EP1490591B1 - Device for damping vibrations on fuel injection systems having a high-pressure accumulating space - Google Patents

Description

Technical area

In injection systems for injecting fuel into the combustion chambers of air compressors Internal combustion engines, today come high-pressure collecting chambers (common rail) for use. The most tubular configured in a thicker wall thickness High-pressure accumulation spaces comprise throttle valves which are arranged at pressure pipe connections are. By means of the throttle valves are generated at the end of the injection process returning pressure waves that occur when closing the nozzle in the fuel injector can, steamed.

State of the art

A high pressure collection room according to the generic term of Claim 1 is from Drucksckrift EP 0 780 569 A known.

DE 196 50 865 A1 discloses a solenoid valve for controlling the fuel pressure in Control pressure chamber of an injection valve, for example in the injector of a common rail injection system. About the fuel pressure in the control pressure chamber, the movement of a Controlled valve piston, with an injection opening of the injection valve open and is closed again. The solenoid valve has a arranged in a housing part Electromagnet, a moving armature and an armature moved by one Closing spring in the closing direction acted upon control valve member, which with a Valve seat of the solenoid valve interacts and so the fuel drain from the control pressure chamber controls. By the pressure relief of the control room is a movement causes a nozzle needle within the injector in the opening direction, while by a pressurization of the control pressure chamber, a closing movement of the nozzle needle which causes the pressure pulsations that occur, i. the returning ones Is pressure waves.

DE 197 08 104 A1 also shows a solenoid valve for controlling the fuel pressure in the control pressure chamber of an injection valve. This valve is also used in the injector Common rail injection system used. The solenoid valve has one in a housing part arranged electromagnet, a movable armature and one with the armature moved, acted upon by a closing spring in the closing direction control valve member, which cooperates with a valve seat of the solenoid valve and so the fuel drain from the control pressure chamber controls. According to the solution disclosed in DE 197 08 104 A1 the solenoid valve two-piece anchor with an anchor bolt and one on the anchor bolt slidably mounted anchor plate executed. The two-piece version reduces the effective braked mass and thus the bounce behavior of the anchor. However, the armature plate movable relative to the anchor bolt may be closed after closing the Solenoid valve on the anchor bolt nachschwingen disadvantageously and on this Way to self-adjusting pressure pulsations, i. returning pressure waves at Trigger closing of the injection valve member.

From the Bosch manual "Diesel Engines Management", 2. updated and expanded edition; Vieweg 1998, Braunschweig / Wiesbaden ISBN 3-528-03873-X, page 231, right Column, there is a Rückströmdrosselventil, which for damping pressure waves used in fuel injection systems. By means of the cited reference known Rückströmdrosselventiles is prevented that at the end of the injection process generated pressure waves, or their reflections not to reopen the Nozzle needle, i. can lead the injection valve member. Another, uncontrolled Opening the nozzle needle and resulting Nacheinspritzer into the combustion chambers of the Internal combustion engines, would have a very negative impact on the pollutants in the Exhaust gas of the air-compressing internal combustion engine, since the portion of the unburned Hydrocarbons increase significantly when uncontrolled post-injection occurs would.

At the beginning of the fuel delivery lifts the spring-loaded valve cone of Rückströmdrosselventiles by the fuel pressure from his seat. The fuel will now passed through a pressure pipe connection and the pressure pipe to the injection nozzle. With At the end of the fuel delivery, the fuel pressure drops abruptly. The valve spring pushes the valve cone back onto the valve seat. When closing the injector in Fuel injector resulting return pressure waves, via a into the valve cone recessed throttle point reduced so far that no harmful, premature Tired of the material of the high-pressure accumulator favoring pressure wave reflections can occur more.

A disadvantage of the known Rückströmdrosselelement is the fact that these Rückströmdrosselelemente need a relatively large amount of space. This affects the mounting options negative; Furthermore, in the cylinder head area of internal combustion engines anyway very limited installation space available. Furthermore, by the Design of the return flow throttle as a multi-component component the number of sealing points negatively affected, i. elevated.

Presentation of the invention

By the solution according to the invention with the features of claim 1 a vibration damping valve is provided, which is integrated into the interior of the high-pressure collecting space (common rail). About that In addition, the solution proposed by the present invention can be applied to today existing interfaces, from their modification at Use the inventively proposed solution is unnecessary. The invention proposed vibration damping valve is still pre-assembled and safe in the interior of the high pressure accumulator (common rail) arranged. Furthermore, when in use the proposed solution according to the invention no changes / reworking existing piping systems, whether to / from the high-pressure collection room required and it can be used regardless of type according to the modular system. Another advantage of the proposed vibration damping valve is located in his compared to the Rückströmdrosselelement the cited references significantly lower production costs.

In addition to the inner diameter of the high-pressure collecting space (common rail), the seal to the high pressure line, the attachment of the line can be almost unchanged maintained. This can be achieved in that the closing element of the vibration damping valve is housed in the interior of the high-pressure collecting space and its Outdoor area including the local attachments and system components therefore not is affected. Advantageously, the closing element of the vibration damping valve acts on the sealing point of the high-pressure accumulation chamber (common rail) to the high pressure line to the injector, thus to the point at the returning pressure waves or Pressure wave reflections that occur when closing an injection valve member such. one Nozzle needle occur at the end of the injection process, in the high-pressure accumulation chamber (Common rail) can run back.

In addition to a variant of the proposed solution according to the invention as a single Springs attached to a part of a closure member, such as e.g. taken a retaining pin is and is supported against the inner wall of the high-pressure collecting space can the closing element, also formed by an integrally formed spring bar, what the mounting in the axial direction from one end of the high-pressure accumulation chamber in the tubular interior greatly facilitated. In a one-piece Execution of closing element and formed thereon supporting spring tongues, the spring elements can be bent back or punched out by means of a tool or be bent.

The one-piece closure / spring elements can be dependent on the axial length of the location and number in particular the distance of the drain holes variant-specific are manufactured at significantly lower manufacturing costs, compared with the Rückströmdrosselelementen known in the art.

drawing

The invention will be described in more detail below with reference to the drawing.

Figur 1

eine erste Ausführungsvariante der erfindungsgemäßen Lösung, bei dem ein Schließelement an einem vorgespannten Haltebolzenfeder beaufschlagt aufgenommen ist,

Figur 2

eine weitere Ausführungsvariante der erfindungsgemäß vorgeschlagenen Lösung mit einer alternativen Federgeometrie, wobei Schließelement und dieses beaufschlagende Feder einteilig ausgebildet werden können,

Figur 3

eine dritte Ausführungsvariante, welche in axialer Richtung in das Innere des Hochdrucksammelraumes (Common-Rail) montierbar ist und

Figur 4

die perspektivische Ansicht eines einteilig ausgebildeten Schließelementes zur Integration in einen rohrförmig konfigurierten Hohlraum des Hochdrucksammelraumes mit am Schließelement ausgestanzten Federzungen.

It shows:

FIG. 1

a first embodiment of the solution according to the invention, in which a closing element is received acted upon by a prestressed retaining bolt spring,

FIG. 2

a further embodiment of the proposed solution according to the invention with an alternative spring geometry, wherein the closing element and this acting spring can be integrally formed,

FIG. 3

a third embodiment, which in the axial direction in the interior of the high-pressure accumulation space (common rail) can be mounted and

FIG. 4

the perspective view of a one-piece closure element for integration into a tubular cavity of the high-pressure collecting chamber with punched on the closing element spring tongues.

variants

The illustration of Figure 1 is a first embodiment of the invention To take solution in which a closing element is received biased on a retaining bolt is.

An illustrated in Figure 1 high-pressure accumulator 1 limits a tubular substantially circular shaped cavity through an inner wall 2. The one outer wall of the high-pressure accumulator 1 as shown in Figure 1 is denoted by reference numerals 3 marked. The transverse axis 4 of the high-pressure collecting chamber extends in a horizontal Direction, the vertical axis 5 of the high-pressure accumulation chamber extends vertically to the transverse axis. The longitudinal axis 6 of the high pressure accumulation chamber 1 extends in the plane of the drawing at the intersection of transverse axis 4 and vertical axis 5. The wall 7 of the high-pressure collecting chamber is formed in a wall thickness 8, wherein the high-pressure accumulation space 1 is substantially tubular and generally as a forged part is trained. For the control of the interior of the high pressure accumulator 1 occurring high pressures, the wall thickness 8 is designed accordingly. On the outside wall 3 of the high pressure accumulator 1, a nozzle 9 is fixed, which has an internally threaded portion 10 includes. In this is a screw-11, with a corresponding Screwed male threaded portion on which a not shown in Figure 1 to the corresponding injector of a combustion chamber of an internal combustion engine extending High pressure line is included. About the recorded on the screw 11 High pressure line for supplying fuel to the injector of a combustion chamber the internal combustion engine is this from the high-pressure accumulator 1 under very high pressure fuel for injection according to the movement of the Injector valve member of the injector into the combustion chamber of the internal combustion engine fed. When closing the injection valve member of the injector occurring pressure waves flow back through the high pressure line to the screw 11 and can thereby run back into the interior of the high-pressure accumulator 1.

The screw-in connection 11 acts on a disk-like configured component 12, which comprises a first cone 13 located on a shoulder 17 of a High pressure line connection 15 formed conical seat 18 is supported. The screw-in connection 11 is supported on the upper ring-shaped end face of the disc-shaped Component 12 off. By this type of attachment of the high pressure line connection 15 this is caused by the force acting on the shoulder 17 adjusting force with its lower End in a seat 28 at the high-pressure reservoir 1 tightly hired.

In order to prevent that via the high pressure line and the high pressure line connection 15th when closing the injection valve member of the injector resulting pressure waves or Pressure wave reflections run back into the interior of the high-pressure accumulator 1 and this unduly stress it is according to the invention proposed Solution provided a vibration damping valve, which is a substantially Closing element 19 and a closing element via a shaft 22 acting on Spring body 25 and 32, 40 includes.

In the embodiment of the vibration damping valve as shown in FIG FIG. 1 shows a substantially disc-like configured closing element 19, whose outer contour substantially corresponds to the course of the seat surface of the seat 28, in which a wall 7 of the high-pressure accumulator 1 passes through hole expires. The closing element 19 comprises a rod-shaped shaft 22 which abuts his projecting into the interior of the high-pressure accumulator 1 end with an abutment 27 is formed for receiving a spring body 25. In the embodiment of the vibration damping valve according to Figure 1, the closing element 19 via a locking ring 24 with the shaft 22, which serves as a retaining bolt connected. At the extent the closure member 19, i. in the seating area 23 of the seat 28 is at least one formed throttle-like return orifice 20, which is a return flow of fuel in returning to the high-pressure accumulator 1 back pressure waves and thus a Return flow of fuel via the high-pressure line connection 15 via its longitudinal bore 16 allowed in the interior of the high pressure accumulator 1, without this - im essentially caused by the throttling action of the return flow 20 - by high Pressure spikes would be applied.

According to the first embodiment variant of the invention proposed in FIG Vibration damping valve, the closure member 19 substantially in disc-like design and serving as a retaining pin shaft 22, two separate Are components that have a snap ring or a differently designed fastener 24 are connected to each other captive. The at the bottom of the as a retaining bolt serving shank 22 formed abutment 27 supports a turn of a Spring body 25. The windings of the spring body 25, preferably as a spiral spring is formed, expand in terms of their diameter according to a conical Contour 26 in the direction of the inner wall 2 of the high-pressure accumulation chamber 1. As a result the spring body 25 is supported according to its conical contour 26 with a larger diameter on the inner wall 2 of the high-pressure accumulator 1 from, compared with the diameter at which the spring body 25 on the abutment 27 in the lower region of the serving as a retaining pin shaft 22 is received. The conical contour 26 of the Spring body 25 also facilitates the assembly of the spring body 25 through the hole in the wall 7 of the high-pressure accumulator, which is coaxial with the vertical axis 5 of the high-pressure accumulator 1 runs.

In the embodiment of the present invention proposed vibration damping valve As shown in Figure 1, each is a high pressure line connection 15 associated vibration damping valve, essentially a closing body 19, a shaft 22 and a closing element 19 acting on the spring body 25 containing acted upon by a separate spring element 25. This means that along the Longitudinal direction 6 of the high pressure accumulator 1 depending on the number of high-pressure line connections 15, based on the number of cylinders of fuel to be supplied to the internal combustion engine serves, a corresponding number of vibration damping valves 19, 22, 25 is arranged, all independent of each other by individual spring body 25th with conical contour 26 for ease of assembly in the interior of the high-pressure collecting chamber 1, to be preloaded.

That the closing force of the vibration damping valve according to the embodiment in Figure 1 applying spring element is in the interior of the high-pressure accumulation chamber integrated, eliminating existing interfaces such as the inner diameter of the high-pressure collecting space 1, the sealing point to the high-pressure line connection 15 and the attachment the high-pressure line at the high-pressure line connection 15 is maintained unchanged can be. The closing element 19 according to the solution proposed according to the invention the vibration damping valve is directly on the sealing point 23, 28 below of the high-pressure line connection 15. The connection of closing element 19 and as Holding bolt serving shank 22 may be both a trained as a Seeger ring Fastener 24 as well as by welding, cabinets, crimping and the like Connection techniques are made. When mounting the shaft 22 and the spring body 25 provided with a conical contour 26 from the outside through the coaxial with Vertical axis 5 extending bore mounted. Should be due to space or mounting reasons the serving as a retaining pin shaft 22 longer than later functionally necessary be, this can be shortened after assembly (see dashed line illustration of Shank 22 within the longitudinal bore 16 in Figure 1).

FIG. 2 shows a further embodiment of the proposed invention Vibration damping valves with an alternative spring body geometry, wherein the Spring element is integrally formed.

With regard to the design of the connecting piece 9 for the connection of the high pressure line via the screw-in connection 11 and the attachment of the high-pressure line connection 15 the outer wall 3 of the high-pressure accumulation chamber 1 is the description of Figure 1 directed.

According to the embodiment variant of the invention proposed in FIG Vibration damping valves are the closing element 19 and as a retaining bolt Serving shaft 22 integrally formed. At the bottom, in the interior of the high-pressure collecting room 1 protruding end of the shaft 22 is a thickening 34 is formed, which as Support point for a pair of spring tongues 32, 33 is used. The one-piece spring body 30 according to the embodiment of the vibration damping valve in Figure 2 is as configured to the interior of the high-pressure accumulation open U-profile. In manufacturing technology particularly simple way can on the one-piece spring body 30, the spring tongues 32 and 33, which are located on both sides of the inside of the high-pressure collecting space 1 extend extending shaft 22 of the vibration damping valve, be punched out or bent out. The spring tongue ends 57 of the first spring tongue 32 and the second spring tongue 33 are based on a broadening of the extension 34 in the lower region of the shaft 22 from. The first spring tongue 32 and the second Spring tongue 33 can be used to improve the spring action with an S-shaped profiling 37 are provided. By the support of the first spring tongue or the second Spring tongue 33 on the repository 34, the one-piece spring body 30 is a Sealing seat 31 causing, at the upper portion of the inner wall 2 of the high-pressure accumulation chamber 1 employed. The integrally formed spring body 30 is therefore relatively movable to the shaft 22 of the vibration damping valve according to that shown in FIG Version stored. Reference numeral 36 denotes the break-out points, where the spring tongues 32, 33 in Richtunng on the open side of the U-profile trained one-piece spring body are bent.

Also, the closing element 19 of the vibration damping valve in the embodiment according to Figure 2 can laterally on the circumference analogous to the formation of the closing element 19 according to the embodiment of the solution according to the invention shown in Figure 1 be provided with a backflow opening 20. In the embodiment variant shown in FIG. 2 is shown, are therefore seen in the longitudinal direction 6 of the high-pressure accumulation chamber 1 all spring elements connected together. The integrally formed spring body 30 is when mounted in the axial direction, i. in the direction of the longitudinal axis 6 in the interior of the High-pressure collecting chamber 1 inserted. This simplifies the assembly considerably; of the one-piece spring body 30 may be in a specific to the length of the high-pressure accumulation chamber 1 tuned axial length are formed whereby type-specific adjust one-piece spring body 30, depending on the number of cylinders through the high-pressure accumulator 1 with fuel to be supplied internal combustion engine and depending on. Distance of the high pressure ports 15 in the longitudinal direction of the High-pressure collecting chamber 1. For installation in the interior of the high-pressure collecting chamber 1, the one-piece spring body 30 in the longitudinal direction in the interior of the high-pressure collecting space inserted, wherein the spring tongues 32, 33, the S-shaped course 37, can be pushed back by means of an auxiliary tool and at the Shaft 22, spaced at intervals according to the distances of the high pressure line connections 15 protrude into the interior of the high-pressure accumulator 1, be locked.

Also in the embodiment of a vibration damping valve that in Figure 2 is shown immediately at the Rückströmstellen, i. the coaxial with the vertical axis 5 of the high-pressure accumulator 1 extending bore a sealing point 31 is formed, the When closing an injection valve from the injector returning pressure waves or Pressure wave reflections when entering via the axial bore below the closing element 19 occurring pressure peaks in the interior of the high pressure accumulator 1 effective attenuates. The one-piece spring element 30 may, for. B. as a sheet metal profile of a steel with spring properties be made.

Depending on the manufacturing process, i. the bending of the individual spring tongues 32 and 33 at the points 36, the spring tongues 32, 33 also with a different than an S-shaped Contour 37 be provided to a hiring of the edges, the sealing seat 31 at the Inner wall 2 of the high-pressure accumulation chamber to ensure. It is essential in that the spring tongue ends 57 of the mutually opposite spring tongues 32, 33 at the abutment 34 at the lower end of the shaft 22, the axial bore of the Supported high-pressure collecting space support and thus both the closing element 19th pull in the seat 28 as well as the in this embodiment of the present invention proposed vibration damping valve integrally formed spring body 30 in make its sealing seat 31 in the upper region of the high-pressure collecting space sealing.

FIG. 3 shows a further embodiment of the proposed invention Vibration damping valve which in the axial direction in the high-pressure accumulation chamber (Common rail) can be mounted. According to this third embodiment of the invention proposed vibration damping valve is analogous to the embodiments in Figure 1 and Figure 2 above a hole in the wall 7 of the high-pressure accumulation chamber 1 a closing element 19 from which extends into the interior of the High-pressure accumulator 1 a serving as a retaining pin shaft 22 extends. In difference to the embodiments shown in Figure 1 and Figure 2, the shaft 22nd enclosed by a guide 43, which partially into the interior of the high-pressure collecting space 1, i. may be formed projecting over the inner wall 2. That too Closing element 19 of the embodiment of the vibration damping valve shown in Figure 3 can on its outer circumference with at least one return flow opening 20, which acts as a throttle. The lower end of the shaft 22, which in the interior of the high-pressure collecting chamber 1 protrudes similarly as in the figures 1 and FIG. 2 shows an abutment 34 on which, in this embodiment, a ring-shaped trained, one-piece spring body 40 is supported. The one-piece, ring-shaped Spring body 30 extends annularly along the wall 2 of the high-pressure collecting space 1 and includes the area of each high pressure port 15 over the slotted spring arms seen in the direction of the longitudinal axis 6 of the high-pressure collecting chamber 1 42, whose ends 57 above the abutment 34 at the lower end of the shaft 22nd support. The slotted spring arms 42 merge into an annular portion 41, whose lateral surface corresponding to the contour of the inner wall 2 of the high-pressure collecting space 1 is formed. The annular, one-piece spring body 40 is überfedemd educated. This means that after insertion of the spring body 40 in Längsrichung 6 of the high-pressure accumulation chamber, the slotted spring arms 42 in the direction of the two dargestellen in Figure 3 arrows can be bent so that the spring body, i.e. the ends 57 of the slotted spring arms 42 above the abutment 34 at the bottom End of the shaft 22 can engage. The guide 43, of which the shaft 22 enclosed is facilitates the assembly wherein the guide 43 as three or more on the shaft 22 offset by 120 ° C to each other or offset by 90 ° to each other depending on the number of guide ribs may be arranged to assemble the annular, one-piece spring body 40 to facilitate. By means of this configuration of the one-piece spring body 40 can be on the one hand simplify the closing process, as the closing element easier and quickly retracts into its intended seat and ensures a reliable seal.

The closing element 19, the shaft 22 and the annular spring body 44, which essentially make up the vibration damping valve cause a Reduction of the high-pressure port 15 and over the longitudinal bore 16 in the high-pressure accumulator 1 returning pressure pulsations or pressure wave reflections. These arise in the end of the injection phase when in one of the high-pressure collecting space supplied injector whose injection valve moves into its seat, i. the injection is ended. As one equipped with a common-rail fuel injection system Internal combustion engine comprising 4, 6 or 8 cylinders can over each 4, 6 or 8 fuel injectors upon completion of their injection operations with respect Pressure waves or pressure wave reflections on the respective high pressure lines to the High-pressure ports 15 of the high-pressure accumulator 1 run back to a Pressure peak in the interior of the high-pressure accumulation chamber 1 (common rail) can lead. With the inventively proposed vibration damping valve according to the outlined embodiment in Figures 1, 2 or 3, the mechanical Effects in the high-pressure collecting chamber returning pressure peaks through return openings 20 are reduced in the upper region of the closing element 19, since the at least one provided on the outer contour of the seat 23, 28 return flow 20th acts as a throttle.

Figure 4 shows a perspective view of a one-piece closing element for integration in the substantially formed with tubular cross-section high-pressure accumulation chamber with punched spring tongues.

The one-piece spring body 30 shown in Figure 4 extends over an axial length 50, which corresponds to the length of the high-pressure accumulator 1, in which the one-piece spring body 30 inserted in the axial direction corresponding to the longitudinal axis 6 we. In Distances 56 are punched out in the one-piece spring body 30 spring tongues 32 and 33 down. These spring tongues lie with their ends 57 above the abutment 34th (Compare representation according to Figure 3 and thus press the sealing edges 54 to the angled corners of the formed as a U-profile 55 one-piece spring element to the Inner wall 2 of the high-pressure accumulation chamber 1 (see illustration according to FIG. 2).

The side surfaces of the U-profile 55 procured one-piece spring body 30 are with Numeral 52 and 53 and shorter than the side surface 52 and 53, respectively interconnecting bridge. The spring tongues 32 and 33, in the S-shaped contour 37 can run or have another resilient setting enabling contour can support themselves with their spring tongue ends 57 on the abutment 34 and thus form a sealing seat at the top of the high-pressure accumulation chamber 1 each under a High-pressure line connection 15. Depending on the number of injectors with high-pressure line connections 15, the integrally formed spring body 30 in a type-specific Length 50 are formed, with the distance 56 and the number of Ausstanzstellen 51 for the downwardly extending spring tongues 32 and 33 after the number the vibration damping valves directed, i. according to the number of high pressure line connections 15, in the embodiments of the vibration damping valve shown in Figures 1, 2 and 3 each at the top of the wall 7 of the high-pressure collecting space 1 are formed.

LIST OF REFERENCE NUMBERS

1

High-pressure accumulator

2

inner wall

3

outer wall

4

transverse axis

5

vertical axis

6

longitudinal axis

7

wall

8th

Wall thickness

9

Support

10

Internal threaded branch

11

stud fitting

12

disc

13

First cone

14

Second cone

15

High pressure pipe connection

16

longitudinal bore

17

shoulder

18

conical seat

19

closing element

20

return flow

21

Drosselstellezz

22

shaft

23

Seat closing element

24

attachment

25

spring element

26

Conical contour

27

Abutment spring element

28

Seat

30

Spring element (one-piece)

31

Seat

32

First spring tongue

33

Second spring tongue

34

Thickening shaft

35

punching

36

punching place

37

S-shaped contour

40

Over-springing spring body

41

contact surface

42

Slotted spring arm

43

guide section

44

Free space for deformation

50

Longitudinal extension of one-piece spring body (30)

51

punching place

52

First side surface

53

Second side surface

54

sealing edge

55

U-profile

56

Distance punched out

57

Spring tongue ends

Claims (15)

1. High-pressure accumulation space (1) for fuel injection systems, with a number of high-pressure line connections (15) corresponding to the number of combustion spaces of an internal combustion engine to be supplied with fuel, the high-pressure accumulation space having essentially a circular cross section which is delimited by an inner wall (2), the high-pressure line connections (15) comprising a longitudinal bore (16), through which fuel flows, and being received by means of a screw-in element (11) in a connection piece (9) which is fastened to the outside of the high-pressure accumulation space (1) and by means of which the high-pressure line connections (15) are pressed into a seat (28) in the high-pressure accumulation space (1), characterized in that the high-pressure accumulation space (1) receives a vibration-damping valve which comprises a closing element (19) and which is acted upon by a spring body (25; 30, 32, 33; 40) which is supported on a shank (22) connected to the closing element (19) and on the inner wall (2).
2. High-pressure accumulation space (1) according to Claim 1, characterized in that the closing element (19) is received in a bore which passes through the wall (7) of the high-pressure accumulation space (1) and which runs out into the seat (28) for receiving the high-pressure line connection (15).
3. High-pressure accumulation space (1) according to Claim 1, characterized in that the seat (28) for receiving the high-pressure line connection (15) is designed as a conical seat (23).
4. High-pressure accumulation space (1) according to Claim 1, characterized in that the closing element (19) comprises a shank (22) of bar-like design which extends into the inner space of the high-pressure accumulation space (1) and on which an abutment (27, 34) for a spring body (25; 30, 32, 33; 40) is formed.
5. High-pressure accumulation space (1) according to Claim 1, characterized in that the closing element (19) has formed on it at least one backflow orifice (20) having a throttle-like action and allowing a backflow of fuel out of the high-pressure line connection (15) into the high-pressure accumulation space.
6. High-pressure accumulation space (1) according to Claim 1, characterized in that the outer contour of the closing element (19) of disc-shaped design matches with the run of the contour of the seat (28).
7. High-pressure accumulation space (1) according to Claim 1, characterized in that the closing elements (19) of the vibration-damping valve which are assigned to the individual high-pressure line connections (15) are prestressed via individual spring bodies (25).
8. High-pressure accumulation space (1) according to Claim 7, characterized in that the spring bodies (25) have a conical diameter (26) widening from an abutment (27) in the direction of the inner wall (2).
9. High-pressure accumulation space (1) according to Claim 1, characterized in that the closing elements (19) of the vibration-damping valve which are assigned to the individual high-pressure line connections (15) are prestressed jointly by a one-piece spring body (32, 40).
10. High-pressure accumulation space (1) according to Claim 9, characterized in that the one-part spring body (30) is designed as a U-profile (55), from the surfaces of which project spring tongues (32, 33), the ends (57) of which are supported on an abutment (34) of the shank (22).
11. High-pressure accumulation space (1) according to Claim 10, characterized in that sealing edges (54) lying on the inner wall (2) of the high-pressure accumulation space (1) are formed on the U-profile (55) of the one-part spring body (30).
12. High-pressure accumulation space (1) according to Claim 10, characterized in that the spring tongues (32, 33) are located opposite one another in pairs and are arranged at distances (56) from one another on the one-part spring body (30).
13. High-pressure accumulation space (1) according to Claim 10, characterized in that the length (50) of the one-part spring body (30) corresponds to the extent of the high-pressure accumulation space (1) in a longitudinal direction (6).
14. High-pressure accumulation space (1) according to Claim 9, characterized in that the one-part spring body (40) is designed as a spring-over spring body, the outer contour (41) of which corresponds to that of the inner wall (2) and comprises slotted spring arms (42), the ends (57) of which are supported on the abutment (34) of the shank (22).
15. High-pressure accumulation space (1) according to Claim 1, characterized in that the shank (22) of the closing element (19) is guided in a guide (43) passing through the bore for the high-pressure line connection (15).

Images