JPS6143265A - Fuel jet pump of internal combustion 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 the Invention The present invention relates to a fuel injection pump for an internal combustion engine. the distributor is provided with a control edge extending obliquely to the axial direction on the outer peripheral surface of the distributor, the amount of fuel is defined by adjustment of the axial position of the distributor, and the amount of fuel is guided for each injection process by a respective fuel injection conduit leading from said bore to an injection point of the internal combustion engine via a distributor opening, and
A coupling is provided which connects the distributor to a rotating drive shaft, the drive shaft having an oblique guide via which a driving ring is connected to the drive shaft, the driving ring being connected to the driving shaft. rotates with the drive shaft and extends in the axial direction for distributor transmission, allowing for axial phase N difference (both 1 and 1).
two entraining surfaces are provided on the entraining ring or coupling piece;
The invention also relates to a type in which an adjusting device is provided for adjusting the axial position of the entraining ring.

Prior Art A known fuel injection pump of this type is disclosed in West German Patent Application No. 3.
010839, in which the coupling piece passes through two diametrically opposed slits in the wall of the axial bore of the drive shaft.
It is engaged in a guide groove parallel to the axis of a driving ring that is capable of S movement on the outer circumferential surface of the drive shaft. The entrainment ring is provided with an outer flange, into which a roller provided at the end of the adjusting lever engages. The adjusting lever is actuated by an adjusting magnet to define the axial position of the driver ring, which is movable against the force of a return spring carried on the drive shaft.

PROBLEM TO BE SOLVED BY THE INVENTION The disadvantage of this arrangement is that the drive of the distributor takes place via a driver ring which is connected to the drive shaft only by means of a pin on the circumference of the drive shaft.

The pin engages in a groove formed diagonally in the flank of the axial bore of the entrainment ring. In that place there are two more for the fitting.
Two longitudinal grooves are provided in which the ends of the coupling pieces connected to the distributor engage. In short, because of the groove, the entraining ring must be made relatively thick, and the drive shaft must be provided with a relatively wide longitudinal slit for the passage of the coupling piece.

The width of this longitudinal slit must be such that adjustment of the rotational position of the coupling piece relative to the drive shaft and thus of the distributor is guaranteed. By this measure the strength of the drive shaft is significantly weakened. Moreover, in order to accurately and synchronously drive the cam track connected to the end of the drive shaft to operate the radially located pump pistons, it is necessary to avoid torsional and rotational vibrations of the drive shaft. This type of rotational vibration is easily caused by periodic circumferential impact loads on the cam trunk, so the drive shaft must be made to be resistant to torsion.

Increasing the diameter of the drive shaft to increase torsional strength,
Increasing the thickness of the entraining ring increases the required space and increases the moving mass.

Means of the Invention for Solving the Problems The gist of the invention for solving the above-mentioned problems is that the entraining ring is inserted into an axial hole of the drive shaft, and the entrainment ring is inserted into the axial hole of the drive shaft, and Adjustable movement by means of a driving member passing radially through at least one through hole serving as a diagonal guide, which driving member is guided on the cylindrical outer circumferential surface of the drive shaft and actuated by an adjusting device. It is connected to a ring.

Advantageous embodiments of the invention are described in the dependent claims.

Particularly advantageous configurations result when the configuration according to patent claim 9 is combined with the configurations according to patent claims 10 and 11.

With this configuration, it is possible to easily integrate the adjustment device into the pump casing in a compact manner, without the need to significantly change the dimensions of the pumps 7 to 777.The adjustment ring is constructed as a plunger that prevents rotation. In this way, a low-play adjustment of the axial position of the adjusting ring or a low-play adjustment of the rotational position of the distributor with respect to the drive shaft is achieved.The adjusting ring or the plunger guided on the drive shaft When the injection pump is in operation, it is always in sliding contact with the drive shaft, and since the pump interior is filled with fuel, it is lubricated by liquid.

The advantageous embodiment according to claim 8 is valid in the above sense even if the adjusting ring is operated in a different manner and is not designed as a plunger.

Because the diameter of the drive shaft increases significantly towards the cam trunk, it does not require significant radial space (
, an electrical annular adjustment magnet can be provided.

According to the embodiments according to claim 12 and M2S, a precise and desired position of the adjusting ring corresponding to the excitation current flowing through the electromagnet is achieved.

With the arrangement according to claim 14, a low-loss guidance of the magnetic flux, and therefore a high efficiency, is obtained with a small structure and a low current strength. Claim 17
According to the configuration described in paragraph 1, the basic adjustment of the adjusting ring depending on the strength of the excitation current of the electromagnet during operation of the fuel injection pump can be determined by adjusting the preload of the return spring. There is no need to open one fuel injection pump for that. This is because the adjusting tool can be inserted into the axially stepped hole.

DESCRIPTION OF THE PREFERRED EMBODIMENTS In FIG. 1, which shows a first embodiment of the invention, only the functionally important parts of a fuel injection pump are shown schematically. A distributor 3 is mounted in a bore 2 in the housing part 1 of the distributor injection pump of radial piston design.
is rotated once by the drive shaft ε via the joint 4. The distributor 3 has an annular ring 1117 on its outer circumference, which is always connected to a pump piston guide hole 8 extending radially from the bore 2.

A bonnobiston 10 is arranged in the bonnobiston guide hole 8, and the pump piston 10 closes off a C1 working chamber 11 from the side of the annular groove 7 with its end face. Coaxially with respect to the pump piston 10,
A roller tappet 14 is guided in a hole 12 having a diameter 0.degree. C. larger than the diameter of the pump piston guide hole 8,
This row 2 tappet 14 rests via its roller 15 on a cam track 16, which radially surrounds the housing part 1 at this point. The cam track 16 is connected to the drive @6 or to the reed or part thereof and rotates synchronously with the drive shaft or distributor 3. In this case, the pump piston 10 reciprocates via the row 215 and the roller tappet 14 and follows the cam track.

The pump piston 10 then alternately performs a discharge stroke and a suction stroke. The roller is kept in constant contact with the cam track 16 by a spring 11 between the casing part 1 and the roller tappet 14.

The Ml control groove 20 and the second control groove 21 are branched from the concession 87. extending apart from each other in a glyph. The second control groove 21 is formed relatively long and is connected to an axis-parallel portion 22 , which opens into a rectangular control surface 23 .

In the area of the control surface, in a radial plane containing the axis of the distributor 3, injection conduits 25 branch off from the bore 2 in such a way that they are distributed around the circumference of the distributor 30. The number of injection lines corresponds to the number of combustion chambers of the associated internal combustion engine. Corresponding to this number, the pump piston 10 also performs discharge and suction every revolution.

In the working range of the relatively short first control groove, a plurality of control ports 26 are provided in the radial plane at the sides of the bore 2, which control ports 26 are connected via conduits 27 to the fuel tank 28. It is connected to the.

This fuel tank is supplied with fuel in a known manner by a fuel pump, not shown, and this fuel is kept at a relatively low pressure level in the fuel tank 28. The control ports 26 are likewise distributed around the circumference in accordance with the number of injection conduits and have a trapezoidal cross section. As a result, opening and closing are controlled by the first control groove 20 or the second control groove 21 extending at the same angle at the same angle as the side surface of the opening. In the second radial plane, in the area of the axis-parallel portion 22, filling passages FNr 30 open on the circumference of the bore 2, the number and distribution of which are similar to the control openings 26, so that The inlet cross section of the filling channel 30 is closed at the latest simultaneously with the closing of the control port 26 in each case. This charge goes through lol
530 is similarly connected to the fuel tank 28.

The end of the distributor 3 protruding from the bore 2 is loaded by an adjusting device 32 for adjusting the axial position of the distributor. This adjustment device 32 is shown schematically in FIG. 1 as an adjustment magnet 32. Mover 33 of this adjustment magnet
adjusts the distributor 3 against the force of the return spring 35 acting on the other end of the distributor. This return spring 35 is supported in a blind hole 36 provided in the drive @6. An end 31 of the distributor protrudes from the bore 2 on the drive shaft side into this blind bore. This end 37 is connected via a pin 39 to a coupling piece which is approximately ring-shaped and has two guide strips 41 on its outer circumference. Piece 41 has a surface parallel to the axis. This guide strip 41 engages in a corresponding guide slot 42 of a driver ring 44, which can carry out a rotational movement and which can move the end 31 of the distributor 3 and the coupling piece 40. It is mounted in an axial bore 36 in a manner that it can be surrounded. The drive ring 44 as well as the coupling piece 40 essentially have a drive surface 45 that extends in the axial direction or is parallel to the axis. The driver ring 44 is provided with an axial through hole 46 through which the return spring is supported at the bottom of the bore 36 without interfering with the function of the driver ring.

A through hole 48 is provided in the wall of the axial hole 36 in an area that overlaps with the entraining ring 44 .
Reference numeral 8 is formed as a diagonal guide, and has the shape of a long hole extending in a spiral manner obliquely with respect to the axis. Within this range, the adjustment ring 5 on the cylindrical outer peripheral surface of the drive shaft is
A compression spring 52 is arranged between this adjusting ring 50 and a radially enlarged portion 57 guided into the cam track 16 of the drive shaft. The axial movement of the adjusting ring 50 is limited by the axial length of the through-hole 48, in that the driver 53, which passes through the through-hole 48, is inserted radially into the adjusting ring. This entrainment element 53 is designed in the form of a pin which engages in the entrainment ring 44 . As shown in Figure M2, this pin is removable.
In effect, this pin is connected to an elastic lip 54 which grips the adjusting ring from the outside and holds the pin 53 in its inserted position in the adjusting ring and in the driver ring. The end of the clip 54 is then bent and engaged in the cutout of the adjustment ring 50 in the radial direction.

The adjusting ring 50, which is connected to the drive shaft 6 by means of a driver element 53, has a concession groove 55 on its outer periphery, in which the end 58 of the adjustment lever 57 engages.

The side walls of this yielding groove 55 form an axially oriented annular enclosure into which the end of the adjusting lever 57 engages against the force of the compression spring 52. The end 58 of the adjusting lever 57 can also be of spherical design and have a latching roller. The end portion 58 of the adjustment lever 57 may be formed into a fork shape and grip the collar of the adjustment ring 50.

The adjustment lever 57 is rotatable around a shaft 59, and has an adjustment magnet 62 at the other end 60 of the adjustment lever 57.
An armature 61 is engaged, the adjusting magnet serving as an adjusting device for adjusting the axial position of the driver ring. This adjusting magnet 62, like the adjusting magnet 32, is controlled by an electronic control device 63 depending on the operating parameters. The armature 61 is movable between two adjustable stops 64 , 65 , which also define the pivot angle of the adjusting lever 57 . This allows the starting and final position of the adjusting ring 50 to be adjusted.

The fuel injection pump described so far is described in detail in West German Patent Application No. 3400612 and West German Patent Application No. 3010839 in connection with the configuration of the control groove 20.21 and the injection amount adjustment carried out thereby. It is constructed similarly to the injection pump described in . The second control groove 21 which advances depending on the axial position of the distributor 3 at the control port 2
6, the control port 26 that reduces the load on the pump working chamber is opened early (or late) by the first control s20 that moves backward.

This staggered opening of the control ports 26 results in differences in the CIJ injected fuel quantities, which are injected at different axial positions of the distributor. For quick filling, a filling passage 30 is provided which fills the second control groove 21 before the second control groove 21 connects to one of the control ports 26.
1 is opened by an axis-parallel portion 22 .

At the same time, filling also takes place via the first control groove 20 and the control port 26 located overlappingly therewith. This makes it possible to fill the pump work chamber particularly quickly. After the 29th control groove 21 and its axially parallel portion 22 have passed through the control port 26 or the filling passage 30, injection is effected by the pump piston, which is moved inward by the cam ring. The fuel pumped by the pump piston reaches one of the injection conduits 25 via the yielding groove 7, the second control groove 21 and the square control surface 23, which injection conduit 25 is currently under control. It is open by a surface 23.

FIG. 4 shows the cam lift of the cam track 16 in degrees Celsius corresponding to the rotation angle α. The slope on the left side of FIG. 4 produces the discharge stroke or pump stroke of the piston pump. Two sections A and A' are shown on this left slope. These divisions A, A' represent the times of fuel injection at different axial positions of the distributor. Section A represents the injection amount when the distributor 3 moves significantly toward the drive shaft 6, and section A' represents the injection amount when the distributor 3 moves to a position significantly farther away from the drive shaft 6. ing. Corresponding to the symmetrical inclination of the first control groove 20 with respect to the second control groove 21, the injection start and end times for section A and section A' are also symmetrical with respect to one another. In short, the drive shaft 6
With the same relative position of the distributor to , the start of injection in section A with a large injection quantity is initiated at a relatively early crank angle, and on the other hand the injection start in section A with a small injection quantity
′, injection is started at a slow crank angle. The same applies to the end of injection. This relationship can be changed by changing the inclinations of the control grooves 2o and 21.

The coupling 4 makes it possible to change the rotational position of the distributor relative to the drive shaft. While the adjustment ring 50 maintains a predetermined axial position, no rotation of the distributor 3 relative to the drive shaft 6 occurs. Regardless of the position of the distributor 3, the adjusting ring 50 can be moved axially via the adjusting lever 57. The driver element 53 then follows the extension of the through hole 48 and rotates the driver ring 44 relative to the drive shaft 6 . At the same time, the entraining ring 44 entrains the coupling piece 40 with its axis-parallel entraining surface 45 and rotates the distributor 3 by the same amount. This adjustment moves the °C injection timing in relation to the cam lift. In relation to the axial position of the adjusting ring 50, section A' is located between the upper solid line position and/or the lower broken line position. The electronic control unit 63 can adjust the predetermined injection start timing independently of the injection amount, injection pressure, rotational speed, fuel temperature and fuel viscosity, or can adjust the cam to obtain various injection rates. Different degrees of inclination of the lift head can be used for the injection.The control outlay is then significantly lower and the adjustment can be carried out in different ways.The adjustable stop 64,65 allows the adjustment device The control range is limited and the starting position can also be defined by an adjustable stop 64.The coupling piece 40 allows a very play-free following of the distributor when selecting the connection and also allows the drive shaft to The adjustment is made very precisely in order not to weaken the strength of the signal.

The embodiment shown in FIG. 5 is constructed substantially the same as the embodiment shown in FIG. 1 with respect to the distributor and pump piston drive. Regarding these parts, reference is therefore made to the embodiment shown in FIG. In the embodiment shown in FIG. 5, an adjustment device is provided for adjusting the relative position of the distributor with respect to the drive shaft. Similarly to the embodiment shown in FIG.
6 is fitted and inserted.

This entraining ring 66 is likewise provided with a coupling piece 40,
This coupling piece 40 can be moved with its guide strip 41 into an axis-parallel guide slot 42 of a forest-shaped entraining ring 66 . The entraining ring 66 has a closed bottom;
A return spring 68 is supported on this bottom, which is supported on the other side by a spring receiver 69.

The spring support 69 rests on the end of a pin 71 which is press-fitted into the bore 70, which is designed as an axial bore 360 of reduced diameter which is designed as a stepped bore. Similarly, a mounting hole 72 continues from this hole 70, and this mounting hole 72 opens coaxially with the hole 70 into an outer end surface 73 of the drive shaft 6'.

The guide slot 42 of the entraining ring 660 adjoins the groove 14, which groove 14 has a spherical groove base 15. A pin 11 is inserted into this groove 74, and this pin 7
1 has the function of the entraining member 530 in the embodiment shown in FIG. The pins 11 are diametrically opposed and located at 2°C.
The through holes 78 are formed as oblique guides corresponding to each other and have the shape of a spiral elongated hole inclined at the same angle with respect to the axis of the drive shaft. . The end portion 79 of the pin 11 that projects outward from the through hole 18 is formed in a step shape, and a tip ring 80 is engaged with the step portion 16, and this tip ring 80 is engaged with the step portion 16. Prevents movement in the axial direction. In short, the hinge ring 80 is adapted to and inserted into the outer periphery of the drive shaft. The ring 80 and the stepped portion 16 of the pin 11 are
It is provided on the opposite side to the return spring 68. The indexing ring 80 cooperates with an adjusting ring 81, which is movable in the area of the axial bore 36 along the outer circumference of the cylindrical part 82 of the drive shaft 6'. The end face of the adjustment ring 81 facing the adjustment ring 80 is designed as a support surface for the adjustment ring 80, so that the drive shaft together with the pin 17 can rotate unhindered relative to the adjustment ring 81. can. FIG. 5 Pressurized Water j Instead of special construction, the adjusting ring 81 is designed as a plunger, which has an inner part 83 that slides on a cylindrical part 82 and an outer cylindrical part 84. The inner part 83 and the outer part 84 are connected to each other via a prong 85.

The adjustment ring 81, which is also formed as a plunger, is formed as a component of an electromagnet 9, which has an annular coil 86.
Coil 86 is supported by core 87. core 8
1 is outside the coil. It includes an outer cylinder 88 surrounding the coil and a yoke 89 which covers one end face of the coil and is magnetically coupled to the outer cylinder and has a central hole 90. The central hole allows the yoke to connect the cylindrical portion 82 of the drive shaft 6' to the VC
A C-shaped air gap is formed. The magnetic flux generated by the excitation of the coil 86 is transmitted to the shaft at this point. The other end of the outer cylinder 88 is open and projects axially beyond the coil 86 so that a plunger serving as an adjusting ring can be retracted in this area.

The coil 86 is seated in a support 91, and the support 91 has a gap 92 between itself and the drive shaft 6'. is free to move at its end 79 and, upon excitation of the electromagnet, a part of the cylindrical inner part 83 of the adjusting ring 81 is retracted for adjustment of the hinge 17.

The support 91 is held inside the core by a cover ring 94 and is thus fixed to the pump casing by screws 95 at the end projecting from the outer cylinder of the core. The cover ring 94 allows passage of the cylindrical inner part 83 of the adjusting ring 81 and is provided with a guide pin 96 extending axially parallel to the open end of the outer cylinder 88. ℃ and at that location engages in a suitable guide hole 91 provided in the annular gusset 85 of the adjusting ring 81, thereby preventing rotation of the adjusting ring 81 even if the drive shaft 6' rotates. be done.

The coil 86 is connected to an electronic control device 63 via a connecting portion and a conductor (not shown in FIG. 5), and this electronic control device 63 controls the current flowing through the coil as in the embodiment shown in FIG. The position of the adjustment ring 81 is determined by the adjustment ring 81, and the adjustment ring 81 is operated by the return spring 6 under the action of its repellent magnetic force.
8 and moves the entraining ring 66. Due to the spherical design of the groove bottom, no catching forces act on the adjusting ring or the driving ring, so that the behavior of the adjusting ring 81 as a hinge support is maintained. As the excitation current increases, the mover 81 is drawn deeper into the outer cylinder 88 of the core. The magnetic flux flows through the outer cylinder 88, the yoke 89, the cylindrical portion 82 of the drive shaft 6', and reaches the mover 81. In order to correspond to the injected excitation current and to adapt the adjustment of the armature 81, the wall thickness of the outer cylinder 88 can be varied within the overlapping range with the cylindrical outer part of the armature 81, which different magnetic flux densities can be obtained or, for the same excitation current, different adjustment factors can be produced. The advantage of this configuration is that the adjustment ring 81 is fixed in a rotational position, which allows the adjustment ring 81 to be
It is loaded only by the sliding friction, so that there is no hysteretic transition from static friction to sliding friction when introducing the adjustment movement. Moreover, the adjusting ring 81 is surrounded by fuel, so that there is sufficient lubricating medium to reduce the side-to-side friction. The prestress of the return spring 68 can advantageously be varied during installation by means of a tool 98 inserted into the bore 12, so that a predetermined change of the excitation current and the axial position of the adjusting ring 81 or of the drive member 66 Correspondence can be obtained. For that reason. The pin 71 can be moved axially in one direction or the other.

Instead of preventing rotation of the adjusting litz 810 by the guide pin 96, in the embodiment shown in FIG. 6, the outer cylinder 88'
has a vertical slit 99 extending from its open side as a starting point, and the vertical slits 99 extend parallel to each other's axes. This makes it possible to prevent the adjustment ring 810 from rotating. Cylindrical outer portion 84 of the grand gloss 81'
A vertical groove 100 is formed inside facing the vertical slit, and this vertical groove 100 has the same width as the vertical slit 99. In this configuration, during excitation. Plunger 81
' is secured in the illustrated overlapping position with the longitudinal slit 99 of the outer cylinder 88'. The advantage of this measure is that friction occurring on the pin 96 against the adjustment of the syringe 81 is avoided. In that case the outer cylinder 88'
It is only necessary to provide the longitudinal slits 99 and the longitudinal grooves 100 only in the partial region of the plunger 81' or in the partial region of the plunger 81'.

Effects of the present invention According to the present invention, the reduction in the effective cross section of the drive shaft is extremely small (at most, only a narrow guide groove is reduced. Furthermore, since the drive shaft does not require a shaft pin, the outer periphery can be effectively The joint can be compactly accommodated in the axial hole of the drive shaft.In doing so, the lever arm of the connection between the joint piece and the entraining ring located inside is significantly reduced. This makes the entire system more torsionally resistant.

[Brief explanation of drawings]

FIG. 1 is a vertical cross-sectional view of the first embodiment of the present invention, and FIG.
A cross-sectional view taken along the line ■-■ in the figure, Figure 3 is lll of Figure 1.
4 is a diagram showing the lift height and injection timing of the cam track in relation to the crank angle in °C. FIG. 5 is a longitudinal sectional view of the second embodiment of the present invention, and FIG. The figure is a partial view of the adjustment ring rotation prevention means of the second embodiment.

Claims (1)

[Claims] 1. A fuel injection pump for an internal combustion engine, comprising a distributor (3) arranged in a hole (2) of a casing and an adjustment device (32) for adjusting the axial position of this distributor. , the distributor is provided with control edges (20, 21) extending obliquely to the axial direction on its outer circumferential surface, the amount of fuel is defined by adjustment of the axial position of the distributor, and the amount of fuel is controlled by adjusting the axial position of the distributor. is guided for each injection process by a respective fuel injection conduit (25) leading from said bore (2) to the injection point of the internal combustion engine via the distributor opening, and the distributor ( 3) and a rotating drive shaft (6), the drive shaft (6) has an oblique guide via which the entraining ring (44) is connected to the drive shaft. The entraining ring rotates together with the drive shaft to generate a coupling piece (40) which is connected to the distributor (2) and projects into the axial bore (36) of the drive shaft (6).
), and for the transmission of forces in the rotational direction, at least one entraining surface (45) extending in the axial direction and allowing a relative axial movement is provided on the entraining ring or the coupling piece. and is provided with an adjusting device (62, 57, 50, 53) for adjusting the axial position of the entraining ring (44), the entraining ring (44)
inserted into the axial bore (36) of the drive shaft (6) and passing radially through at least one through-hole (48) serving as said diagonal guide provided in the wall of said axial bore; The movement can be adjusted by a driving member (53),
This entrainment element (53) is connected to an adjusting ring (50) guided on the cylindrical outer circumferential surface (49) of the drive shaft (6) and actuated by an adjusting device (62, 57). A fuel injection pump for an internal combustion engine featuring: 2. 2. Fuel injection pump according to claim 1, wherein the entraining member (53) consists of a pin. 3. 2. Fuel injection pump according to claim 1, wherein the adjusting ring (50) has an axially oriented annular surface, in which the adjusting lever (57) engages. 4. The adjustment lever (57) is an electromagnet (62).
7. A fuel injection pump according to claim 6, wherein the electromagnet is controlled by an electronic control device (63) for adjusting the injection timing. 5. Claim 2: The driver element (53) consisting of a pin passes through two through holes (48) arranged diametrically opposite each other in the wall of the axial hole (36). fuel injection pump. 6. The entraining member (53) is mounted in a recess (74) of the entraining ring (66), which allows pivoting about an axis perpendicular to the distributor axis, and the entraining member and the entraining ring are connected to each other. 6. The fuel injection pump according to claim 5, wherein the contact surface therebetween is formed into a spherical shape in the direction of rotation. 7. Claim 5: The driving element is provided with a step (76) at its outer end (79) for connection with the adjusting ring (81) and for axial fixation of the driving element. Or the fuel injection pump according to item 6. 8. A sliding ring (80) guided on the drive shaft engages in the step (76), and this sliding ring is arranged between the driving member and the end face of the adjusting ring (81) which is prevented from rotating. The fuel injection pump according to claim 7, which is disposed in the fuel injection pump. 9. The adjustment ring (81) is an electromagnet (86).
, 88, 89), the fuel injection pump according to any one of claims 5 to 8. 10. An electromagnet is provided to serve the actuation of the adjusting ring, the electromagnet having a coil (86) fixed to the casing, which coil encircles the rotating drive shaft (6'). 10. The fuel injection pump as claimed in claim 9, wherein the adjusting ring is encircling and is designed as a plunger. 11. 11. The fuel injection pump according to claim 10, wherein the movable element is prevented from rotating. 12. The core of the electromagnet supporting the coil (86) is provided with an outer cylinder (88) which extends axially beyond the coil and whose inner periphery is connected to the outer periphery of the plunger (81). 12. The fuel injection pump according to claim 10 or 11, wherein a working air gap is formed between the fuel injection pumps. 13. 13. Fuel injection pump according to claim 12, characterized in that in the working region of the part of the outer cylinder (88) which receives the plunger (81), its outer surface is provided with a profile for changing the magnetic flux cross-section. 14. The coil (6) has an outer cylinder (88
) is magnetically coupled to the drive shaft (6'
), the yoke forms a magnetic flux to the drive shaft (6'), and the coil (6) is retained by a cover ring (74);
This cover ring (94) is arranged between the drive shaft (6') and the drive shaft (6').
13. Fuel injection pump according to claim 12, forming a cylindrical inner part (83) and an annular gap (92) for passage of the plunger. 15. At least one axial guide pin (96) fixed to the casing is provided, which guide pin projects into a suitable guide hole (97) of the plunger (81') to prevent rotation. A fuel injection pump according to any one of claims 12 to 14. 16. Cylindrical inner portion (83) of plunger (81)
16. Fuel injection pump according to claim 15, wherein the cylindrical outer part (84) is connected to the cylindrical outer part (84) via an annular web (85) provided with a guide hole (97). 17. In order to prevent rotation of mutually adjacent parts of the movable element (81) of the electromagnet and the outer cylinder (88) of the core, they each have the same width in the circumferential direction and are located at least partially opposite to each other. Notch (99,100
) are provided in claims 12 to 14.
The fuel injection pump according to any one of the preceding paragraphs. 18. A return spring (68) is attached to the entrainment ring (66) at one end.
The hole in the axial direction of the drive shaft is formed as a compression spring supported by a stepped hole (
36, 70), and a pin (11) is provided with a spring receiver in this step hole to support the other end of the return spring.
is inserted, the insertion depth of which can be varied by a tool guided through the step hole from the drive shaft side for adjusting the preload of the compression spring.
16. The fuel injection pump according to any one of items 1 to 16.