EP1477666A1 - Supply pump, in particular high pressure fuel pump for internal combustion engines - Google Patents

Abstract

The pump (16) includes a pump housing (28), and an electromagnetic actuator mechanism (24) integrated into the pump housing and operable to adjust the fluid quantity supplied by the pump. A magnetic circuit (91) of the actuator mechanism is closed by at least a region of the pump housing.

Description

State of the art

The invention relates to a feed pump, in particular High-pressure fuel pump for an internal combustion engine, with a pump housing and an electromagnetic Actuation device, with the help of which of the Delivery pump funded amount of fluid can be adjusted.

Such a feed pump is known from DE 199 38 504 A1 known. This is a single-cylinder high-pressure pump for high pressure supply in common rail injection systems of internal combustion engines. With the help of a electromagnetic actuator may be Inlet valve of the feed pump even during a Conveyor stroke of a piston of the feed pump forcibly be kept open. For this purpose, a valve element of Inlet valve of a plunger of the actuator applied. The actuator itself is in encapsulated in a separate housing.

The object of the present invention is a delivery pump of the type mentioned in such a way that they produced cheaper and with her even at high Speeds of the pump, the pumped amount of fluid can be adjusted precisely.

This object is in a feed pump the above mentioned type solved by the Actuator integrated into the pump housing so is that a magnetic circuit of the actuator at least through a region of the pump housing is closed.

Advantages of the invention

A first advantage of the feed pump according to the invention is that it can be produced inexpensively, as for the production of the actuator comparatively low material usage is required. The reason for this is the fact that according to the invention a Part of the magnetic flux, which for the electromagnetic Actuation of the actuator must be generated, not in the actuator itself, but in the actuator Housing of the feed pump is performed. This still has a second advantage: The feed pump according to the invention builds smaller and can therefore be easier for example in an internal combustion engine are installed.

Furthermore, with the inventive Actuator comparatively short switching times will be realized. By this one understands that time, with the actuator of a switch position in another switch position can be actuated. short Switching times are, for example, in internal combustion engines advantageous, which may have high speeds: Da the usual delivery pumps directly from the internal combustion engine are driven, stand at such high speeds only short periods for switching the Eetätigungseinrichtung to disposal. Particularly problematic are the Internal combustion engines with turbocharger possible high Speeds. These must have speeds up to 9000 Revolutions per minute can be expected. At a High-pressure pump with a so-called triple cam, so three strokes per revolution, resulting in a period at these speeds of 4.6 ms. With the present Invention, it is possible, even within such a short Safe period period.

The short switching times arise because of the strong integration of the actuator in the Feed pump only comparatively small distances between the generation of electromagnetic force and the Attack location must be bridged, which is a lesser Inertia of the parts used for this result, which in turn, in turn, high accelerations and in the Result causes short switching times. By inclusion the delivery pump housing to close the magnetic circuit Beyond that, a comparatively lossless Guiding the magnetic flux allows, what the efficiency the actuator and thus ultimately the Switching times favorably influenced.

Advantageous developments of the invention are in Subclaims specified.

In a first development it is proposed that the Actuating a bracket element from a comprises magnetic material which is arranged and connected to the pump housing so that it is for Conclusion of the magnetic circuit at least contributes. This Training is inexpensive and easy to manufacture.

It is also proposed that the actuating device on the pump housing facing side of a Magnetic anchor a connection element for connection to the pump housing and on the pump housing opposite side of the armature an armature counter element having, wherein the connecting element and the Anchor counter element via a sleeve member of a non-magnetic or dielectric material connected to each other. In this way, the Magnetic anchor optimally integrated in the magnetic circuit.

In this regard, it is proposed that the Connecting element with the sleeve element, and the Sleeve member welded to the armature counter-element, and all three elements at least part of a pre-assembled hydraulic assembly are. By the welding is good fluid tightness and pre-assembly overall facilitates the assembly of the invention Feed pump.

In a further development for this purpose, it is proposed that the connecting element with the pump housing is welded. This also makes a good Fluid tightness of the system achieved. For positioning is It is advantageous if the elements each first be joined together with a press connection. It is also advantageous if the Connecting element is positioned so that a certain opening stroke of the intake valve is set, which results when the actuator at the stop is applied.

Another embodiment provides that the Anchor counter element at least indirectly a stop for forms an actuating element of the actuating device and connected to the dielectric sleeve to size, such that thereby the one end position of the Berätigungselements is set. A precise Setting an end position of the actuating element creates reproducible conditions and increases precision the adjustment of the flow rate of the feed pump. By the possibly existing double function of Armature counter element, namely on the one hand line of Magnetic flux and on the other hand limitation of the movement path the actuator, material is also saved, which reduces the costs and reduces the size.

When the actuator turns off a solenoid Brass, the temperature influence on the Switching time of the actuator can be minimized. This is related to the fact that the specific resistance of brass depends less on the temperature than for example, that of copper.

Also advantageous is that training the according to the invention, in which the Actuator a separate electrical assembly having. As a result, the production of the feed pump once again simplified, because the electrical assembly in advance can be put together.

In this regard, it is proposed that the electrical assembly by a bracket element on Pump housing is held. This ironing element can if necessary, be that which has been mentioned in the beginning was and which serves for the conclusion of the magnetic circuit. By such a stirrup element is at low Material use and ease of production a safe Securing the electrical assembly guaranteed.

It is particularly advantageous if the electrical Assembly in installation position by a biasing element is biased. As a result, manufacturing tolerances balanced, which lowers the production costs.

Another particularly advantageous embodiment of according to the invention is characterized that an actuator of the actuator to a valve element of the feed pump attacks in one place, which is off-center with respect to the valve element. As a result, the for an actuation of the valve element force to be applied by the actuator reduced. When actuated by the Actuator raises the valve element due of the off-center attack in an imbalance, in which It is not only the actuator of the Actuator, but also for example a housing-side area supported. Share this the holding forces on the one hand on this housing side Range and on the other on the actuator on. Thus, the actuator can be made smaller which ultimately results in shorter switching times Has.

In that case, that the actuating element, if the Electromagnetic actuator is de-energized, the Valve element by spring force in an open position presses, this can be provided a smaller spring, which the size of the actuator again reduced. In addition, upon actuation of the Actuator smaller spring forces are overcome, which also benefits the switching times.

A realization of such an off-center Attack point may be that the longitudinal axis of Actuator against a plane of the Valve element is at an angle not equal to 90 °. Alternatively or additionally, it is possible that the Longitudinal axis of the actuating element relative to the center of the Valve element is arranged offset. Both are easy to realize.

It is also proposed that two to the two Front sides of a magnet armature adjacent spaces over a Fluid connection are interconnected. This creates a pressure relief of these rooms, which also faster Switching times enabled.

In this case, the fluid connection at least one preferably spiral groove in the lateral surface of the magnet armature include. With such a spiral groove is the Symmetry of the armature not or at least not significantly influenced.

Similarly, it is suggested that the Pump housing and the magnet armature facing sides of the Connecting element via a fluid connection with each other are connected. This can be done for example by a Plural axial holes in the connecting element done.

A further embodiment of the invention Feed pump provides that the actuating device a having first stop element on which the of a Inlet valve of the pump facing away from the end of a Actuator of the actuator in his Movement comes into contact, and that by means of a Spot welding is attached. This again increases the Precision in the positioning of the end position of the Actuator, as for the stop element Material selected with correspondingly optimal properties can be. To absorb impact forces is a easy to apply spot welding for fixation sufficient.

The actuating device can also be a second Include stop element, which in a guide of a Actuating element of the actuator integrated is and the stroke of the actuator to a Inlet valve of the delivery pump limited. Thus, without Significant additional effort also this final position of the Actuator can be adjusted precisely.

drawing

The following are particularly preferred Embodiments of the present invention below With reference to the accompanying drawings explained in more detail.

Figur 1

eine schematische Darstellung von Komponenten einer Brennkraftmaschine mit einer Förderpumpe und einer Betätigungseinrichtung;

Figur 2

einen Teilschnitt durch ein erstes Ausführungsbeispiel der Förderpumpe und der Betätigungseinrichtung von Figur 1;

Figur 3

einen Teilschnitt durch eine hydraulische Baugruppe der Betätigungseinrichtung von Figur 2;

Figur 4

einen Schnitt durch eine elektrische Baugruppe der Betätigungseinrichtung von Figur 2;

Figur 5

eine perspektivische Darstellung eines Magnetankers der hydraulischen Baugruppe von Figur 3;

Figur 6

eine perspektivische Darstellung eines Verbindungselements der hydraulischen Baugruppe von Figur 3;

Figur 7

eine Darstellung ähnlich Figur 2 eines abgewandelten Ausführungsbeispiels;

Figur 8

eine Darstellung ähnlich Figur 2 eines nochmals abgewandelten Ausführungsbeispiels;

Figur 9

eine Darstellung ähnlich Figur 2 einer nochmals anderen Ausführungsform;

Figur 10

einen Teilschnitt durch eine hydraulische Baugruppe der Betätigungseinrichtung von Figur 9;

Figur 11

einen Schnitt durch eine elektrische Baugruppe der Betätigungseinrichtung von Figur 9;

Figur 12

eine perspektivische Darstellung eines Magnetankers der hydraulischen Baugruppe von Figur 10;

Figur 13

eine perspektivische Darstellung eines Verbindungselements der hydraulischen Baugruppe von Figur 10;

Figur 14

einen Teilschnitt durch einen Teil der Baugruppe von Figur 10 zur Erläuterung des Zusammenbaus;

Figur 15

eine Darstellung ähnlich Figur 9 eines abgewandelten Ausführungsbeispiels; und

Figur 16

eine Darstellung ähnlich Figur 9 eines nochmals abgewandelten Ausführungsbeispiels.

In the drawing show:

FIG. 1

a schematic representation of components of an internal combustion engine with a feed pump and an actuator;

FIG. 2

a partial section through a first embodiment of the feed pump and the actuator of Figure 1;

FIG. 3

a partial section through a hydraulic assembly of the actuator of Figure 2;

FIG. 4

a section through an electrical assembly of the actuator of Figure 2;

FIG. 5

a perspective view of a magnet armature of the hydraulic assembly of Figure 3;

FIG. 6

a perspective view of a connecting element of the hydraulic assembly of Figure 3;

FIG. 7

a representation similar to Figure 2 of a modified embodiment;

FIG. 8

a representation similar to Figure 2 of a further modified embodiment;

FIG. 9

a representation similar to Figure 2 of yet another embodiment;

FIG. 10

a partial section through a hydraulic assembly of the actuator of Figure 9;

FIG. 11

a section through an electrical assembly of the actuator of Figure 9;

FIG. 12

a perspective view of a magnet armature of the hydraulic assembly of Figure 10;

FIG. 13

a perspective view of a connecting element of the hydraulic assembly of Figure 10;

FIG. 14

a partial section through part of the assembly of Figure 10 to explain the assembly;

FIG. 15

a representation similar to Figure 9 of a modified embodiment; and

FIG. 16

a representation similar to Figure 9 of a further modified embodiment.

Description of the embodiments

In Figure 1, an internal combustion engine carries the total Reference numeral 10. It comprises a prefeed pump 12, which the fuel from a container 14 to a Promotes high pressure pump 16 out. This compresses the Fuel to a very high pressure and promotes it too a fuel manifold 18 in which the fuel stored under high pressure. To the fuel manifold 18 are multiple fuel injectors 20 connected to the fuel inject combustion chambers 22 assigned directly to them.

The high-pressure pump 16 is not on in Figure 1 shown way directly from a camshaft of the Internal combustion engine 10 driven. It is, as will be explained below, to a single-cylinder piston pump. For adjusting the flow rate of High pressure pump 16 is an electromagnetic to this Actuator 24 mounted, which of a Control and regulating device 26 is controlled.

In the present case, particularly relevant components now explained with reference to Figures 2 to 6:

The high pressure pump 16 includes a pump housing 28 in which a delivery piston 30 is reciprocably received. The delivery piston 30 defines a delivery chamber 32, in the the fuel in a suction stroke of the delivery piston 30 via an inlet 34 and an inlet valve 36 passes. On Outlet channel 38 does not lead from the delivery chamber 32 to a illustrated exhaust valve and on to the fuel manifold 18. The inlet valve 36 is a spring-loaded check valve with a valve spring 40, a disc-shaped valve element 42 and a annular valve seat 44. The actuator 24 is in the embodiment shown in Figure 2 coaxial with a central axis 46 of the valve element 42 arranged. It comprises a hydraulic assembly 48 (See Figure 3) and an electrical assembly 50th (See Figure 4).

The hydraulic assembly 48 comprises a tubular Connecting element 52 (see Figure 6), on the in Installation position facing away from the inlet valve 36 end Sleeve member 54 is pushed in a press fit. In a Longitudinal bore 56 of the connecting element 52 is on the in Installation position the inlet valve 36 facing the end Guide ring 58 received in a press fit, in which a plunger-like actuator 60 is guided. The Actuator 60 extends over the two ends of the connecting element 52 addition. On his from Inlet valve 36 remote end portion is a cylindrical magnet armature 62 (see FIG. 5) pushed on and also fastened in a press fit. On the outer circumferential surface of the magnet armature 62 is, as shown in FIG 5, a spiral groove 63 is present, which from an end face of the armature 62 to opposite end leads. Between the Magnetic armature 62 and the guide ring 58 is a compression spring 64 braced.

The end remote from the connecting element 52 of the Sleeve member 54 is defined by a lid portion 66 locked. A disk-shaped stop member 68 is in Sleeve member 54 in close proximity to the lid portion 66th added. The actuator 60 is available with his from Inlet valve 36 projecting end slightly above the armature 62 out. Therefore, in the in Figs. 2 and 3 shown rest position the actuator 60 of the Pressed spring 64 against the stop member 68. in the Connecting element 52 are in its longitudinal direction extending holes 70 are present, which are the two End sides (without reference numeral) of the connecting element 52nd fluidly interconnect.

The electrical assembly 50 (FIG. 4) comprises a Coil carrier 72 and a magnetic coil 74. The winding of the Magnetic coil 74 is made of brass. Coil carrier 72 and magnetic coil 74 are molded with plastic 76. The Integration of the electromagnetic actuator 24 in the high pressure pump 16 is as follows:

First, the hydraulic assembly 48 is pre-assembled. For this purpose, the magnet armature 62 with the actuating element 60 joined, which then into the longitudinal bore 56 of the Connecting element 52 is introduced. Then the Compression spring 64 is pushed onto the actuator 60 and Finally, the guide ring 58 in the longitudinal bore 56th brought in. By an appropriate positioning of the Guide ring 58 is ultimately the spring force of Compressed spring 64 is set. Then the stopper 68 in the sleeve member 54 is inserted and by a Spot weld 78 attached. Now the sleeve element becomes 54 so pushed to measure on the connecting element 52, that a desired possible stroke of the Actuator 60 results. Between the Connecting element 52 and the sleeve member 54 is a Press fit provided.

In addition, these two parts but also by a Weld 80 connected to each other. From the figures is can be seen that the armature 62 on the one hand in Sleeve member 54 is guided and on the other hand on Connecting element 52 can strike. to Wear reduction is therefore on the armature 62 and on Connecting element 52 in the appropriate places a Chrome layer (not shown) provided. Through this In addition, chromium layer is between these two Elements created an axial residual air gap.

After mounting the inlet valve 36 in the pump housing 28th is the preassembled hydraulic assembly 48 am Pump housing 28 attached. This is a Connecting portion 82 of the connecting element 52 in Press fit in a receiving opening 84 of the pump housing 28th positioned, in such a way that at a Actuation of the actuator 60 a desired Opening movement of the valve element 42 of the intake valve 36 results and when not actuated actuator 60th the inlet valve 36 is closed. It goes without saying that the opening stroke of the valve element 42 of the Inlet valve 36 significantly by the maximum allowable hydraulic flow force is determined on the Valve element 42 attacks during operation. For tightness after to ensure the outside, now the connecting element 52nd by a weld 86 with the pump housing 28th welded.

The likewise preassembled electrical assembly 50 is now pushed onto the hydraulic assembly 48. Then is a bow-shaped fastener 88 on the electrical assembly 50 is pushed and with the Pump housing 28 welded (reference numeral 90). The Bow-shaped fastener 88 is made of a material manufactured, which has magnetic properties. The same applies to the pump housing 28. About the Connecting element 52, the armature 62, the bow-shaped Fastener 88 and the pump housing 28 is so in Operation a closed magnetic circuit 91 created (this is in the figure by a dot-dash line ) Indicated. For tolerance compensation and compensation of Thermal expansion is between the electrical assembly 50 and the pump housing 28, a spring element 92 braced.

The high pressure pump 16 and the actuator 24 work as follows:

If no current is applied to the solenoid 74, is located the actuator 60 in the shown in Figure 2 End position in which it bears against the stop member 68. In this State, the position of the valve element 42 of the Inlet valve 36 alone by the pressure differences influenced between the delivery chamber 32 and the inlet 34. Thus, from the high pressure pump 16 at each delivery stroke the delivery piston 30, the maximum possible amount of fuel promoted. Should be less for each delivery stroke Fuel will be delivered during a Delivery stroke the solenoid coil 74 excited. This will be on Magnetic armature 62 generates a force through which the Actuator 60 against the force of the compression spring 64, the valve spring 40 and the valve element 42 attacking hydraulic forces is applied. In the episode will the inlet valve 36 during a delivery stroke at least temporarily kept open, leaving the fuel not to the fuel rail 18, but back to Inlet 34 is promoted.

In Figure 7 is an alternative embodiment of a High pressure pump 16 shown. Thereby carry such elements and areas which are equivalent functions to elements and areas of those shown in Figures 2 to 6 Have high-pressure pump, the same reference numerals. she are not explained again in detail.

In contrast to the previous embodiment is the receiving opening 84 for the electromagnetic Actuator 24 is not coaxial with the central axis of Valve element 46, but with respect to this laterally to S added. Thus, the actuator 60 engages the Valve element 42 of the intake valve 36 off-center. at energized solenoid 74 thereby becomes the valve member 42 open at an angle, and it lies in the forced open Position on the one to the actuator 60 and the others on the annular valve seat 44.

The same is shown in FIG. 8 Embodiment. Again, such elements and Areas that are functionally equivalent to elements and Areas of the illustrated in Figures 2 to 7 Embodiments bear the same reference numerals and not explained again in detail. In the case of FIG. 8 illustrated embodiment, the longitudinal axis of the Actuator 60 with respect to a plane in which the valve element 42 is in the closed state, in an angle W, which is not equal to 90 °. Also by this becomes an off - center point of attack of the Actuator 60 on the valve element 42 of the Inlet valve 36 created.

In the illustrated in Figures 2 to 8 High pressure pumps 16 was the electromagnetic Actuator 24 designed so that when not energized solenoid 74, ie in the de-energized state, the Position of the valve element 42 of the inlet valve 36 of the electromagnetic actuator 24 is not was influenced. Such an electromagnetic Actuator 24 is also called "de-energized closed ".

In connection with FIGS. 9 to 15, the following will be described Embodiments of high pressure pumps 16 explained at which the electromagnetic actuator 24 "normally open" is, which is when not energized Solenoid 74, the valve element 42 of the inlet valve 36th from the actuator 60 in the open position is pressed. It also applies that such elements and areas which are equivalent functions to elements and portions of those shown in Figs Embodiments have the same reference numerals wear and are not explained again in detail.

First, it is noticeable that on the connecting element 52 at its the inlet valve 36 end facing a radially inward pointing collar 94 is present at which the Guide ring 58 is supported. Furthermore, the actuator has 60 in contrast to the previous embodiments in the high-pressure pump 16 shown in FIG Central portion 96 with a larger diameter than his both end sections 98 and 100 respectively Inlet valve 36 remote from the magnet armature 62 is a cylindrical armature counterpart 102 is present, which is welded to the sleeve member 54. The from the Inlet valve 36 remote end 100 of the Actuator 60 is in a blind hole 104 of the Anchor counterpart 102 added, in which a cup-shaped stop member 68 is inserted.

Between the stop member 68 and one between the End portion 100 and the central portion 96 of Actuator 60 formed paragraph (without Reference numeral) is the opening direction of the Inlet valve 36 acting compression spring 64 clamped. The Bow-shaped fastener 88 is in the in FIG. 9 shown embodiment directly with the Anchor counterpart 102 welded (reference numeral 105). Thus the magnetic circuit 91 through the armature counterpart 102, the bow-shaped fastening element 88, the pump housing 28, the connecting element 52 and the armature 62nd closed. As with the previous ones Embodiments, the sleeve member 54 of a is made of nonmagnetic material, the Magnet flux with energized solenoid 74 completely over the armature 62 is passed.

During operation of the high-pressure pump 16, the magnetic coil 74 remains energized to achieve maximum delivery. If the delivery rate is to be reduced, the Magnetic coil 74 briefly de-energized. This will be the Actuator 60 by the compression spring 64 against the Force of the valve spring 40 and against the hydraulic force on the valve element 42 moves in the opening direction, whereby the Valve element 42 lifts off from the valve seat 44. As a stop in Opening direction acts while the guide ring 58, which in this case with one between the left End portion 98 and the central portion 96 of Actuator 60 formed paragraph (without Reference numerals) cooperates.

The assembly of the hydraulic assembly 48 is carried out by that first of the guide ring 58 on the connecting element 52nd and then the sleeve member 54 on the connecting element 52 is attached. Then, the stopper 68 in Anchor counterpart 102 is pressed and the compression spring 64 in the stop member 68 inserted. For adjusting the axial Restluftspalts between the armature 62 and the Anchor counterpart 102, the actuator 60 must together with the armature 62 on the one hand and the Anchor counterpart 102 with the associated with him Stopping part 68 on the other hand be paired.

This pairing can, as can be seen from Figure 14, under Use of a spacer 106 made during the Assembly of the magnet armature 62 on the actuating element 60 between armature 62 and armature counterpart 102 placed becomes. The thickness of this spacer 106 then corresponds the residual air gap. It would also be possible, the distance between a stop surface (without reference numeral) of Stopper 68 and the corresponding surface of the Anchor counterpart 102 to measure and then the Magnetic armature 62 on the actuator 60 to measure put.

The hydraulic assembly 48 is completed by the Anchor counterpart 102 with the actuator 60 and the Magnetic armature 62 inserted into the sleeve member 54 and with this is welded. It is used to set a desired strokes of the actuator 60 the Anchor counterpart 102 to measure in the sleeve member 54th inserted. Preferably, this is a press fit intended. The sleeve member 54 is on the one hand with the Connecting element 52 and on the other hand with the Anchor counterpart 102 in 80 tightly welded. Subsequently is the hydraulic assembly 48 in the corresponding Receiving opening 84 inserted in the pump housing 28 and 86th welded. Then, the electric assembly 50 becomes mounted and the bracket 88 welded in 90 and 105.

The modifications shown in FIGS. 15 and 16 of FIGS Figure 9 shown high pressure pump differ from this by the same characteristics by which the in Figures 7 and 8 embodiments of the differ in Figure 2 shown high-pressure pump 16. The above with regard to functionally equivalent Elements and areas apply accordingly.

Claims (18)

Feed pump (16), in particular high-pressure fuel pump for an internal combustion engine (10), with a pump housing (28) and an electromagnetic actuator (24), with the aid of the delivery pump (16) conveyed fluid amount can be adjusted, characterized in that the actuating device (24) is integrated into the pump housing (28) such that a magnetic circuit (91) of the actuating device (24) is closed at least by a region of the pump housing (28). Feed pump (16) according to claim 1, characterized in that the actuating device (24) comprises a stirrup element (88) of a magnetic material, which is arranged and connected to the pump housing (28) so that it is for the conclusion of the magnetic circuit (91 ) at least contributes. Feed pump (16) according to one of claims 1 or 2, characterized in that the actuating device (24) on the pump housing (28) facing side of a magnet armature (62) has a connecting element (52) for connection to the pump housing (28) and on the side facing away from the pump housing (28) side of the armature (62) comprises an armature counter-element (102), wherein the connecting element (52) and the armature counter-element (102) via a sleeve member (54) of a non-magnetic or dielectric material are interconnected. A feed pump (16) according to claim 3, characterized in that the connecting element (52) is welded (80) to the sleeve element (54), and the sleeve element (54) is welded (80) to the armature counter-element (102), and all three elements (52, 54, 102) are at least part of a pre-assembled hydraulic assembly (48). Feed pump (16) according to claim 4, characterized in that the connecting element (52) with the pump housing (28) is welded (86). Feed pump (16) according to one of claims 3 to 5, characterized in that the armature counter-element (102) at least indirectly forms a stop for an actuating element (60) of the actuating device (24) and is connected to the sleeve member (54) to measure, so in that an end position of the actuating element (60) is thereby adjusted. Feed pump (16) according to one of the preceding claims, characterized in that the actuating device (24) comprises a magnetic coil (74) made of brass. Feed pump (16) according to one of the preceding claims, characterized in that the actuating device (24) has a separate electrical assembly (50). Feed pump (16) according to claim 8, characterized in that the electrical assembly (50) by a bracket member (88) on the pump housing (28) is held. Feed pump according to one of claims 8 or 9, characterized in that the electrical assembly (50) in the installed position by a biasing member (92) is biased. Feed pump (16) according to one of the preceding claims, characterized in that an actuating element (60) of the actuating device (24) acts on a valve element (42) of the feed pump (16) at a location which is off-center with respect to the valve element (42). Feed pump (16) according to claim 11, characterized in that the longitudinal axis of the actuating element (60) with respect to a plane of the valve element (42) at an angle (W) is not equal to 90 °. Feed pump (16) according to any one of claims 11 or 12, characterized in that the longitudinal axis of the actuating element (60) relative to the center of the valve element (42) offset (S) is arranged. Feed pump (16) according to any one of the preceding claims, characterized in that two adjacent to the two end faces of a magnet armature (62) spaces are connected to each other via a fluid connection (63). Feed pump according to claim 14, characterized in that the fluid connection comprises at least one preferably spiral-shaped groove (63) in the lateral surface of the magnet armature (62). Feed pump (16) according to one of claims 3 to 15, characterized in that the pump housing (28) and the magnet armature (62) facing sides of the connecting element (52) via a fluid connection (70) are interconnected. Feed pump (16) according to any one of the preceding claims, characterized in that the actuating device (24) has a first stop element (68) on which of an inlet valve (36) of the feed pump (16) facing away from the end of an actuating element (60) of the actuating device (24) can come into contact with its movement, and which is fixed by means of a spot weld (78). Feed pump (16) according to one of the preceding claims, characterized in that the actuating device (24) comprises a second stop element (58) which is integrated in a guide of an actuating element (60) of the actuating device (24) and the stroke of the actuating element (60 ) is limited to an inlet valve (36) of the feed pump (16) out.

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