JP2000097052A - Centrifugal governor of diesel engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To lessen the swing inertia of a governor lever for enhancement of the responsive sensitivity and eliminate necessity for components control of a torque-up device. SOLUTION: A governor weight 37 is coupled interlockingly with the input part 16 of a first lever 13A while a start spring 19 and a regulating tool 39 of a fuel injection pump are coupled interlockingly with the output part 17, and a speed governing lever 28 is coupled with the second lever 13B through a governor spring 27, and the swinging end 13b of the second lever 13B is received by a swing restrict pin 18 in the position 4/4 equivalent to the total load. A torque-up means 14 to be interposed between the first lever 13A and second lever 13B is made from a member capable of elastically deforming the second lever 13B and provided with a regulating hole 15 for regulating the torque-up amount by lessening the bending rigidity of the second lever 13B located between the swinging support shaft 11 of the second lever 13B and the mounting point Ps of the spring 27.

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 more particularly to a novel technique for adjusting a torque increase of the centrifugal governor.

[0002]

2. Description of the Related Art As a centrifugal governor for a diesel engine, for example, the one shown in FIG. 6 has been conventionally known.
Here, FIG. 6 is a front view of a centrifugal governor according to a conventional example. As shown in FIG. 6, the centrifugal governor 10 includes a governor lever 13 pivotally supported by a pivot shaft 11, and the governor lever 13 includes a first lever 13A and a second lever 13B. A torque increasing device 20 is interposed between the first lever 13A and the second lever 13B.

A governor weight 37 is operatively connected to the input portion 16 of the first lever 13A via a governor sleeve 36, and a start spring 19 and a rack pin 39 of the fuel injection pump 3 are operatively connected to the output portion 17 of the first lever 13A. The speed control lever 28 is connected to the second lever 13B via the governor spring 27, and the rack pin 39 is connected to the fuel increasing side R by the start spring 19 and the governor spring 27.
While the governor weight 37 presses the rack pin 39 to the fuel reduction side L via the first lever 13A. Then, the governor lever 13 is swung by an unbalanced force between the elastic pressure on the fuel increasing side R and the pressing force on the fuel decreasing side L, and the rack pin 39 is adjusted and moved.

The torque-up device 20 includes a case body 21, a torque pin 23 projecting from the front end side of the case body 21 so as to be able to advance and retreat, and facing the receiving portion 26 of the second lever 13 B so as to resiliently contact with the case body 21. A torque spring (not shown) accommodated in the pressure pin 21 for resiliently pressing the torque pin 23. When the engine shifts from the full load operation state to the overload operation state, the fuel injection amount is increased to exert the tenacity. It is configured as follows. FIG.
Reference numeral 2 is the governor case, 4 is the governor weight 37.
The governor shafts for rotating are shown.

[0005]

In the above conventional example, the first
Since the torque-up device 20 is interposed between the lever 13A and the second lever 13B, the swing inertia of the governor lever 13 increases due to the mass of the torque-up device 20. In addition, when metering the amount of torque increase with a built-in actual machine or with a dedicated torque increase meter,
In the case of being out of the metering range, it is necessary to prepare a plurality of torque pins and torque springs in advance and exchange them appropriately, which makes the parts management troublesome.
The present invention has been made in view of such circumstances, and has as its technical object to reduce the swing inertia of a governor lever to increase response sensitivity and eliminate the need for component management of a torque-up device.

[0006]

The invention according to claim 1 has the following basic configuration. For example, FIG.
As shown in (B), at least the first lever 13A and the second lever 1 pivotally supported by the pivot shaft 11 respectively.
3B, a governor lever 13 is formed, and a governor weight 37 is interlockedly connected to the input portion 16 of the first lever 13A, and a start spring 19 and a metering device 39 of the fuel injection pump 3 are interlockedly connected to the output portion 17. The governing lever 28 is connected to the second lever 13B via the governor spring 27, and the swing end 13b of the second lever 13B is
At the full load equivalent position 4/4 by the rocking regulation pin 18, and the torque increasing means 14 is interposed between the first lever 13A and the second lever 13B to change the engine from the full load operation state to the overload operation state. Is configured to increase the fuel injection amount in conjunction with the shift to. Here, “the governor lever 13 is composed of at least the first lever 13A and the second lever 13B” means that the governor lever 13 is composed of two or more levers. The governor lever 13 that interposes the third lever 13C between the first lever 13A and the second lever 13B is not excluded.

According to the first aspect of the present invention, there is provided a centrifugal governor having the above-mentioned basic structure, wherein the following torque increasing means is employed in place of the conventional torque increasing device. This torque increasing means 14
, Together constitute the second lever 13B in an elastically deformable member, the bending of the second lever 13B between the rack attachment point P _S of the oscillating support shaft 11 and the governor spring 27 of the second lever 13B It is characterized in that a metering hole 15 for adjusting the torque increase amount by reducing the rigidity is formed.

According to a second aspect of the present invention, there is provided a centrifugal governor according to the first aspect, wherein the metering hole 15 is received at a middle portion of the second lever 13B to receive the contact piece 25 of the first lever 13A. It is characterized in that it is opened near the stop 26.

[0009]

According to the first aspect of the present invention, in the centrifugal governor having the above-described basic configuration, the second lever made of an elastically deformable member instead of the conventional torque-up device 20 is used. Since the torque-up means 14 is constituted only by drilling a metering hole 15 for metering the torque-up amount in 13B, in adjusting the torque-up amount,
There is no need to prepare a plurality of torque pins and torque springs in advance. This eliminates the need for component management of the torque-up device as in the conventional example. In addition, metering hole 1
Opening 5 reduces the mass of the second lever 13B and eliminates the conventional torque-up device 20, so that the swing inertia of the governor lever 13 is reduced, and the response sensitivity can be increased.

(B) According to the second aspect of the present invention, in the centrifugal governor according to the first aspect, for example, as shown in FIG. 3, the metering hole 15 is formed at an intermediate portion of the second lever 13B. Since the first lever 13A is opened in the vicinity of the receiving portion 26 for receiving the contact piece 25, the maximum bending stress acts on the second lever 13B where the metering hole 15 is opened, and the bending amount due to the elastic deformation is also reduced. Since the number increases, the amount of torque increase can be easily adjusted. Further, the mass of the intermediate portion of the second lever 13B is reduced, and the swing inertia of the second lever 13B is correspondingly reduced, so that the response sensitivity can be increased.

[0011]

Embodiments of the present invention will be described below in more detail with reference to the drawings. FIG. 1 shows a centrifugal governor according to a first embodiment of the present invention, and FIG. 1 (A) is a schematic view of the centrifugal governor at a position corresponding to a full load.
FIG. 2B is a schematic diagram of the centrifugal governor at a position corresponding to a torque increase, and FIG. 2 is a graph showing the relationship between the rotational speed N of the engine and the positions of the torque pins corresponding to the fuel injection charge Q and the torque.

The centrifugal governor 10 has the same basic configuration as the conventional example. That is, as shown in FIGS. 1A and 1B, a governor lever 13 is formed by a first lever 13A and a second lever 13B pivotally supported by a swing support shaft 11, respectively.
The governor weight 37 is interlockedly connected to the input portion 16 of the first lever 13A, and the start spring 19 and the rack pin 39 which is a metering tool of the fuel injection pump 3 are interlockedly connected to the output portion 17, thereby forming the second lever 13A. Lever 13B
The governor spring 27 is connected to the governor spring 27, and the rack pin 39 is elastically pressed to the fuel increasing side R by the start spring 19 and the governor spring 27, whereas the governor weight G of the governor weight 37 causes the first.
The rack pin 39 is pressed to the fuel reduction side L via the lever 13A. The governor lever 13 is driven by an unbalanced force between the elastic force on the fuel increasing side R and the pressing force on the fuel decreasing side L.
Is rocked so that the rack pin 39 is adjusted and moved. The swing end 13 of the second lever 13B
b is received at the full load equivalent position 4/4 by the swing regulation pin 18.

Hereinafter, the characteristic configuration of the present invention will be described. In the present invention, the following torque increasing means 14 is employed in place of the conventional torque increasing device 20. The torque-up means 14, the second lever 13B as well as an elastic deformable member, said between rack attachment point P _S of the swing shaft 11 and the governor spring 27 of the second lever 13B (here The second lever 13 is disposed near the pivot shaft 11).
B is provided with a metering hole 15 for lowering the bending rigidity and metering the torque increase amount. Here, the elastically deformable member means a resilient bending member such as a sheet metal member.

The operation of the torque increasing means 14 will be described below. When the engine reaches the full load operation state A shown in FIG. 2, as shown in FIG.
The swing end 13b of 3B is received by the swing regulating pin 18, and the rack pin 39 is located at the full load equivalent position 4/4 via the first lever 13A. In this state, the governor force G
Bending moment _G · a = F G · b clockwise is applied to the receiving portion 26 of the second lever 13B, which is commensurate with counterclockwise bending moment S · c by the tension S of the governor spring 27 caused by. The second lever 13B constructed at an elastically deformable member in the metering hole 15 is elastically deformed to project to the right by the moment F _G · b by the governor force G.

When the engine shifts from the full load operation state A shown in FIG. 2 to the overload operation state, the rotation speed of the engine decreases, and accordingly, the governor force G decreases. Then, as shown in FIG. 1B, the clockwise bending moment Fg · b due to the reduced governor force g also decreases, whereas the counterclockwise bending moment S · c due to the tension S of the governor spring 27 decreases. Relatively large. For this reason, the second lever 13B is elastically deformed in a convex shape to the left. That is, when the engine shifts from the full load operation state A to the overload operation state, the second lever 13B is elastically deformed from a rightward convex state to a leftward convex state.
3A moves the rack pin 39 from the full load equivalent position 4/4 to the torque increase equivalent position Tu (torque increase operation state B shown in FIG. 2) as a limit. As a result, the fuel injection amount is increased, and the engine exhibits tenacity.

FIG. 3 is a diagram illustrating a method of adjusting the torque increase amount by incorporating the centrifugal governor 10 according to the present invention into a monitor device corresponding to an actual machine. Reference numeral 7 in this figure
Denotes a drive motor for rotating the governor shaft 4, and the one end 5 of the governor shaft 4 and the output shaft 6 of the drive motor 7 are linked and connected. Reference numeral 8 denotes a non-contact type distance sensor that detects a metering position of a rack (not shown) or a rack pin 39 as a metering tool of the fuel injection pump 3. Hereinafter, a method of adjusting the torque increase amount using this monitor device will be described.

First, the governor shaft 4 is rotated by the drive motor 7 at the rated engine speed (for example, 3600 rpm).
Next, the speed control lever 28 is pulled to set the tension S of the governor spring 27 to a predetermined value corresponding to the full load operation state.
In this state, the swing regulating pin 18 is adjusted forward and backward to receive the swing end 13b of the second lever 13B with the swing regulating pin 18, and the distance sensor 8 detects that the rack pin 39 is at the full load equivalent position 4/4. Probate by

Next, the rotation speed of the governor shaft 4 is reduced by the drive motor 7, and the rotation speed (for example, 1500 rpm) corresponding to the torque-up position Tu in the overload operation state of the engine.
Rotate in m). In this state, the distance sensor 8 reads whether or not the rack pin 39 is at the torque-up position Tu. When the position of the rack pin 39 is out of the allowable range and deviates to the fuel reduction side, the metering hole 15 is opened at a predetermined position of the second lever 13B to adjust the torque increase amount. When the metering hole 15 is opened in this way, the bending rigidity of the second lever 13B decreases, and the state of the elastic deformation changes. Therefore, the above adjustment is repeated again to meter the torque increase amount.

When the position of the rack pin 39 deviates from the allowable range to the fuel increasing side, it cannot be corrected. To avoid this, data on the position and size of the metering hole 15 is required. The first metering hole 15
Is set to fall within the allowable range in the second processing on the weight reduction side. According to the above configuration, it is not necessary to prepare a plurality of torque pins and torque springs before adjusting the torque increase amount. This eliminates the need for component management of the torque-up device as in the conventional example. Further, since the mass of the second lever 13B is reduced by opening the metering hole 15, and the conventional torque increasing device 20 is eliminated, the swing inertia of the governor lever 13 is reduced, and the response sensitivity can be increased.

Further, as shown in FIG. 3, the metering hole 15 is provided at an intermediate portion of the second lever 13B, and the contact piece 25 of the first lever 13A is provided.
When it is opened in the vicinity of the receiving portion 26 for receiving the maximum bending stress acts on the intermediate portion of the second lever 13B,
Since the amount of deflection due to elastic deformation also increases, it is easy to adjust the amount of torque increase. In addition, the mass of the intermediate portion of the second lever 13B having the metering hole 15 is reduced, and the swing inertia of the second lever 13B is reduced by that amount, so that the response sensitivity can be increased.

FIG. 4 is a diagram exemplifying a method of adjusting the torque-up amount by the dedicated torque-up metering machine 40. The torque-up metering machine 40 includes a base 41, a support column 43 provided on the base 41, and a swing support shaft 1 of the governor lever 13.
1, an arm 45 having a lever locking pin 44 provided on a column 43, a guide 46 of a lifting rod 47 and a locking bolt 48 of a governor spring 27, and fixed to the upper end of the lifting rod 47. Load 52
And a dial gauge 50 provided at the upper end of the support column 43. The load 52 (W ₁ ) corresponds to the full load operation state of the engine, and the torque increase position in the overload operation state. Load 52 (W equivalent to Tu)
₂ ) are individually loaded on the load mounting table 49, and the amount of torque increase is measured from the amount of change in the deflection of the second lever 13B. Hereinafter, this torque-up metering machine 4
A method of adjusting the torque increase amount using 0 will be described.

First, the governor spring 2 is fixed with the locking bolt 48.
7 is set to a predetermined value corresponding to the full load operation state. In this state, the lever locking pin 44 is adjusted forward and backward to
The swinging end 13b of the lever 13B is
Accept at 4. Next, a load 52 (W ₁ ) corresponding to the full load operation state of the engine is loaded on the load mounting table 49, and the amount of deflection of the second lever 13 </ b> B (imaginary line) at this time is read by the dial cage 50. The load 52 (W) corresponding to the torque-up position Tu in the overload operation state of the engine continues.
₂ ) is loaded on the load mounting table 49, and the amount of deflection of the second lever 13B (solid line) at this time is read by the dial cage 50. When the amount of change in the deflection of the second lever 13B is out of the allowable range and deviates toward the fuel reduction side, the metering hole 15 is opened at a predetermined position of the second lever 13B in the same manner as described above, and the torque increase amount is increased. Weigh. Also in this case, the component management of the torque-up device as in the conventional example is unnecessary, the swing inertia of the governor lever 13 is reduced, and the response sensitivity can be increased.

FIG. 5 is a schematic view of a centrifugal governor according to a second embodiment of the present invention. The present invention is not limited to a two-lever governor lever, and can be implemented with a three-lever governor lever with appropriate modifications. That is, as shown in FIG. 5, the centrifugal governor 10 has a third lever 13A between the first lever 13A and the second lever 13B.
1 is different from that of FIG. 1 in that a lever 13C is supported by the swing support shaft 11 and a torque-up regulating pin 19 is provided on the governor wall 2a so as to be able to advance and retreat. It is configured similarly to a centrifugal governor.

The reference numeral 25a in FIG.
The contact portion between 3C and the second lever 13B, reference numeral 25b is the first
The contact part of the lever 13A and the 3rd lever 13C is shown. According to this embodiment, when the change amount of the deflection of the second lever 13B is out of the allowable range and deviates to the fuel increasing side, the torque-up regulating pin 19 can regulate the torque-up amount.

[Brief description of the drawings]

FIG. 1 shows a centrifugal governor according to a first embodiment of the present invention. FIG. 1 (A) is a schematic diagram of a centrifugal governor at a full load equivalent position, and FIG. 1 (B) is a torque increase equivalent position. It is a schematic diagram of a centrifugal governor.

FIG. 2 is a graph showing a relationship between an engine rotation speed N and a position of a torque pin.

FIG. 3 is a diagram illustrating a method of adjusting a torque increase amount by incorporating a centrifugal governor into a monitor device corresponding to an actual machine.

FIG. 4 is a diagram illustrating a method of measuring a torque-up amount by a torque-up metering machine.

FIG. 5 is a schematic diagram of a centrifugal governor according to a second embodiment of the present invention.

FIG. 6 is a front view of a centrifugal governor according to a conventional example.

[Explanation of symbols]

Reference Signs List 10: centrifugal governor, 11: swing shaft, 13: governor lever, 13A: first lever, 13B: second lever, 13
b: swinging end of the second lever, 14: torque increasing means,
15: metering hole, 16: input part of first lever, 17: first
Output part of lever, 18: swing regulating pin, 19: start spring, 25: contact piece of first lever, 26: receiving part of second lever, 27: governor spring, 28: speed control lever, 39 ... Fuel injection pump metering tool (torque pin),
4/4 ... full load corresponding position, rack attachment point of P _S ... governor spring.

Claims (2)

[Claims] 1. A governor lever (13) comprising at least a first lever (13A) and a second lever (13B) pivotally supported by a pivot shaft (11), respectively, and the first lever (13) is provided. 13A), the governor weight (37) is linked to the input section (16) and the output section (1).
7) The start spring (19) and the metering device (39) of the fuel injection pump (3) are interlocked and connected, and the second lever (13B) is connected to the speed adjusting lever (28) via the governor spring (27). Then, the swing end (13b) of the second lever (13B) is received at the full load equivalent position (4/4) by the swing regulation pin (18), and the first lever (13A) and the second lever (13) are received. 13B), a centrifugal diesel engine configured to increase the fuel injection amount in conjunction with the transition from the full load operation state to the overload operation state of the diesel engine. In the governor, the torque increasing means (14) is provided with the second lever (1).
The 3B) as well as an elastic deformable member, said second lever between said second lever (swinging shaft (11 13B)) rack attachment point of the governor spring (27) and (P _S) (13B) A centrifugal governor for a diesel engine, wherein a metering hole (15) for adjusting a torque increase amount by lowering a bending rigidity is formed. 2. The centrifugal governor for a diesel engine according to claim 1, wherein the metering hole (15) is provided at an intermediate portion of the second lever (13B) and at a contact piece (25) of the first lever (13A). A centrifugal governor for a diesel engine, which is opened in the vicinity of a receiving portion (26) for receiving a).