JPS63272959A - Fuel injection pump for reciprocating diesel engine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application The present invention relates to a fuel injection pump for a double-acting diesel engine, the pump extending at an inclination to the longitudinal axis of the plunger X7. Cooperative with the cylinder orifice [1] to determine the start and end of the discharge by the plunger
at least two plungers 17 having lands formed on their generating surfaces and capable of reciprocating vertically within the cylinder;
The plunger is equipped with a device which is attached to the outside of the cylinder and capable of reciprocating linearly with the plunger, and which rotates the plunger around its longitudinal axis.

In the known injection pumps of class 11 (according to the prior art), the swiveling charge can act to change the amount of fuel injected into the working cylinder of the engine depending on the negative/+1 of the engine. The pivoting changes the position of the land inclined with respect to the orifice of the cylinder so that the end of the plunger I is changed from 1j11 and/or t.

Due to the nature of the construction of the pump, the pivoting range of the plunge AI is limited to approximately 60°. Therefore, the sloped land is
The fI11 plane of the plunger extends over a range of 60°. Therefore, the land is relatively steep in view of the evolution of the generating surface of the example. The steep slope is caused by the fuel overflow caused by IIQ 04, l! If '5 affects the reproducibility of the discharge stroke of the plunger and therefore the injected 61
deviates significantly from the position of control 21I+. Such deviations or fluctuations are caused, for example, by the sum of the 4J errors in the transmission path from the controller to the runner that act on the control controller (gap tolerances, incorrect assembly, etc.). The variation in the stroke of the plunge rod 7 is proportionately greater as the land is steeper; another disadvantage of steeper lands is that a full opening of the overflow orifice of the cylinder is required for the corresponding land. Plunge puller 7
associated with the end of the injection phase by the stroke of . This means that the injection, instead of terminating rapidly, lingers, impairing the combustion of the fuel. 2, the above-mentioned type of injection Q (pump is used only for the constant start of injection).
T I) making it physically impossible to advance the start of injection before C).

SUMMARY OF THE INVENTION The object of the invention is to improve an injection pump of the above-mentioned type in such a way that the disadvantages caused by the steepness of the lands are eliminated. .

According to the invention, the device SEL, control rod and 1
an adjusting sleeve disposed between the plunger 17 and extending eccentrically around the plunger 1 and having internal teeth on the right side of the plunger A7; pivotably coupled to.

The eccentric arrangement of the adjusting sleeve with internal teeth and the placement of the mating external teeth on plunger A7 allow the sleeve to pivot to an even larger pivot of plunge V, approximately twice the normal plunger pivot range, approximately 120°. Convert.

This increase in 1 lunge V7 turning range fills all
This is achieved by a linear stroke of the rod, which stroke remains the same size as in the jet pumps of the type already mentioned.

Due to the increasing range of swivel of the plunger, the inclined land may extend over a greater proportion, corresponding to the generating surface of the plunge ψ, and therefore, when viewed in a developed view,
Land's slope is much gentler than Moe's. Therefore, the disadvantages mentioned in connection with the steep lands of known pumps are:
significantly reduced.

Therefore, the stroke O of the plunge V due to the error in the transmission path
- fluctuations are significantly less and the injection phase ends more rapidly because the plunger stroke required for the corresponding plunger A7 to completely open the overflow orifice is smaller.

The new pump also allows the start of delivery to be modified, ie the start of injection to be advanced before the TDC of ignition.

Embodiments of the invention are described in detail in Section F with reference to the accompanying drawings. .

DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring to FIG. 1, the cylinder 2 of the pump is provided within the cable lung 1 of the pump and is fixed within the casing 1 by a cover 3. The plunger 4 is guided in vertical reciprocating motion within the cylinder 2 and is formed with a land 5 on its generating surface near its upper end, the land 5 being at an angle relative to the 1417] adaxial axis of the plunger 7. Extends at a slope. The land 5 cooperates in a known manner C with two radial bores (not shown in FIG. 1) in the cylinder wall of the pump so as to define the beginning and end of the projection of the plunger.

Fuel for injection is supplied to an annular chamber 6 between the casing 1 and the cylinder 2 via a feed line (not shown in Figure 1) and then from the chamber 6 to the pump via a bore defining the beginning of the discharge. Go to discharge chamber 7. Plunger 4
The fuel M to be injected during the discharge stroke passes through the center bore 8 of the cover 3 and is injected into the cylinder head of the engine.
Go to the 8th vessel (not shown).

The plunger 4 does not protrude from the cylinder 2 and has a flange 9 at its lower end.
It engages the tappet 10 which is guided in a direction-interlocking manner.

'The F-V knob 11 is connected to the flange 9 and the tappet 10.
The F end of the compression spring 12 engages around some of the
The button 7 comes into contact with the button 11. The upper end of the spring 12 abuts a spring cup 13 fixed within the casing 1 . The compression spring 12 ensures that the seven flange 9 permanently engages the tappet 10. The roller 14 is rotatably mounted at its lower end on the tappet 10 and shifts over the cam 15 of the camshaft which drives the plunger 4 in the rhythm of the engine.

A sleeve 16 is formed at and extends around the lower end of the cylinder 2, projects beyond the cylinder of the pump, and has two diametrically opposed sleeves each engaged by a radial arm 17 of the plunger 74. It has an axial slot. The axial length of the slot is at least as long as the plunger 4
is equal to the maximum stroke of Therefore, a simultaneous rotating connection is provided between the plunger 4 and the sleeve 16,
The sleeve 16 rotatably slides on the cylinder 2.

In the area above the slot, the sleeve 16 has external teeth 18 which mesh with the inner #19 of the adjustment sleeve 20, which is arranged eccentrically on the sleeve 16 and thus on the pusher 4. The adjustment sleeve 20 is attached to the pivot 2 which can be seen in FIG.
mounted inside the casing 1 so as to rotate around the casing 1,
It has radially outwardly extending lugs 22 on its outer periphery. A companion pin 23 extending downwardly in FIG.
It will be extended within 4 days. Therefore, the rod 25 with only quasi-S shown in FIG.
The movement of sleeve 20 through an angle of approximately 60° as shown by the dashed lines of member 24 and pin 23 in FIG.
It acts via the member 24 and the pin 23 so as to pivot. In the position shown in upper dashed lines in FIG. 2, the lateral limit surface 22' of the lug 22, visible in FIG. 3, engages in the stop screw 26 of the pump casing 1. The screw 26 is
It is adjustable by means of an adjusting nut 27.

A similar stop screw and adjustment nut arrangement is on the opposite side of the pivot area of the sleeve 20 and on the limit surface 22 of the lug.
The dimension of the stroke S and thus the limit of the pivoting range of the lug 22 is limited by the fact that there must be no further weakening of the casing 1 in the mentioned area.The internal toothing 19 and the external toothing 18 The pivoting of the sleeve 20 is caused by the rotation of the sleeve 16 and therefore of the plunger 4.
It is converted into an accommodative movement. The limits of the pivoting movement of the sleeve 16 depend on the eccentricity it 1 between the longitudinal axis of the plunger 17 and the axis 21 of the sleeve 20, which can be seen in FIG. Sleeve 16, i.e. approximately 120° of plunge V4
The maximum turning range of is given.

As seen in FIG. 1, the jull pump has its lower half engaging an engine casing 30 that mounts a camshaft. In order that the injection pump can be easily disassembled and reassembled, the outer limit of the lug 22 is within the diameter of the upper bore 31 of the engine casing that houses the casing 1 of the pump. JB is important for pumps. One injector per working cylinder of the engine is Md in the engine casing in the manner described above, and the associated cams corresponding to the force l\15 are on a common camshaft. The control rod 25 is common to all working cylinders and has a forked element 24 for each injection pump. The 11% of the fuel yp+ to be injected into the working cylinder can be made equal to each other by adjusting the fuel 24 and the screw 26 relative to the control rod.

As a variant of the above-described embodiment, the sleeve 16 may be omitted and the external teeth are provided directly on the 1-lunge puller 4. In this case, the external teeth remain in engagement with the internal teeth 19 of the adjusting sleeve 20 during the vertical reciprocating movement of the plunger.
It must have an axial length that increases in a certain way.

[Brief explanation of the drawing]

Figure 1 is a longitudinal sectional view of the fuel injection pump installed in the engine casing, Figure 2 is a sectional view taken along lines A-13 and CD in Figure 1, and Figure 3 is a cross-sectional view of the fuel injection pump near the teeth. A cross-sectional view of the part is shown. DESCRIPTION OF SYMBOLS 1... Casing, 2... Cylinder, 4... Plunger, 5... Land, 10... Tappet, 16...
... Sleeve, 18... External teeth, 19... Internal teeth, 20
...adjustment sleeve, 22...lug, 22', 22"
... limit surface, 23 ... companion pin, 24 ... member with fork, 25 ... control rod, 26 ... stop screw, 30 ... engine casing.

Claims (6)

[Claims] (1) comprising at least one plunger vertically reciprocatable within a cylinder and having a land formed on its generating surface, the land extending at an inclination to the longitudinal axis of the plunger; a linearly reciprocatable control rod mounted on the outside of the cylinder and cooperating with the plunger, the control rod cooperating with the orifice of the cylinder to determine the beginning and end of discharge by the plunger; A reciprocating diesel engine fuel injection pump comprising a device for pivoting the plunger about its longitudinal axis, the device having an adjusting sleeve, the sleeve being disposed between the control rod and the plunger. extending eccentrically around the plunger and having internal teeth;
A pump characterized in that the tooth engages an external tooth of the plunger and is pivotally connected to the control rod. (2) A pump according to claim 1, comprising a pump casing, the casing extending by its lower end around a tappet that houses the cylinder and transmits the vertical reciprocating motion of the plunger. extending and housed in an engine casing housing a camshaft drive, the connection between the sleeve and the control rod being within the contour of the pump casing housed by the engine casing. A pump characterized in that: (3) In the pump according to claim 2, the sleeve has a lug on the outside thereof, and the lug is
Pump, characterized in that, in order to limit the pivoting range of the adjusting sleeve, its two lateral end faces cooperate with an abutment of the pump casing. (4) The pump according to claim 3, wherein the abutting portion of the pump casing is adjustable. 5. A pump according to claim 3, wherein the companion pin extends into a forked member fixed to the lug and adjustably fixed to the control rod. (6) Any one of claims 1 to 5
3. The pump according to claim 1, wherein the plunger is coupled to an axially stationary coupling sleeve, the coupling sleeve being rotatably mounted on the cylinder and having the external teeth on the outside thereof. pump.