JP2784539B2 - Fuel governor for hydraulic governor - Google Patents

Description

Description: TECHNICAL FIELD The present invention relates to a hydraulic governor.

(Prior Art) In general, a hydraulic governor generally includes an output lever interlockingly connected to a fuel metering member, an output piston which is moved by hydraulic pressure to rotate the output lever via an output terminal shaft, and a flyweight according to the engine speed. The control valve includes a control valve for controlling the hydraulic pressure by the centrifugal force of the mechanism, and a speed control lever for adjusting a set load of a speed spring that is balanced with the centrifugal force of the flyweight mechanism. The fuel injection amount limiting device for limiting the maximum fuel injection amount is provided with, for example, a fuel limiting bolt, and is adjusted to a predetermined limiting amount.

However, once the limit amount is set, as shown in FIG. 8, the limit injection amount is fixed at a constant value r regardless of the partial load operation and the full load operation, and the following problem occurs.

In other words, when an overload is applied during partial load operation with a large marine engine, the rack position is rapidly moved to the fuel increasing side by the action of the hydraulic governor and reaches the same limit r as at full load, but the rotation speed is increased. Since the number does not increase abruptly, the injection amount becomes excessive. At this time, generation of black smoke and surging of the exhaust turbine and the like occur.

(Object of the Invention) An object of the present invention is to make it possible to automatically change the fuel-limited injection amount according to the rotation speed, thereby generating black smoke when a sudden overload occurs during partial load operation. And surging of the exhaust turbine.

Further, the invention is intended to make it possible to incorporate the injection amount limiting device into the hydraulic governor mechanism to facilitate the assembly to the engine.

Another object of the present invention is to make it possible to easily change the rate of change of the fuel injection amount restriction amount.

(Technical Means for Achieving the Object) In order to achieve the above object, the present invention provides a flyweight mechanism 16 that expands in a case-like governor body 1 by centrifugal force in accordance with the number of machine revolutions, A control valve 13 operated by a flyweight mechanism 16, an output piston 20 hydraulically controlled by the control valve 13, a terminal shaft 43 connected to the output piston 20 via a terminal arm 39,
A speed control shaft 46 disposed substantially parallel to the terminal shaft 43 and having a speed control lever 47 at an end outside the governor body; a fork 50 formed on the speed control shaft 46;
39 and a floating lever 51 whose intermediate portion is connected to a speed spring 57 that balances the centrifugal force of the flyweight mechanism 16 with one end of the terminal shaft 43 protruding outside the governor body. An output lever 60 is connected to the projecting portion, a tip end of the output lever 60 is connected to a fuel metering member, and a fuel injection amount of a hydraulic governor for changing a set load of a speed spring 57 by rotating a speed control lever 47. In the limiting device, an eccentric lever 65 is fixed to an end of the output terminal shaft 43 outside the governor main body, and an eccentric portion 64 is attached to a tip end of the eccentric lever 65.
The end portion of the output lever 60 is pivotally connected via a through hole, and a long hole 66 is formed in an intermediate portion of the output lever 60 outside the governor body, and a rotation fulcrum shaft 67 can be moved within the long hole 66 in the long hole. And a fulcrum shaft position changing lever extending outside the governor body 1 so as to extend over the rotation fulcrum shaft 67 and the speed control shaft 46.
72, the fulcrum shaft position changing lever 72 is rotatably supported by a fixed shaft 71 provided in the governor main body 1 intermediate the speed control shaft 46 and the terminal shaft 43. One end of the fulcrum shaft position changing lever 72 is provided by protruding an end of the fulcrum shaft position changing lever 72 by fixing the fulcrum shaft position changing eccentric lever 78 to the protruding portion. The portion supports the fulcrum shaft 67, and has a long hole 76 formed in the other end in the length direction of the lever, and the eccentric pin of the eccentric lever 78 for changing the fulcrum shaft position is formed in the long hole 76.
As the speed control lever 47 is turned to the speed decreasing side, the fulcrum shaft 67 is moved to the lever ratio side for reducing the fuel injection amount with respect to the turning amount of the terminal shaft 43 as the speed control lever 47 is turned to the speed decreasing side. A fuel injection amount limiting device for a hydraulic governor, characterized in that:

(Operation) When the speed control lever is operated to the speed decreasing side, the fulcrum shaft moves to, for example, the adjustment member mounting side of the output lever via the fulcrum shaft position changing mechanism, and the lever ratio decreases. As a result, the limited injection amount is reduced, and the fuel injection amount is not excessively increased even when a sudden overload is applied.

(Example) FIG. 3 is a longitudinal sectional view of a hydraulic governor to which the present invention is applied, viewed from the front side (operating side), and the right side of the drawing (fuel injection pump side) is assumed to be the front. First, the basic structure of the hydraulic governor will be described with reference to FIG. The governor body 1 is directly attached to the engine, and has an oil sump chamber in the upper half.
The governor body 1 has an output piston 20 at the front half thereof, a control valve 13 at a rear position thereof, and a gear shaft 2 at a lower end of the governor body 1 at which the rotation of the engine is transmitted at an increased speed. I have. One gear 6 of the gear pump 5 is formed integrally with the upper end of the gear shaft 2, and the other gear 7 meshing with the gear 6 is formed integrally with the lower end of the sleeve 8. The oil suction port 29 of the gear pump 5 communicates with the oil sump chamber 12, and the discharge side communicates with a regulating valve (not shown) for obtaining a constant pressure. The above-mentioned regulating valve keeps the high-pressure hydraulic oil generated by the gear pump at a constant pressure, and
The oil is fed into the oil passage 30 from 34, and at the same time, the overflowed hydraulic oil is returned to the gear pump suction side.

The sleeve 8 is fitted in the sleeve support hole 10 of the governor main body 1 in a liquid-tight state, is rotatable and is immovable in the vertical direction, and has a fly-Eit mechanism 16 supported at the upper end so as to be able to expand in the radial direction. I have. Three annular grooves 18a, 18b, 18c are formed on the outer periphery of the sleeve 8 at intervals in the vertical direction, and these annular grooves 18a, 18b, 18c are opened to the inner peripheral hole of the sleeve 8 through passage holes. I have. The lower annular groove 18c communicates with the oil reservoir 12 via an oil passage 33.

The control valve 13 is rotatably and vertically movably fitted into the inner peripheral hole of the sleeve 8, and the lower surface of the upper end of the control valve 13 contacts the arm of the fly weight mechanism 16, and the fly weight When the mechanism 16 is expanded by centrifugal force, it is pushed upward. A collar-shaped land portion 13a is formed at a substantially central portion in the vertical direction of the control valve 13, and small-diameter portions 13b and 13c are formed on both upper and lower sides thereof.

The lower portion of the output piston 20 is vertically movably fitted to the cylinder portion 23 to partition the inside of the cylinder portion 23 into an upper annular oil chamber 21 and a lower oil chamber 22.
It moves up and down due to the pressure difference between 21 and 22. The upper annular oil chamber 21 has an oil passage 30 into which the high-pressure oil is fed.
Through the upper annular groove 18a of the sleeve 8. The lower oil chamber 22 of the cylinder portion 23 communicates with the intermediate annular groove 18b of the sleeve 8.

A compensating bushing 37 for compensation is fixed below the cylinder portion 23 so as to be isolated therefrom.
A compensating piston 36 is fitted in 37. The compensating piston 36 is connected to a rod 35 fitted and supported by the output piston 20, and the rod 35 moves upward due to a difference in spring strength between the compensating upper spring 25 and the lower spring 26 in the output piston 20. Has been energized.
The upper annular chamber of the compensating piston 36 communicates with a chamber 10a at the lower end of the sleeve support hole 10, and the chamber 10a communicates with the oil sump chamber 12 via a needle valve (not shown). The lower chamber of the compensating piston 36 communicates with the oil reservoir 12 via an oil passage (not shown).

An output terminal shaft 43 is disposed above the oil sump chamber 12 at a position forward of the control valve 13 and is rotatably supported by the governor main body 1. The terminal shaft 43 has a rear end outside the governor main body on the back side. An output lever 60 is operatively connected via an eccentric lever mechanism to be described later, and an upper end of the output lever 60 is operatively connected to a fuel metering rack of a front fuel injection pump via a fuel metering rod 61 and the like. A terminal arm 39 extending forward and upward is fixed to a portion of the terminal shaft 43 inside the governor main body.
And a pin 41 pivotally connected to the upper end of the output piston 20. That is, the vertical movement of the output piston 20 rotates the terminal shaft 43 via the terminal arm 39, and further rotates the output lever 60 via the eccentric lever mechanism to perform fuel metering. I have.

The terminal shaft 43 is located behind the control valve 13.
A speed control shaft 46 is disposed at substantially the same height as the speed control shaft 46, and is rotatably supported by the governor body 1. A speed control lever 47 for manual operation is fixed to an end of the speed control shaft 46 outside the governor main body, and a fork 50 extending forward is fixed to an inner portion of the governor main body 1. The rear end of a floating lever 51 extending forward is pivotally connected to the fork 50 via a pin, and the front end of the rotating lever 51 has a long groove 55 connected to the speed droop adjuster 54 of the terminal arm 39. I agree. A spring pressing piece 52 is supported at an intermediate portion of the floating lever 51 via a pin, and a speed spring 57 is contracted between the spring pressing piece 52 and the upper end of the control valve 13. That is, by rotating the speed control lever 47 to change the set load of the speed spring 57, the rotation speed can be set to a desired speed.

FIG. 1 is a view of the governor body viewed from the back side of FIG. 3, FIG.
FIG. 1 is a top view of FIG. 1 and shows an output lever 60 using an eccentric lever mechanism which is a main part of the present invention.
And the mounting structure of the fulcrum shaft position changing lever 72 will be described. Note that since FIG. 1 is a rear view, the left side of the drawings is the front in FIGS. 1 and 2. In FIG. 2, an eccentric lever 65 is fixed to the rear end of the terminal shaft 43, and an output eccentric shaft 64 is fixed to the tip of the eccentric lever 65. An eccentric lever 78 for changing a fulcrum is fixed to an end on the back side of the speed control shaft 46, and an eccentric pin 75 is screwed to the eccentric lever 78 so that the mounting position can be freely changed. A fulcrum shaft position changing lever 72 is disposed on the back side of both eccentric levers 65 and 78, and a fixed shaft 71 projecting from the back side of the governor body 1 is fixed between the terminal shaft 43 and the speed control shaft 46, An intermediate portion of the fulcrum shaft position changing lever 72 is rotatably supported on the fixed shaft 71. The output lever 60 is disposed on the back side of the front end of the fulcrum shaft position changing lever 72,
A fulcrum shaft 67 which can be freely changed in position, which is a rotation fulcrum of 60, is fixed to the front end of a fulcrum shaft position changing lever 72.

In FIG. 1, an output lever 60 has a hole 60a formed at the lower end thereof rotatably fitted to an eccentric shaft 64. An elongated hole 66 is formed at an intermediate portion of the output lever 60 and extends in a direction substantially along a tangential direction of a circumference around the fixed shaft 71.
A slider 68 having a rectangular cross section is fitted in the slot 66 so as to be movable in the length direction of the long hole, and the slider 68 is
Are rotatably fitted to a fulcrum shaft 67 at the front end of the shaft. A long hole 76 long in the length direction of the lever is formed at a rear portion of the fulcrum changing lever 72, and a slider 73 having a rectangular cross section is fitted in the long hole 76 so as to be movable in the long hole length direction. Is rotatably fitted to the eccentric pin 75. That is, by rotating the speed control lever 47 in, for example, the speed decreasing direction, the fulcrum shaft position changing lever 72 is rotated around the fixed axis in the K1 direction via the eccentric lever 78 and the eccentric pin 75 of the speed control shaft 46, As a result, the fulcrum shaft 67 is raised, and the lever ratio X / Y of the output lever 67 is increased.
Is designed to be smaller.

The eccentric lever 78 for changing the fulcrum shaft position has a plurality of female screws 77 for pin mounting, and by appropriately selecting the female screw 77 and mounting the eccentric pin 75, the speed control lever
The amount of movement of the fulcrum shaft 67 with respect to the amount of rotation of 47 can be adjusted. For example, when the position of the eccentric pin 75 is moved to the fixed shaft side, the fulcrum shaft with respect to the rotation amount of the speed control lever 47 is
The movement amount of 67 has become large.

The operation will be described. First, the basic operation of the hydraulic governor
This will be briefly described with reference to the drawings. The rotation of the crankshaft of the engine is transmitted to the gear shaft 2 and the gear pump 5 rotates the oil sump chamber 12.
The oil sucked in from above and pressurized is adjusted to a constant pressure by a recurring valve to pressurize the oil passage 30 and return the overflowed oil to the reservoir chamber 12.

When the load and the output are balanced, the centrifugal force of the flyweight mechanism 16 and the load of the speed spring 57 are balanced, the land 13a of the control valve 13 closes the communication hole of the intermediate annular groove 18b, and the cylinder There is no oil spill from the lower oil chamber 23. Therefore, the output piston 20 is kept at a fixed position.

If the load is reduced while the speed control lever 47 is maintained at a fixed position, the centrifugal force of the flyweight mechanism 16 increases due to an increase in the rotation speed, and the control valve 13 rises, and The portion 13a is located between the upper annular groove 18a and the intermediate annular groove 18b to block between the two annular grooves 18a and 18b, and the intermediate annular groove 18b and the lower annular groove 18c, and the lower small diameter portion 13c
To communicate through. As a result, the lower oil chamber of the cylinder 23
The oil of 22 is discharged to the oil reservoir 12 through the oil passage 31, the lower small diameter portion 13c and the oil passage 33, the output piston 20 descends, and the output lever 60 is turned to the fuel decreasing side via the terminal shaft 43. Move.
This suppresses an increase in the rotation speed, lowers the control valve 13 to return the speed spring 57 and the centrifugal force to a balanced state, and the land portion 13a closes the intermediate annular groove 18b again. When the terminal shaft 43 rotates toward the fuel decreasing side as described above, the floating lever 51 slightly lowers around the speed control shaft 46 to slightly compress the speed spring 57, and slightly increases the set load. It has become.

When the load increases, the pressure of the regulating valve is applied to the lower oil chamber 22 of the cylinder section 23 by lowering the control valve 13, the output piston 20 rises, and the output lever 60 is turned to the fuel increasing side. To reduce the rotation speed. At this time, the output transmission between the terminal shaft 43 and the output lever 60 is performed, for example, in FIG. 1, when the terminal shaft 43 is turned to the fuel increasing side, via the eccentric lever 65 and the eccentric shaft 64. Rotates toward the fuel increasing side with the fulcrum shaft 67 as a fulcrum.

Next, the case where overload is applied when the speed control lever 47 is set to the full state on the speed increasing side or the slow state (partial load state) on the speed decreasing side will be described.

FIG. 5 shows the positional relationship between the levers when the speed control lever is full, in which the solid line shows the position of each lever in the steady state and the broken line shows the position of each lever when an overload is applied. In this state, the center P of the fulcrum shaft 67 substantially coincides with the center O2 of the terminal shaft 43, and the lever ratio L of the output lever 60 is X / Y. When the engine speed is suddenly reduced due to an overload on the engine, the terminal shaft 43 rotates to the fuel increasing side to the maximum amount by the action of the governor, and the position of the eccentric shaft 64 is in the range of q from Q to Q '. If the eccentric shaft 64 moves, the upper end connecting portion of the output lever 60 moves from R to R 'in response to the movement of the eccentric shaft 64, and the movement amount r is represented by L * q.

FIG. 6 shows the positional relationship between the levers in the speed control lever slow (partial load) state, in which the solid line shows the position of each lever in a steady state, and the broken line shows the position of each lever when an overload is applied. In this state, the center P of the fulcrum shaft 67
Has moved above the center O2 of the terminal shaft 43,
The lever ratio L '= X' / Y 'of the output lever 60 is smaller than the lever ratio L = X / Y of FIG. Here, when an overload is applied, the position of the eccentric shaft 64 is moved in the range of q to the maximum fuel increase side from Q to Q 'by the same action as in the full state. The upper end connecting portion of the output lever 60 moves in the range of r 'from R to R', but the lever ratio L '= X'
Since / Y 'is smaller than the lever ratio L in FIG. 5, the moving amount r' = L'.times.q of the connecting point P is equal to r in the full state.
= L × q, so that the increase in the fuel injection amount (maximum limit injection amount) is small, thereby preventing excess fuel.

That is, as the speed control lever 47 is rotated from the speed control lever full state of FIG. 1 to the speed control lever slow state as shown in FIG. 4, the lever ratio decreases accordingly, thereby limiting as shown in FIG. The injection amount r becomes smaller as r '.

(Effects of the Invention) As described above, according to the present invention, a flyweight mechanism 16 that expands in a case-like governor body 1 by centrifugal force in accordance with the number of machine revolutions, and is operated by the flyweight mechanism 16. A control valve 13, an output piston 20 hydraulically controlled by the control valve 13, a terminal shaft 43 connected to the output piston 20 via a terminal arm 39,
A speed control shaft 46 disposed substantially parallel to the terminal shaft 43 and having a speed control lever 47 at an end outside the governor body; a fork 50 formed on the speed control shaft 46;
39 and a floating lever 51 whose intermediate portion is connected to a speed spring 57 that balances the centrifugal force of the flyweight mechanism 16 with the floating shaft 51.One end of the terminal shaft 43 projects outside the governor main body. An output lever 60 is connected to the projecting portion, a tip end of the output lever 60 is connected to a fuel metering member, and a fuel injection amount of a hydraulic governor for changing a set load of a speed spring 57 by rotating a speed control lever 47. In the limiting device, an eccentric lever 65 is fixed to an end of the output terminal shaft 43 outside the governor main body, and an eccentric portion 64 is attached to a tip end of the eccentric lever 65.
The end portion of the output lever 60 is pivotally connected via a through hole, and a long hole 66 is formed in an intermediate portion of the output lever 60 outside the governor body, and a rotation fulcrum shaft 67 can be moved within the long hole 66 in the long hole. And a fulcrum shaft position changing lever extending outside the governor body 1 so as to extend over the rotation fulcrum shaft 67 and the speed control shaft 46.
72, the fulcrum shaft position changing lever 72 is rotatably supported by a fixed shaft 71 provided in the governor main body 1 intermediate the speed control shaft 46 and the terminal shaft 43. One end of the fulcrum shaft position changing lever 72 is provided by protruding an end of the fulcrum shaft position changing lever 72 by fixing the fulcrum shaft position changing eccentric lever 78 to the protruding portion. The portion supports the fulcrum shaft 67, and has a long hole 76 formed in the other end in the length direction of the lever, and the eccentric pin of the eccentric lever 78 for changing the fulcrum shaft position is formed in the long hole 76.
As the speed control lever 47 is turned to the speed decreasing side, the fulcrum shaft 67 is moved to the lever ratio side for reducing the fuel injection amount with respect to the turning amount of the terminal shaft 43 as the speed control lever 47 is turned to the speed decreasing side. (1) During the partial load operation, the increase in the fuel injection amount with respect to the rotation amount of the terminal shaft 43 decreases and the maximum limit fuel injection amount also decreases. Therefore, the fuel amount increases when a sudden load is applied. However, there is no concern about excessive increase in fuel, and generation of black smoke and surging of the exhaust turbine can be prevented.

(2) The rotation of the speed control lever 47 causes the speed spring 57
At the same time as changing the set load, the position of the fulcrum shaft of the output lever 60 can be changed accordingly. No adjustment operation is required.

(3) Eccentric levers 65 and 78 are provided at the axial ends of the existing output terminal shaft 43 and the speed control shaft 46 on the outer side of the governor body 1, respectively, and the tip of the eccentric lever 65 of the output terminal shaft 43 is provided. The end of the output lever 60 is supported on the eccentric shaft 64 via the eccentric shaft 64, and the both ends of the fulcrum shaft position changing lever 72 disposed outside the governor body 1 are connected to the long holes 66, 67 and the fulcrum shaft 6 respectively.
7 and the output lever 60 and the eccentric lever 7 via the eccentric pin 75.
8, the fulcrum shaft position changing mechanism including the fulcrum shaft position changing lever 72 uses the conventional hydraulic governor parts without significantly changing the conventional hydraulic governor mechanism. The outer surface of the main body can be simply and compactly additionally provided, and a reduction in manufacturing cost can be achieved.

(4) If the mounting position of the eccentric pin with respect to the fulcrum shaft position changing eccentric lever 72 fixed to the speed control shaft 46 can be freely changed in the eccentric lever length direction as in the second aspect of the present invention, the speed control is performed. The rate of change of the fuel-limited injection amount with respect to the amount of rotation of the lever can be easily changed.

[Brief description of the drawings]

FIG. 1 is a rear view of a fuel injection amount limiting device for a hydraulic governor to which the present invention is applied (a rear view when FIG. 3 is the front side), and FIG. 2 is a view of FIG. FIG. 3 is a front view of the entire section of the hydraulic governor, FIG. 4 is a front view of the same part as FIG. 1 in a partial load state, and FIG. 5 is a simplified view of FIG. FIG. 6 is a simplified diagram of FIG. 4 showing the relationship of the link mechanism at the time of full load, and FIG. 6 is a simplified diagram of the operation showing the relationship of the link mechanism at the time of partial load. FIG. 8 is an injection amount characteristic diagram when the present invention is applied, and FIG. 8 is an injection amount characteristic diagram of a conventional example. 13 ... Control valve, 16 ... Fly weight mechanism,
20 …… Output piston, 43 …… Output terminal shaft, 47 ……
Speed control lever, 64: Eccentric shaft, 65: Eccentric lever, 66
············································································ Elongated hole

──────────────────────────────────────────────────続 き Continuation of the front page (56) References JP-A-61-104125 (JP, A) JP-A-61-23835 (JP, A) JP-A-57-165633 (JP, A) 30723 (JP, U) Fully open 58-124630 (JP, U) Fully open 63-71438 (JP, U) (58) Fields studied (Int. Cl. ⁶ , DB name) F02D 1/00-1 / 18

Claims (2)

(57) [Claims] 1. A flyweight mechanism (16) that expands by centrifugal force according to a machine rotation speed in a case-like governor body (1), and a control valve (13) operated by the flyweight mechanism (16). ), An output piston (20) hydraulically controlled by the control valve (13), and the output piston (20)
A terminal shaft (43) connected to the terminal shaft (39) via a terminal arm (39), and a speed control shaft (47) disposed substantially parallel to the terminal shaft (43) and having a speed control lever (47) at an end outside the governor body. A speed spring which is pivotally connected between a terminal arm (39) and a fork (50) formed on the speed control shaft (46) and a speed control shaft (46) so that an intermediate portion thereof balances the centrifugal force of the flyweight mechanism (16). (57), and one end of the terminal shaft (43) protrudes out of the governor main body, and the output lever (60) is connected to the protruding portion. The tip is connected to the fuel metering member, and the speed control lever (47) is turned to rotate the speed spring (5).
7) In the fuel injection amount limiting device for a hydraulic governor for changing the set load, an eccentric lever (65) is fixed to an end of the output terminal shaft (43) outside the governor body, and the eccentric lever (65) is The end of the output lever (60) is pivotally connected to the tip via an eccentric shaft (64), and a long hole (6
6), and a rotation fulcrum shaft 67 is movably fitted in the long hole (66). The rotation fulcrum shaft (67) and the speed control shaft are provided outside the governor body 1. A fulcrum shaft position changing lever (72) extending so as to straddle (46) is arranged, and
2) is rotatably supported on a fixed shaft (71) provided in the governor body (1) part between the speed control shaft (46) and the terminal shaft (43), and the end of the speed control shaft (46) Part out of the governor body,
An eccentric lever (78) for changing the fulcrum shaft position is fixed to the protrusion, and an eccentric pin (75) is provided at an end of the eccentric lever (78). One end of the fulcrum shaft position changing lever (72) is Support axis (6
7), and a long hole (76) is formed in the other end portion in the length direction of the lever, and the eccentric pin (75) of the eccentric lever (78) for changing the fulcrum shaft position is inserted into the long hole (76). As the speed control lever (47) is turned to the speed decreasing side, the fulcrum shaft (67) is moved toward the lever ratio side to reduce the fuel injection amount with respect to the rotation amount of the terminal shaft (43). ). A fuel injection amount limiting device for a hydraulic governor, wherein 2. The hydraulic governor according to claim 1, wherein the mounting position of the eccentric pin (75) with respect to the eccentric lever (78) fixed to the speed control shaft (46) can be changed in the eccentric lever length direction. Fuel injection amount limiting device.