DE1206657B - Fuel injection pump for multi-cylinder internal combustion engines - Google Patents

Description

FEDERAL REPUBLIC OF GERMANY

GERMAN

PATENT OFFICE

EDITORIAL

Int. α .:

F02f

German class: 46 c2-115 /02

Number: 1206 657

File number: S 730771 a / 46 c2

Filing date: March 20, 1961

Opening day: December 9, 1965

The invention relates to a fuel injection pump for multi-cylinder internal combustion engines with a fixed body and a distributor, which within the body by an equiaxed Shaft is set in rotation, which in turn is driven by the motor fed by the pump is driven, the pump also including at least one pump piston which is so arranged is that it is in a transverse bore which is in one of the through the stationary body and the drive shaft formed parts is displaced by a cam carried by the other part can be, wherein the fixed body is provided with distribution channels which lead to the injection nozzles lead and with carried by the distributor, with the mentioned bore in connection standing distribution passages cooperate, wherein the pump contains a control member, which of a controller responsive to the speed of the drive shaft is actuated, which controller for this shaft is coaxial and opens the outlet openings provided in the first of these parts periodically and closes.

In the patent 1152 848 it has already been suggested that this should not be used to transmit the forces of the ^ 5 Pump self-serving regulating element to be controlled by one and the same regulator so that it is below that Speed at which the controller begins to reduce the injection quantity when the speed increases, relative to the second of the mentioned parts is rotated so that the beginning of the injection is changed is, above this speed, however, is adjusted axially so that the delivery rate of the pump depends Working cycle is changed in accordance with the increase in their speed.

In the embodiment described in the cited patent based on this principle are the pump piston or the pump piston in a transverse bore carried by the stationary body arranged and operated by a cam attached to the drive shaft while the distributor and the control element are formed by one and the same rotary valve, which with is provided by inclined surfaces limited distribution and outlet grooves, the training is made so that the axial displacement of the slide in which the increase in Speed corresponding sense, the amplitude of the angular stroke is reduced, while the hole of the piston or the piston is not switched to exhaust.

The invention relates to a modified fuel injection pump for multi-cylinder
Internal combustion engines

Applicant:

Societe Industrielle Generale de Mecanique

Appliquee S.I.G.M.A., Paris

Representative:

Dipl.-Ing. E. F. Eitner, patent attorney,

Munich 5, Erhardtstr. 8th

Named as inventor:
Jean Rene Giraudon,
Rueil Malmaison (France)

Claimed priority:

France of March 30, 1960 (822 897)

management form of an injection pump operating according to the above principle of the earlier patent.

The pump, which has a control element designed according to the above principle, is according to the invention characterized in that the or the pump piston in a known manner in a Transverse bore are arranged, which is formed in an arrangement which extends through the drive shaft and the manifold is formed, the pistons being actuated by a stationary cam, and the control element is formed in a likewise known manner by a stationary ring, which cooperates with outlet openings provided on this arrangement.

Rotated in a known injection pump described in French patent specification 1 218 014 the controller forms a ring in such a way that initially the start of the injection is changed, whereupon this Ring takes a second ring with it, which is adjusted so that the delivery rate of the pump is changed in accordance with the increase in their speed. The pump pistons are on this device arranged in a transverse bore of the drive shaft. The known facility has the disadvantage that the change in the beginning of the injection inevitably continues when the delivery rate of the pump is reduced under the action of the regulator. With a decrease in the injected However, the amount of fuel is a change in the

509 757/110

3 4

at the beginning of the spraying it is useless and often even harmful. Outside spring 12 with rollers 13 held in contact that is with the known device one and the- which are on a stationary ring-shaped The same return spring for the device to roll cams 14 with inner elevations. This change the start of the injection and for the lifts are opposite each other so that the RoI device to change the delivery rate 5 len 13 are raised symmetrically and the piston is provided, whereby the course of the injection is also symmetrical alternating movements at the beginning connected with the course of the delivery rate. The shaft 2 has radial feed channels that will. This makes it impossible to provide the course of FIG To influence change in the start of injection, longitudinal channel 1 and, on the other hand, during the suction afterwards once the course of the change in the io strokes of the piston 11 with channels 16 in the walls Delivery rate has been determined. Furthermore, it is connected to the housing 17 of the pump, impossible to set lower and upper limits for the vessel. This housing serves as a fuel container determine the speed between which the connection and for this purpose a filler neck 18 can have, change of the start of injection takes place. These stand during the delivery strokes of the piston 11 According to the invention, disadvantages are thereby increased, of course, that the channels 15 do not coincide with the channels 16 in FIG sided that for the device to change the connection.

Start of injection and for the device to finally change the shaft 2 with a radial change Two different dividing channels 19 are provided for the conveying capacity, and the housing 17 is which are provided. Finally, the provided with channels 20, the number of which is equal to that of the known device is a constant maintenance of the form 20 leading to the injection nozzles nozzle 21 is what performance cannot be guaranteed with certainty when the training is made in such a way that the channel 19 what with the device according to the invention not with one of the channels 20 during the delivery strokes the case is. the piston 11 is in communication. F i g. 1 corresponds

The invention is described below with reference to the end of such a conveying stroke, i.e. H. to the

on the drawing on the basis of an embodiment example in which the connection between

game explained. channel 19 and one of channels 20 just below

F i g. 1 is a schematic axial section of a ruptured area and the channels 15 with the channels 16

injection pump according to the invention are connected in the position

its parts, which are below the control speed according to the invention is now on the control ring 6 with

Speeds correspond; 30 sliding fit a control ring 22 is placed, which axially

F i g. 2 is a cross section along the line II-II of the responding to the speed of the shaft 2 by a

F i g. 1 of the shaft and the control ring of the pump; the controller can be moved, whereby the win-

F i g. 3 is one of the F i g. 2 corresponding transverse position of the ring 6 by two between the

cut after the rotation of the shaft of the pump; Ring 6 and ring 22 or between ring 22

F i g. 4 and 5 show in plan the grooves of the 35 and housing 17 arranged sets of pins

Control ring or the actuation ring of the pump and grooves is determined, while its axial position

of Fig. 1; ment by two between the ring6 and the ring

F i g. 6 shows partly in side view and partly 22 or between the ring 6 and a part more firmly

in axial section certain parts of FIG. 1 arranged in the axial position opposite the shaft 2

regulation, which is determined at an intermediate control speed of 40 sets of springs,

to take. A centrifugal governor is expediently used as the controller

The pump is used on any suitable, which e.g. B. by a load on shaft 2

Way designed so that the fuel in a solid drive pulley 23 and one on this shaft

Channel 1 is conveyed, which is formed in a shaft 2 axially displaceable driven pulley 24,

is formed, which z. B. via a flange 3 with 45 wherein the two discs are approximately frustoconical

is driven at a speed which corresponds to that of the surfaces between which flyweights

Not shown motor 25 fed by the pump are arranged. These carry balls 26, with wel-

proportional and, in particular, this is the same, where they are supported on these surfaces, and will

this channel has outlet grooves 4 and 5, guided radially through the cutouts of a disk 27,

which open on the circumference of the shaft 2 and with 50. Depending on the increase in the speed of the

a ring 6 fixed, but adjustable position to- shaft 2, the disc 24 in Fig. 1 is opposite to the

cooperate, which always with a sliding fit on the shaft resistance of the two spring sets mentioned

is pushed open and continuous, shifted 90 ° more to the right.

has mutually offset holes 7, 8, 9 and 10, the disc 24 is on the control ring 22 by means

the number of which is equal to the number of cylinders in the engine. 55 of a ball bearing 28 or the like. Mounted, whereby the

As shown in FIG. 2 and 3, the groove 5 is counter-disk 24 successively on the rings 22 and 6

above the groove 4 in the indicated by an arrow and centered on the shaft 2.

Direction of rotation of shaft 2 offset by about 120 °. Of the two sets of springs, the first can go through

As can also be seen from Fig. 1, the groove 5 is formed in a single tongue 29, e.g. a helical spring.

one sense and the groove 4 in the opposite sense 60, which between two on the rings 6

inclined so that the shortest distance between the shoulders and 22 provided is arranged, while

Grooves 4 and 5 in successive cross sections of the second set of springs through at least one

th is formed by a spring 30 from left to right in FIG. 1, which is not between one

moving level decreases. illustrated shell with opposite the housing 17

To convey the fuel under pressure in the 65 fixed, but expediently adjustable position and one

Channel 1 are arranged in at least one radial bore disc 31, which opposite the

of shaft 2, e.g. B. in two such bores, such as the housing can perform a translational movement,

shown, piston 11 arranged, which by a pivotable on an axis 33 compensating

Lever 32 transmits the compressive force of the springs 30 to the face of the ring 6. The springs 30 can Incidentally, also surround the shaft 2, as shown in FIG. 1 shown at 30 a by attaching to one end support a shoulder of the shaft 2 without changing the operation of the assembly; the disadvantage however, such an arrangement makes the springs 30 difficult to adjust.

The springs 29 and 30 are given such parameters that the spring 29 yields before the springs 30, the rings 6 and 22 being expediently provided with shoulders 6 α and 22 α , which come into contact with one another before the spring 29 is completely compressed, The mutual displacements of the rings 6 and 22 in the other direction can be limited by a perforated disk 34.

The two sets of pins and grooves are carried on one side by one of the ring 22 Pin 35 and a provided on the circumference of the ring 6 groove 36 and on the other hand by one of the housing 17 carried pin 37 and a provided on the circumference of the ring 22 groove 38 is formed.

As in Fig. 4 and 5, the groove 38 can be parallel to the axis of the shaft 2 and the groove 36 too this lie at an angle. Finally, there is also the ring 22 with two mutually opposite grooves 39 and 40 provided.

The injection pump works as follows: During the delivery of the pump, the pistons are 11 pressed by the cam 14 inward. As long as the groove 4 and the hole 7 fit together Are connected, the pumped fuel passes through the hole 7 of the ring 6 and through the groove 39 of the ring 22. As soon as the groove 4 is covered by the wall of the ring 6 (FIG. 2), the can Fuel no longer escapes through the hole 7 and is through the channels 1, 19 and 20 of the Firing order of the engine supplied to the corresponding injector.

The injection lasts until the moment in which the hole 9 begins to expose the groove 5 (Fig. 3), since at this moment the fuel through the hole 9 of the ring 6 and the groove 40 of the Ring 22 begins to emerge.

While the pump is being sucked in, the pistons 11 are pressed outwards by the spring 12, and the channel 1 receives the fuel entering through the channels 15, 16 and optionally the hole 9 on.

The same work cycle is repeated with holes 8 and 10, then with holes 9 and 7 and finally with the holes 10 and 8. There are thus four injections per revolution of the shaft 2, which corresponds to the work cycle of a four-cylinder four-stroke engine.

The position of the grooves 4 and 5 is determined so that when the ring 6 is adjusted to the right Side of FIG. 1 the angle decreases by which the shaft 2 moves between the instant in which the groove 4 is completely closed (FIG. 2), and the moment in which the groove 5 begins to open (Fig. 3), rotates; this reduces the delivery rate per work cycle.

Furthermore, when the ring is twisted in the direction of rotation of the shaft or in the opposite direction The direction of the start of the injection is delayed or brought forward.

If the engine is running at a speed which is below a given limit value, the stops Spring 29 spreads the rings 6 and 22 apart, as in F i g. 1 shown, the ring 6 against the Compensating lever 32 pushes, which is pressed by the springs 30 against a stop. The ring 22 under the action of the spring 29 presses the disk 24 back and approaches the centrifugal weights 25 the axis of the shaft 2. The axial position and the angular position of the ring 6 with respect to the shaft are therefore unchangeable, and the delivery rate per work cycle as well as the time of the start of the injection are constant.

As soon as the speed of the engine exceeds the above limit value, the centrifugal weights 25 spread from the axis of the shaft 2, making the disc

24 and the ring 22 in FIG. 1 to be moved to the right, the ring 22 through the pin 37 and the Groove 38 is performed. Since the springs 30 are stronger than the spring 29, the latter is compressed, so that the ring 6 does not move axially. The axial movement of the ring 22 relative to the Ring 6 moves the pin 35 in the groove 36, whereby the ring 6 rotates around itself by an angle which depends on the inclination of the groove 36 (FIG. 5) and the size of the axial displacement of the ring 6 depends. The start of injection is therefore in accordance with the increase in the number of revolutions of the engine brought forward.

The ring 6 remains immobile in the axial direction until the shoulders 6 α and 22 α come into contact with one another (FIG. 6). If the speed continues to increase, the flyweights are used

25 developed centrifugal forces greater than the resistance the springs 30. The disc 24 then presses the arrangement formed by the rings 6 and 22 according to the right side of FIG. 1 and 6, whereby the pin 37 is relatively displaced in the groove 38. Since this latter is straight (Fig. 4), a translational movement of the ring 6 and thus a Reduction of the delivery rate of the pump per work cycle and thereby a limitation of the speed of the motor to the desired value.

The regularity of the regulation as a function of the speed can be determined by a corresponding Choice of the characteristic of the springs 30 and by adjusting the preload of these springs, which can take place during operation, as well as determined by an appropriate design of the groove 36 will. Furthermore, according to a variant embodiment, the groove 38 with respect to the axis of Shaft 2 are inclined on at least part of its length, while the groove 36 is formed so that they is parallel to this axis over at least part of its length. Furthermore, on one and the same groove 36 or 38 inclined sections are provided, which alternate in one or the other Direction are inclined, whereby the control options according to the motors used and the can be considerably enlarged by these machines to be driven. Finally, the controller can turn on of the shaft 2 on the one facing away from the drive flange 3 Side of the pumping and distribution assembly are attached.

The injection pump according to the invention has numerous advantages, in particular the following:

Thanks to the use of separate springs, which can be adjusted separately, are

the control function and the function of changing the start of injection separated from one another; There are numerous control options by changing the characteristics of the springs, their Preload, the possible stroke of the control ring compared to the control ring and the unwound Shape of the grooves that determine the movement of the control ring and the control ring;

the control device centered on the pump shaft ensures a small footprint;

the training is simple and relatively cheap;

the control device has only negligible inertia.

Claims (2)

Patent claims: 1. Fuel injection pump for multi-cylinder internal combustion engines with a fixed Body and a distributor, which within the body by an equiaxed shaft in Revolution is displaced, which in turn is driven by the motor fed by the pump wherein the pump also includes at least one pump piston which is so arranged is that it is in a transverse hole, soft in one of the through the fixed body and the Drive shaft formed parts is formed by one carried by the other part Cams can be moved, wherein the fixed body is provided with distribution channels, which lead to the injectors and carried by the manifold, with the one mentioned Bore communicating distribution passages cooperate with the pump contains a control element which is controlled by a controller responsive to the speed of the drive shaft is actuated, which is coaxial with this shaft and provided in the first of these parts Outlet openings periodically opens and closes, but not for the transmission of the Forces of the pump itself serving control element is controlled by one and the same controller so, that it is below the speed at which the controller controls the injection quantity when the speed increases begins to decrease, is rotated relative to the second of the mentioned parts so that the beginning of the injection changes is, above this speed, however, is adjusted axially so that the delivery rate of the Pump is changed per work cycle in accordance with the increase in its speed, thereby characterized in that the or each pump piston (11) in a known manner in a Transverse bore of the unit formed by the drive shaft and the distributor are arranged and are actuated by a stationary cam (14), the control element in a likewise known manner Way is formed by a stationary ring (6), which with the provided on this unit Outlet openings (4,5) cooperates. 2. Pump according to claim 1, characterized in that the control ring on the drive shaft (2) (6) is arranged with a sliding fit and that a control ring (22) with a sliding fit on the control ring is arranged, which is axially displaceable by the controller, the angular position of this Control ring by two between the control ring (6) and the control ring (22) or between the Sets of pins (35 and 37, respectively) and grooves arranged on the control ring and the housing of the pump (36 or 38) is determined, while its axial position is determined by two between the control ring (6) and the control ring (22) or between the control ring and a part which with respect to the shaft of the pump assumes a fixed axial position, arranged sets of springs (29, 30) is determined. Considered publications:
French Patent No. 1 218 014. Legacy Patents Considered:
German Patent No. 1152 848. 1 sheet of drawings 509 757/110 11.65 © Bundesdnickerei Berlin