JPS5838619B2 - Fuel injection pump device for internal combustion engine - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a fuel injection pump device for supplying fuel to an internal combustion engine.

The device is of the type that includes an injection pump having an axially movable control rod that determines the amount of fuel delivered by the injection pump during each injection stroke, and a governor device that controls the position of the control rod. .

The object of the invention is to provide a simple and convenient device of this kind.

According to the invention, the invention comprises an injection pump having an axially movable control rod for determining the amount of fuel delivered by the injection pump during each injection stroke, and a governor device, the governor device comprising a fixed pin. a swinging member attached around the swinging member; a first swing link having one end pivotally connected to the swinging member at a position away from the fixed pin; and a first swing link pivotally mounted to the end of the swinging member opposite to the one end. a slot formed in a second swing link, a block disposed within the slot, and an operator adjustable shaft for adjusting the position of the block within the slot; a speed responsive device having a governor weight connected to the control rod at an end opposite the pivot point with the member and responsive to engine speed, and for causing movement of the swinging member about the fixed pin; a servo device having a servo valve;
The servo valve has a valve member connected to the speed responsive device such that during normal operation of the governor system, the oscillating member is connected via the first link to the speed responsive device as the engine speed increases. Movement of the governor weight causes the fuel supply to the engine to decrease, and conversely, when the speed decreases, the fuel supply increases.
Further, in the event of a failure of the servo device, the first link is configured to engage the swinging member at the end opposite to its pivot position with the swinging member and directly transmit the action of the speed response device to the swinging member. A fuel injection pump device for supplying fuel to an internal combustion engine is provided.

The main feature of the invention is the servomechanism.

This servomechanism provides the force necessary to move the control rod of the injection pump.

Generally, the force required to move the control rods is generated by a centrifugal weight mechanism.

Therefore, this mechanism must be constructed so that it can generate sufficient force to move the control rods.

In order to increase the force produced by the weight mechanism, it is necessary to increase the mass of the individual weights.

This necessarily results in an increase in the size of the weight mechanism.

This is because the various members supporting the weight must be made large to provide the necessary support.

If a servomechanism is used to move the control rod, the weight mechanism can be made relatively small.

This is because the weight mechanism only needs to move the valve control member of the servomechanism.

Since the weight mechanism is small, the spring that resists the action of the weight mechanism can also be made correspondingly small.

Hereinafter, one embodiment of the present invention will be described based on the drawings.

First, the fuel injection pump device before improvement according to the present invention is
This will be explained with reference to Figure 4.

The device shown in FIGS. 1 and 2 has an end cap 11 fixed by bolts.
The pump housing 10 includes a pump housing 10 having a pump housing 10.

The end cap 11 together with the housing 10 constitutes a chamber 12 in which a governor mechanism is placed.

A rotating shaft 13 extending through the chamber and housing 10 includes cams for actuating individual injection pumps within the pump housing, which are shown collectively at 14 in FIG.

A shaft 13 extends through the end cap and is driven in timed relationship with the associated mechanism in use.

The amount of fuel supplied with each injection stroke is determined by the fuel control rod 15
The frame is axially movable within the housing 10 and projects into the chamber 12.

The shaft has a speed responsive device 16, which has a cup-shaped member 17 in which a plurality of governor weights 1 are arranged.
There are 8.

The weights pivot outwardly as the rotational speed of the shaft increases, imparting axial movement to the sleeve 19 during such outward movement.

Sleeve 19 then imparts axial movement to another sleeve 20 via roller thrust bearings 21 .

There is also a further sleeve 22 on the shaft, and interposed between the sleeves 20 and 22 is a coiled compression spring 23.

The amount of compression of the compression spring 23 is limited by the annular flange of the sleeve 22 hitting a step provided in the bore of the sleeve 20.

Sleeve 22 engages the curved end of main governor spring 24.

This is a bifurcated leaf spring, forming a loop around a fixed shaft 25 extending across the end cap 11 at its end remote from the sleeve 22.

The adjustment device 26 associated with the leaf spring also consists of an angularly movable plate having a pin 27 which engages the leaf spring midway between its ends.

The position of the plate is therefore such that the force exerted by the spring is
is determined by an adjustable stop 28 which can be operated from the outside.

The arrangement of the device is such that as the speed increases, the weights 18 move outwards, causing compression of the springs 23 first.

When the annular flange on sleeve 22 engages a step in sleeve 20, spring 24 is deflected.

The sleeve 20 has a circumferential groove 29 in which a first,
The slippers 30 are arranged as shown in FIG.

The slipper 30 is pivotally mounted on a first link 31, said link being pivotably mounted about an axis defined by a pin 32 fixed to the housing 10.

The other end of the link 31 is pivotally connected to one end of the second link 33.

A pair of legs of the link 33 form a slot 34;
Located within this slot is a slidable protrusion 35 supported by a pin 36.

Block 35 and pin 36 effectively form a pivot axis for second link 33.

One of the legs of link 33 extends upwardly and engages an abutment pin mounted on an extension of control rod 15.

This leg is urged into engagement with the abutment pin using a coiled tension spring 37.

The end of the spring remote from the leg extends around a pin supported by a plate 38 mounted on the control rod.

The second link 33 has a slot 34, as shown in FIG. 3, in which a block 35 attached to a pin 36 is placed.

The pin 36 moves within a slot 39 formed in the guide plate 40.

The pin 36 is attached to the arm 41 as shown in FIGS.

This arm 41 is pivotally connected to another arm 42.

Arm 42 is carried on a shaft 43 which extends outside the housing and is connected in use to a vehicle throttle pedal which is driven by an engine.

When arm 42 is moved in a clockwise direction, as seen in FIG. 2, about the axis of shaft 43, pin 36 moves downwardly, as seen in FIG.

During such downward movement, block 35 moves downwardly within slot 34, thereby imparting axial motion to control rod 15.

As mentioned above, the pin 36 is forced into the slot 39 formed in the guide plate 40.

The guide plate 40 is fixed to the housing 10 of the device.

In FIG. 3, pin 36 is at the closed end of slot 39, which represents the lowest required speed position.

As pin 36 is moved downward, second link 33
pivots around its pivot point with the first link 31, and the control rod is moved to the left.

Such movement increases the amount of fuel delivered to each injection stroke of the injection pump.

If, for example, pin 36 were to be midway between the ends of slot 39, link 31 would increase as the associated engine speed increases.
is moved in a counterclockwise direction as viewed in FIG. 3 via slipper 30 by the governor weight.

Such movement then moves the second link 33 clockwise about the axis formed by the pin 36.

This reduces the amount of fuel delivered with each injection stroke.

As shown in FIGS. 1 and 2, pin 36 is pivotally mounted within an arm 41, which arm 41 is pivotally mounted at the end of another arm 42. As shown in FIGS.

This arm 42 extends outside the housing and is pivotally connected to an angularly adjustable shaft 43 that is used to connect to an operator adjustable member, such as a throttle pedal on a vehicle driven by an engine.

In FIG. 2, clockwise movement of the shaft 43 and the arm 42 about the axis of the shaft 43 is achieved through the slot 39.
causing downward movement of pin 36 within.

In this manner, the effective pivot point of the second link 33 can be adjusted and the vehicle operator will experience virtually no reaction from the governor weight 18 and spring 24.

That is, the pin 36 serves as a pivot point for the second link 33.

While the pin 36 moves down within the slot 39, the third link 31
doesn't move.

Since the first link 31 is connected to the centrifugal mechanism via the slipper 30, no reaction occurs to the throttle pedal due to the action of the governor weight 18 and the spring 23.

The downward movement of pin 36 within slot 39 causes leftward movement of the control rod in FIG. 3, thus increasing the amount of fuel supplied to the associated engine.

Chamber 1 for torque control with respect to engine speed.
2 is equipped with a mechanism described below.

Referring to FIG. 1.2, there is now one slipper 44 which moves within the circumferential groove 29.

The slipper is pivotally mounted in a mount 45 which is pivoted about an axis 46 supported by the wall of the housing 10.

The mount 45 is connected to a link 48 via a coiled tension spring 47.
Connect to.

The other end of the link 48 is pivotally connected to the arm 49.

This arm 49 is then connected to arm 50.

The axis of angular movement of arms 49 and 50 is constituted by a pin 51 supported by a plate 52 whose angular position is adjustable.

The set position of plate 52 can be adjusted from outside the housing, and this plate is pivotally mounted on shaft 53.

A coiled torsion spring 54' is provided for retaining plate 52 in engagement with an adjustable stop.

Said tension spring 47 serves to transmit motion between the mount 45 and the link 48.

For example, if the link 48 becomes immobile due to the cam surface 54 on the arm 50 being held by the pin 55, the action of the weight mechanism is impaired.

In such a case, spring 47 serves to effect relative movement between link 48 and mount 45.

The end of the arm 50 on the side away from the pin 51 has a cam surface 54.
This cam surface has a pin 5 protruding laterally from the plate 38.
It can be multiplied by 5.

Pin 55 together with cam surface 54 constitutes a maximum fuel position stop, and the amount of movement of control rod 15 to the right in FIG. 2 is limited by the contact of cam surface 54 and pin 55.

In FIG. 2, cam surface 54 is not in position to capture pin 55.

Therefore, when the driver adjustable shaft 43 is moved angularly,
Control rod 15 is moved to a position where excess fuel is available for starting.

As soon as the engine is started, the governor weight 18 moves outwardly displacing the sleeve 20 against the action of the relatively light spring 23.

This movement is transmitted via link 48, causing arm 54 to pivot in a counterclockwise direction in FIG.

However, at the same time, the control rod is connected to the slipper 30 and the second link 38.
As a result, the pin 55 passes through the arm 54 without touching it.

This pin is thus enabled to cooperate with the cam surface 54 as a stop for the maximum fuel position of the device.

The contour of the cam surface 54 is configured to provide a maximum fuel that varies as engine speed changes.

A device (not shown) is provided for adjusting the relative position of link 48 and mount 45.

As shown in FIG. 1, the arm 49 is connected to a pin 51 which is rotatably mounted in a bushing carried by an arm 52 which is now carried by one bushing and which Another bushing is rotatable about a shaft 53 and is loaded by a leaf spring 54' such that the plate 52 engages the adjustable stop shown in FIG.

The shaft 53 can be rotated from outside the housing using a lever 56.

The shaft has a stop plate 57 which is connected to the plate 38.
It is movable into position to engage the upper protrusion and is adapted to move the control rod to a minimum or zero fuel position.

During this movement, tension spring 37 is stressed, allowing relative movement of second link 33 and control rod 15.

In the configuration described above, the force required to move control rod 15 is within the range of the force provided by weight 18.

In some versions of the device the forces required are much greater.

It is not always practical to modify the structure of the governor weight so that it provides greater force.

The reason for this is that it becomes necessary to change various springs as well.

To eliminate this difficulty, a servo device is provided.

The force required to move a control rod depends on the number of pumps connected to the control rod.

At some point during the cyclic action process, the control rod becomes very difficult to move.

The cause lies in the various forces generated in the individual pumps.

For example, if the pump system were to supply fuel to an eight-cylinder engine, it would have eight individual injection pumps whose control members would be connected to the control rods.

Each pump operates only once per rotation of its drive shaft, but in an eight-cylinder pump there are eight periods during which the control rods are difficult to move during rotation of the drive shaft.

Additionally, in some pumps, a fluid pressure reaction is applied to the control rod.

Therefore, it is desirable to move the control rods by means of a governor mechanism in order to obtain a regulating effect on the amount of fuel delivered by the system as quickly as possible.

Although the dimensions of the weight mechanism can be increased to ensure adequate force, this is not necessarily desirable.

The improved device according to the present invention will be explained below.

The slipper 30 shown in FIG. 6 is supported by a pin 60 attached to a first link 61.

The first link 61 is pivoted about a pin 62 which is supported by a rocker member 63.

The swinging member 63 is equivalent to the first link 31 and is connected to the second link 33.

The swinging member 63 is mounted on a bearing supported by a pin 64 fixed to the housing, and the pins 60 and 62 are arranged in diametrically opposed positions with respect to the axis of the pin 64.

Furthermore, the extension of the pin 60 is inserted into the hole 65 formed in the swinging member 63 with a gap.

In operation, movement of the sleeve 20 and hence the slipper 30 causes the first link 61 to pivot about the pin 62 until the gap between the pin 60 and the wall of the hole 65 is closed, and then the movement of the rocker member 63 Rotation occurs.

It functions to prevent the engine from speeding too high in the event that the servo system described below is damaged.

The servo arrangement consists of a pair of pistons 66, 67, which are housed in respective cylinders in special end caps for the housing.

The axes of movement of the pistons are substantially parallel and spaced from one another, and the pistons engage the rocker member 63 on either side of its pivot axis, as shown in FIG.

A servo valve, indicated at 68, controls the action of the piston.

Piston 66 has a larger diameter than piston 67.

The servo valve 68 has a valve member 6 that is slidable with the sleeve 70.
9, the valve member 69 is connected to the first link 6 by a link 71.
Connect to 1.

The cylinder containing the piston 67 is in constant communication with a source of fluid, preferably a source of fuel 72, at a substantially constant pressure.

Valve member 69 has a central land 73 which, in the equilibrium position of the servo valve, closes off a boat formed in sleeve 70 and connecting with the cylinder containing piston 66.

A groove on one side of the land, on the left side in FIG. 7, communicates with a central hole provided in the valve member, which opens into the chamber at one end.

The groove on the other side of the land portion 73 communicates with the cylinder containing the piston 67 by a boat formed in the sleeve 70.

In operation, the piston 67 applies a substantially constant force from the fuel source to the rocker member 63, and in the servo valve equilibrium position, where the land covers a given boat, the piston 66 is inserted. Hydraulic lock occurs in the cylinder.

As a result, no movement of the swinging member 63 occurs.

If the valve member 69 moves to the left (FIG. 7), the piston 66
Since the cylinder containing the pressurized fuel is supplied with pressurized fuel and the piston 66 has a large area, the force generated by the pressurized fuel moves the rocker member counterclockwise.

Conversely, if the valve member moves to the right, fuel can exit the cylinder containing the piston 66 and the rocker member 6
3 moves in a clockwise direction (Figure 5).

Movement of valve member 70 is controlled by slipper 30.

If this slipper is moved by sleeve 20, lever 61 pivots about pin 62 and moves link 71 in one direction or the other.

Of course, this moves the swinging member 63 in an appropriate direction,
Pin 62 is moved about the axis of pin 64.

The second link 61 then pivots about the axis of the pin 60 and the valve member 70 returns to its equilibrium position.

The pin 60 shown in FIG. 6 is smaller than the hole 65 in the rocker member 63, and the pin 60 does not engage the wall of the hole 65 during normal operation, that is, when the servo system is operating properly.

If the servo device fails, this pin 60 is moved by the weight mechanism and engages the wall of the bore 65, so that the rocker member 63 is moved as described above, minimizing the risk of overspeeding the engine. It turns out.

If the pin 60 is not in the bore 65 and the engine overspeeds, the first link 61 will rotate about the pin 62 but will not transmit any movement to the rocker member 63.

When the servo device operates correctly, the first link 61
The movement is transmitted to the swinging member 63 via the servo device.

That is, the overspeed prevention function of the engine is such that the pin 60 is connected to the hole 6 as described above.
This is guaranteed by being within 5.

[Brief explanation of the drawing]

Fig. 1 is a vertical sectional view of the device before improvement, Fig. 2 is a sectional view taken in the direction of arrow A in Fig. 1, and Fig. 3 is a partially removed view taken in the direction of arrow B in Fig. 1. The cross-sectional view shown in Fig. 4 is the 3rd
Figures 5 and 6.7 are views similar to Figure 3 showing only a part of the apparatus shown in the figure, and Figures 5 and 6.7 are views showing embodiments of the apparatus of the present invention. 10... Housing, 11... End cover,
12... Chamber, 13... Rotating shaft, 14... Cam, 15... Control rod, 16... Speed response device, 18 ...Governor weight, 19,20,22...Sleeve, 23...Compression spring, 24...Main governor spring, 26... Adjustment device, 28...
・Stop, 29... Circumferential groove, 30...
Slipper-31...First link, 33...
...Second link, 35...Block, 39...
... Slot, 40 ... Information board, 41.4
2...Arm, 43...Driver adjustable shaft, 44...Slipper-150...
...Arm, 54...Cam surface, 61...
...First link, 63... Swinging member, 66°6
7... Piston, 68... Servo valve,
69... Valve member, 70... Sleeve,
73... Central land part.

Claims (1)

[Claims] 1 comprises an injection pump with an axially movable control rod 15 for determining the amount of fuel delivered by the injection pump on each injection stroke, and a governor device, the governor device being arranged around a fixed pin 64. The attached swing member 63, a first swing link 61 having one end pivotally connected to the swing member 63 at a position away from the fixed pin, and a first swing link 61 pivotally connected to the end of the swing member opposite to the one end. a slot 34 formed in the second pivot link 33, a block 35 disposed within the slot, and an operator adjustable shaft 43 for adjusting the position of the block within the slot;
the second link 33 is connected to the control rod at an end opposite to the pivot point with the rocking member, and a speed response device 16 having a governor weight 18 responsive to engine speed;
a servo device 66,67 having a servo valve 68 for causing movement of the rocking member about the fixed pin 64, the servo valve 68 having a valve member 69, which valve member is responsive to the velocity response. The swinging member 6 is connected to the device through the first link 61 during normal operation of the governor device.
3, when the engine speed increases and the governor weight moves, the fuel supply to the engine decreases, and conversely, when the speed decreases, the fuel supply increases. Further, in the event of a failure of the servo device, the first link engages the swinging member at an end opposite to its pivot position with the swinging member, and directly transmits the action of the speed response device to the swinging member. A fuel injection pump device for supplying fuel to an internal combustion engine, characterized by: