) Both ends of the floating lever are slidably engaged with the metering operation rod and the thruster in a direction substantially perpendicular to their axial directions. At the same time, on the thruster side, the other end of the floating lever is sandwiched between the thruster and the idle spring and is engaged via a slider, so that the other end of the floating lever is Even though the end side is sandwiched between the thruster and the idle spring, smooth displacement is achieved without being affected by this, and as a result, this also works to prevent the thruster from prying force due to sliding of the slider. This makes it as easy as possible to change and adjust the lever ratio of the floating lever to the metering operation rod and the thruster.

(3) Since the other end of the floating lever is sandwiched between the thruster and the idle spring, the swinging of the floating lever is appropriately restricted at the other end, and the flow There is no rattling when changing the lever ratio of the ching lever, which helps maintain stable driving conditions.

(4) Since the center of rotation of the floating lever is a pin support, unlike the conventional structure in which the center of rotation of the floating lever has a sliding support structure, the center of rotation of the floating lever may wear out and cause the floating to occur. There is little fear that the operating characteristics of the lever and, by extension, the regulating characteristics of the governor will change, and the governor's regulating action can be maintained well over a long period of time. (5) A thruster that constantly rotates around its axis The thruster engaging portion of the floating lever, which is non-rotating, is connected via a slider that is slidably displaced in the axial direction along the thruster engaging portion and a thrust bearing member that abuts and supports the thruster so as to be relatively rotatable. Therefore, the thruster and the thruster engaging portion can be smoothly displaced relative to each other in the axial direction of the thruster engaging portion even though the thruster is rotating around the axis. , the operability of the floating lever is improved. (6) The floating lever and the regulator lever are pin supported, and the thruster engaging portion of the floating lever and the thruster are constructed to have a simple and inexpensive slider and thrust bearing. Since the floating lever and the regulator lever are connected through a member so as to be relatively displaceable, the floating lever and the regulator lever must be slid and supported through a slide member with a complex structure, and the floating lever and thruster must be connected to each other using relatively expensive bearings. Compared to conventional governors connected via bolts, the structure can be simplified and costs can be reduced, among other effects.

[Brief explanation of drawings]

FIG. 1 is a sectional view of a governor according to an embodiment of the present invention;
Figure 2 is a -longitudinal cross-sectional view of Figure 1, Figure 3 is a vertical cross-sectional view of Figure 1.
FIG. 4 is an exploded perspective view of essential parts of the governor shown in FIG. 1. 2...Centrifugal weight device, 3...Measuring operation rod, 5...
...(Fuel injection system) Unit injector, 6...
... Regulator lever shaft, 11 ... Governor weight, 12 ... Thruster, 16 ... Thrust bearing member (thrust ball bearing), 18 ... Slider, 2
1...Floating lever, 22...Regulator lever, 41...Idle spring.

Claims (1)

[Claims] 1 A centrifugal weight device having governor weights 11, 11 whose tilting angle changes according to the engine rotation speed, and a thruster 12 which is slidably displaced in the axial direction by receiving the tilting displacement force of the governor weights 11, 11. The thruster 12 of No. 2 and the metering operation rod 3, which controls the increase/decrease of the fuel injection amount of the fuel injection device 5 by being moved forward and backward in the axial direction, are rotated by the regulator lever shaft 6. The regulator lever 22 is interconnected by a floating lever 21 whose intermediate portion is connected to the regulator lever 22,
The governor for an internal combustion engine is configured to transmit the displacement of the thruster 12 of the centrifugal weight device 2 to the metering operation rod 3 via the floating lever 21,
The displacement direction of the thruster 12 and the metering operation rod 3
The floating lever 21 and the regulator lever 22 are substantially parallel to each other.
are relatively rotatably supported by a connecting pin 24, and one end 21a of the floating lever 21 is sandwiched between the thruster 12 and an idle spring 41 disposed opposite thereto. and a slider 18 that is slidably attached to the thruster 12 in the axial direction of the floating lever 21 and the thruster 12.
is slidably engaged in a direction substantially perpendicular to the direction of displacement of the thruster 12 via a thrust bearing member 16 that abuts and supports the thruster 12 so as to be relatively rotatable, and the other end 21b is connected to the metering operation rod 3. The regulator lever 22 is slidably engaged with the floating lever 21 in a direction substantially perpendicular to its displacement direction, and furthermore, the regulator lever 22 moves the floating lever 21 in the axial direction by rotating the regulator shaft 6. A governor for an internal combustion engine, characterized in that it is configured to be movable.