JPH10299602A - Fuel injection unit for internal combustion engine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To put a valve control element in contact with a first and second valve seats without jumping by disposing a damping unit between an end facing to the adjusting magnet and the anchor plate of the valve control element. SOLUTION: An anchor plate 81 is disposed in a control valve element 45 via a damping unit 101 at an end facing to an adjusting magnet 49 and is operatively connected to the adjusting magnet 49. The adjusting magnet 49 is mounted on the casing 20 of an injection unit 15 via a middle plate 85 at the extension of a casing hole 47. The casing hole 47 is enlarged at the exit to the middle plate 85 to form a spring chamber 87. In the spring chamber 87 is disposed a return spring 91 set between the link disc of the middle plate 85 and a spring receiver 89 in the control valve element 45. The return spring 91 holds the control valve element 45 of a three-way control valve 19 in contact with a second valve seat 65 a second valve seal plane 67 when the adjusting magnet 49 is not supplied with current.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a fuel injection unit of the type defined in claim 1.

[0002]

2. Description of the Related Art According to DE 43 32 119 A1, a fuel injection unit of the above type having a number of fuel injection devices corresponding to the number of injection points into the combustion chamber of the internal combustion engine to be supplied with fuel, In a fuel injection device, for proper combustion of fuel in a combustion chamber of an internal combustion engine,
It is known that the injection pressure can be freely adjusted in addition to the free control of the injection start and the injection end. The high-pressure fuel pump transfers fuel from the fuel storage tank at high pressure to the high-pressure collecting chamber via a transfer conduit. This high-pressure collecting chamber is connected via a high-pressure conduit to the individual injection units corresponding to the number of injection points in the combustion chamber to be supplied with fuel. In this case, each of these injection units is composed of an injection valve that enters the combustion chamber of the internal combustion engine and a three-way control valve that controls the injection valve. In this case, the valve member of the injection valve configured as a seat valve has on its shaft a pressure surface formed with a reduced cross section towards the valve seat. At this pressure level, the valve member protrudes into a first pressure chamber which is always connected to the high pressure conduit to the high pressure collecting chamber and the injection opening in the valve seat. In this case, the pressure in the pressure chamber loads the valve member in the opening direction. At the end face opposite the valve seat, the valve member defines a second pressure chamber. This pressure chamber can be connected via a three-way control valve to a high-pressure line or a pressure-release line to the fuel storage tank. In this case, the effective cross-section under pressure at the valve member is smaller in the region of the first pressure chamber than in the region of the second pressure chamber.

[0003] The three-way control valve controlled by the electric control device is configured as a double seat valve, the double seat valve of which
In the axial direction, a piston-like control valve adjustable between two stops configured as a valve seat connects the end-side pressure chamber of the injection valve with the high-pressure line or the discharge line depending on the switching position. I do. In this case, the throttling effect during the connection between the second pressure chamber and the pressure relief conduit is realized by a reduction in the effective area of the outflow cross section inside the three-way control valve.

[0004] The control of the control valve member is effected via an adjusting magnet. This adjusting magnet is arranged on the casing of the injection unit via an intermediate plate. At the end of the control valve member facing the adjusting magnet, an anchor plate is inserted into the control valve member and tightened with screws. The positioning of the control valve member takes place via a return spring tightened between the ring disk of the intermediate plate and the spring receiver of the valve member, with no current flowing through the adjusting magnet. This causes the control valve member to contact the second valve seat at the second valve sealing surface. In this valve seat, the high-pressure conduit is connected to the first pressure chamber, and the high-pressure conduit is connected to the second pressure chamber via a second flow chamber in the three-way control valve. If injection is desired, a current is passed through the electric adjusting magnet by the control device, so that the control member of the three-way control valve is brought into contact with the first valve sealing surface against the force of the return spring. Closing the connection between the first flow chamber connected to the high pressure conduit and the second flow chamber connected to the second pressure chamber. This reduces the pressure in the second pressure chamber, lifts the injection valve member from the valve seat against the force of the valve spring and opens the injection valve.

[0005] In this case, the known fuel injection unit generates a valve jump when the control valve member collides with the first valve seal surface in a state where a current is applied to the adjusting magnet, and particularly the injection process is performed. There is the disadvantage that the control valve member collides with the second sealing surface later and after the electric adjusting magnet has been switched to a current-free state, so that the control valve member is rebounded. This valve departure causes a delay in the injection at the beginning of the injection process and, in particular, a post-injection of the fuel at the end of the injection process, which leads to an undefined and indeterminate injection course.

[0006]

SUMMARY OF THE INVENTION It is an object of the present invention to prevent valve jump so that the control valve member contacts the first and second valve seats without jump.

[0007]

The object of the invention has been achieved by providing a damping device between the end of the control valve member facing the adjusting magnet and the anchor plate. This enables accurate control of the fuel injection amount. Therefore a controlled, in the combustion chamber of the internal combustion engine,
The prescribed combustion becomes possible.

[0008] The damping device preferably has a spring element fixedly connected on the one hand to the control valve element and, on the other hand, fixedly to the anchor plate. This provides an indirect arrangement of the anchor plate with respect to the control valve member, so that the anchor plate is provided in the form of a floating bearing. This arrangement is such that after one valve sealing surface has come into contact with the valve seat and the closing process has ended, the shock absorber is activated,
The movement of the anchor plate is slowly damped via the spring member. This allows the sealing surface of the control valve member to contact the valve seat without bouncing. A further advantage is that the anchor plate is mounted in a recess in the intermediate plate, which is fixed on the one hand to the housing and on the other hand receives the adjusting magnet. This intermediate space is filled with oil, so that an additional damping action is achieved by displacement of the oil based on the adjusting movement.

According to an advantageous embodiment of the invention, the spring element is designed as a spring plate, so that a damping action similar to a leaf spring is obtained. In a further advantageous manner, the spring plate is fixedly arranged with respect to the control valve member via a screw between the two flexible members. This makes it possible to adjust the cushioning of the spring plate. In this case, the flexible member arranged between the spring plate and the anchor plate is advantageously larger than the member arranged between the spring plate and the control valve member. This ensures that the post-injection of fuel is prevented, since a greater degree of damping can be effected when the current to the adjusting magnet is switched off, ie when the injection has ended.

[0010] The spring plate and the anchor plate can be connected to each other by a known releasable connection or a non-releasable connection. In this case, a spacer disk is arranged between the spring plate and the anchor plate. The thickness of the spacer disc is greater than the thickness of at least one flexible member disposed between the anchor plate and the spring plate, and determines the spring travel of the anchor plate when the current to the adjusting magnet is turned off. It is advantageous if an intermediate chamber A is left. The spring stroke can be adapted in relation to the adjusting force by the thickness of the spacer disk or the thickness of the flexible element.

The anchor plate preferably has a stepped hole in which the fastening means, preferably a screw, is arranged. This screw serves to secure the spring plate and the flexible member to the control valve. The stepped through-hole has first and second diameters, and is larger than the screw head of the fixing member and the subsequent cylindrical shaft, and the anchor plate is supported floating in the direction of movement of the control member. Can be.

Furthermore, a gap B is formed between the screw head of the coupling means and the shoulder formed by the stepped hole, the gap forming a spring stroke when current is applied to the adjusting magnet. Advantageously, a controlled start of the injection process is enabled when the control valve member is moved to the first valve seat.

The reciprocating movement of the control valve member can be determined in an advantageous manner both by the mass of the anchor plate and the mass of the shock absorber and by the design of the shock absorber. Furthermore, the spring travel can be adjusted both by the size of the intermediate chamber between the flexible member and the anchor plate and by the size of the intermediate chamber between the screw head and the shoulder of the stepped bore. .

[0014] Further advantages and advantageous features of the invention are described in the detailed description, drawings and claims.

[0015]

DESCRIPTION OF THE PREFERRED EMBODIMENTS In the fuel injection device shown in FIG. 1, a high-pressure fuel pump 1, which can be configured as a piston pump, transports fuel from a low-pressure chamber 3 configured as a fuel storage tank. It is conveyed to the high pressure collecting chamber 7 at a high pressure via a conduit. The pressure in the high-pressure collecting chamber 7 is connected via a pressure control valve 9 connected to a return line 11 extending from the high-pressure collecting chamber 7 into the low-pressure chamber 3 and acting on the operating parameters of the internal combustion engine or by the discharge of a high-pressure fuel pump. Adjustable.

Further, from the pressure collecting chamber 7, a high pressure conduit 13 is provided.
Extends toward the individual injection units 15 corresponding to the number of injection points into the combustion chamber of the internal combustion engine to be supplied with fuel. Each of the injection units is formed by an injection valve 17 and a three-way control valve 19 which enter the combustion chamber of the internal combustion engine. These injection valve 17 and three-way control valve 1
9 is arranged in a common casing 20. The injection valve 17 is configured as a seat valve having a piston-shaped injection valve member 21. One end face of the injection valve member 21 has a conical sealing surface 25 with which the injection valve member 21 cooperates with a valve seat 29 adjacent the injection opening 27. The injection valve member 21 has on its shaft a pressure shoulder 31 formed by a reduction in cross section. This pressure shoulder 3
1 is directed to a valve seat 29, and the injection valve member 21 is a pressure shoulder 31 which is formed by a first diameter formed by enlarging the diameter of the guide hole 23.
Into the pressure chamber 33. This pressure chamber 33 extends continuously as a ring gap around the shaft of the injection valve member 21 to the valve seat 29 and is constantly connected to the high-pressure line 13 via a connection line 35 in the casing of the injection unit 15. This high-pressure conduit 13 allows the high-pressure conduit 13
The internal fuel pressure is transmitted to the first pressure chamber 33, and the injection valve member 21 is loaded in the opening direction against the force of the valve spring 39 disposed in the spring chamber 37. The valve spring 39 acts on the end of the valve member 21 protruding from the guide hole 23 on the side opposite to the valve seat 29 via a spring receiver 40. This spring receiver 4
Above the zero, an additional piston 38 acts. The piston 38 has a diameter slightly larger than the diameter of the guide hole 23, and at the end face opposite to the valve seat, a second pressure chamber 4 is formed in a blind hole 42 for guiding the piston 38.
1 is restricted. The second pressure chamber 41 is connected to the three-way control valve 19 via a connection passage 43. in this case,
The fuel pressure that can be built up in the three-way control valve 19 loads the injection valve member 21 in the closing direction.

The three-way control valve 19 connected to the second pressure chamber 41 is configured as a double seat valve and has a piston-shaped control valve member 45. The control valve member 45 is guided into the casing hole 47 and is loaded on one end face 48 by an electric adjusting magnet 49 fixed to the casing 20, and the control valve member 45 is provided on the outer peripheral surface with a first ring groove. Ring-shaped notch 51 is separated from second ring-groove-shaped notch 53. In this case, the diameter of the ring web 50 is enlarged with respect to the diameter of the valve member sections 55, 56 which limit the two notches 51, 53 on opposite sides. In this case, the ring end face of the ring web 50 facing the end face 48 loaded by the adjusting magnet 49 transitions conically from the outer diameter to the inner diameter corresponding to the diameter of the first notch 51, and A conical valve sealing surface 57 is formed. This valve sealing surface 57 cooperates with a first valve seat 59 created by the conical diameter enlargement of the casing bore 47. In this case, the first valve seat 59 and the first notch 51
A first flow passage chamber 61 is formed between the wall of the casing hole 47 and the control valve member 45 between the end portion on the opposite side to the ring web 50. The high-pressure conduit 13 to the common high-pressure collecting chamber 7 is open in the first flow chamber 61, and the connecting conduit 35 is connected from the first flow chamber 61 to the first pressure chamber 33 of the injection valve 17. Extends to. In this case, the connection conduit 35 remains connected to the high-pressure conduit 13 at all times.

On the side opposite to the adjusting magnet 49, the first valve seat 4
9 restricts the second flow chamber 63. A connection passage 43 to the second pressure chamber 41 of the injection valve 17 is opened in the second flow chamber 63, and the flow chamber 63 extends beyond the range of the second notch 53, Casing fixed second valve seat 65
Extending to In this case, this second valve seat 65 is formed by a conical diameter reduction of the casing bore 47 and cooperates with a second valve sealing surface 67 on the end face of the control valve member 45 opposite the adjusting magnet 49. I do.

In this case, the second valve seat 65 is disposed on a filling member 69 having a part of the casing hole 47. The filling member 69 is connected to the casing 2 via a fastening screw 71.
He is tight against zero. The part of the casing bore 47 which lies within the filling member 69 transitions in the form of a stepped bore into a small diameter axial blind bore 73 which is an extension of the casing bore 47. In this case, the diameter of the valve member section 55 protruding into the filling member 69 is smaller than the diameter of the portion of the casing hole 47 that guides the valve member section 55. In this case, the free cross section has a smaller dimension than the open cross section in the second valve seat 65 and thus forms a throttle section.

However, the control valve member 45 is filled with a filling member 69 at the valve member section 55 adjacent to the second valve sealing surface 67.
And the fuel passage is adjoined via a longitudinal groove from the second passage chamber 63 toward the second valve seat 65 of the passage chamber in the casing hole. An inner ring groove is also possible. A lateral hole 75 extends from a blind hole 73 forming a third flow chamber 74, and the lateral hole 75 is connected to the low-pressure chamber 3 via a discharge conduit 77, and through this lateral hole 75, a control valve member is provided. 45 is the second
The second flow chamber 63 is lifted from the valve seat 65 of the second
Can be depressurized.

At the end facing the adjusting magnet 49, the anchor plate 81 is connected to the control valve member 4 via the shock absorber 101.
5. This anchor plate 81 cooperates with an adjusting magnet 49 not shown. This adjusting magnet 49
Is attached to an extension of the casing hole 47 in the casing 20 of the injection unit 15 via the intermediate plate 85. In this case, the casing hole 47 is
5 expands in the area of the outlet to 5 and forms a spring chamber 87. In the spring chamber 87, a return spring 91 tightened between a ring disk of the intermediate plate 85 and a spring receiver 89 of the control valve member 45 is disposed. This return spring 91
The control valve member 45 of the three-way control valve 19 is connected to the second valve seat
Keep in contact with 5.

The control of the adjusting magnet 49 is performed by an electronic control unit 9.
3 is performed. This controller 93 processes operating parameters of the internal combustion engine to be supplied with fuel. The control of the pressure control valve 9 can also be performed via the control device 93.

FIG. 2 shows an enlarged view of the shock absorber 101 constructed according to the present invention. This shock absorber is disposed between the control valve member 45 and the anchor plate 81. The anchor plate 81 is supported via the shock absorbing device 101 so as to be elastically movable or floating with respect to the control valve member 45. The shock absorber 101 is a spring member 1
02, and the spring member 102
Or smaller than the anchor plate 81. Advantageously, the spring member 102 is designed in the form of a strip. The spring element 102 is fixedly connected to the anchor plate 81 by means of a connection 115 which can be disengaged or non-disengageable in the outer edge region, for example a rivet connection or a screw connection. in this case,
A spacer disk 103 is arranged between the spring member 102 and the anchor plate 81. The thickness of the spacer disk 103 determines the distance between the spring member 102 and the anchor plate 81. The spring member 102 is fastened in a central region between the two flexible members 104, 105 with a fixing member 106 configured as a screw and fixed to the control valve member 45. To this end, the screw 106 has a threaded section 107 which engages a threaded hole 110 in the control valve member 45. This threaded section 107 is followed by a cylindrical shaft 108 of increased diameter. As a result, a flexible member 105 disposed between the spring member 102 and the anchor plate 81 is engaged, and the flexible members 104 and 1 are engaged.
The shim disk configured as 05 and the spring member 102 are fixed to the control member 45. A cylindrical shaft 108 followed by a screw head 111 for the fixing screw 106
Are surrounded by the stepped through holes 112 of the anchor plate 81. The through hole 112 is the screw head 11
1 and a first hole 113 and a second hole 114 which are larger in diameter than the cylindrical shaft 108. In this case, the diameter of the second hole 114 is designed to be smaller than the diameter of the screw head 111, so that it forms a shoulder 116 that engages behind the ring section 117 of the screw head 111. In this case, the length of the cylindrical shaft 108 or the length of the second bore 114 is matched to one another such that a distance B is formed between the shoulder 116 and the ring section 117. Furthermore, the thickness of the spacer disk 103 is
Is larger than the thickness of the shim disk 10.
An intermediate chamber A is formed between the base member 5 and the facing body edge of the anchor plate 81. The length of the shaft 108 must be configured in relation to the desired spacing B and the desired spacing A.

The intermediate chamber A forms a spring stroke and the adjusting magnet 4
9 is switched to no current and the control valve member 45 performs a closing movement, thereby determining the damping action when the control valve member 45 is brought into contact with the second valve seat 45 at the second valve sealing surface 47. I do. In the interval B, when it is desired to perform injection, a current is supplied to the electric adjusting magnet 49 by the control device 93, so that the control valve member 45 causes the first valve sealing surface 57 to be moved by the return spring 21 to the first valve sealing surface 57. Determine the degree of spring travel or cushioning when contacting seat 69. Shim disk 104,
The cushioning action of the spring member 102 is determined by the thickness of the shim disks 104, 105 as well as the size of the 105 and the elastic module of the shim disks 104, 105. Further, when adjusting the shock absorber 101, it is necessary to consider the moving mass of the anchor plate 81 and the control valve member 45.

According to the embodiment shown in FIG. 2 with respect to a shim disk 105 which is larger than the shim disk 104, a damping effect of the closing movement of the control member 45 at the end of the injection is provided by the adjusting magnet 49 with a current. Control valve member 4 in the case where
5 is achieved that is greater than the damping effect of the open release movement. Alternatively, the shim disks 104, 105 can be configured to be the same size. Furthermore, in relation to the intended use,
It is also possible to arrange only one shim disk 104 or 105. Further advantageously, the spring member 10 is formed in a rectangular shape.
The jumping operation of the control valve member 45 can be controlled by the thickness and width of the second valve member 2.

The shock absorber 101 can be adapted to act only in one direction of movement, depending on the application. In this case, only the intermediate chamber A or the interval B is provided. Furthermore, instead of the fixing member 106, which is optionally configured as a screw, a spring member 102 and possibly a flexible member 1 are provided.
Other fixing possibilities can be provided to allow fixing of the 04, 105.

The fuel injection device according to the invention works in the following manner: When starting the internal combustion engine, the high-pressure pump 1 transports the fuel from the low-pressure chamber 3 to the high-pressure collecting chamber 7, via a pressure control valve 9. To create an adjustable fuel pressure.

This high fuel pressure is transmitted via the high-pressure line 13 to the individual injection units 15, where it is first connected.
5, the current propagates to the first pressure chamber 33 of the injection valve 17, and no current flows through the electric adjustment magnet 49, and the control valve member 45 of the three-way control valve 19 has the second valve sealing surface. When the three-way control valve 19 is in contact with the second valve seat 65 at 67, the first passage chamber 61, the second passage chamber 63 and the connection passage 43 in the three-way control valve 19 are connected.
And propagates to the second pressure chamber 41 of the injection valve 17 via.
In this case, the injection valve member 21 has a working surface of the piston 38 that is larger than the working surface of the pressure shoulder 31 that restricts the second pressure chamber 41, and is supported in the first pressure chamber 33 and by the valve spring 39. The injection valve 17 is closed because it is held in the valve seat 29.

In the case of injection, the electric adjusting magnet 4
A current flows through the control device 93 through the control device 93, and as a result, the control valve member 45 of the three-way control valve 19 is brought into contact with the second stopper against the force of the return spring 91. That is, the first valve sealing surface 57 is brought into contact with the first valve seat 59,
The connection between the first flow chamber 61 connected to the high-pressure conduit 13 and the second flow chamber 63 connected to the second pressure chamber 41 is closed. During this adjustment movement, the movement of the anchor plate 81 is delayed. This is possible with the spring member 102. As a result, the valve sealing surface 57 of the first valve seat 59 is buffered and collides, so that valve rebound is prevented. In this case, the anchor plate 81 is displaced by the spring stroke indicated by the distance B. In this case, the spring stroke is then followed by the shoulder 116 of the stepped through hole 112.
Is advantageously selected such that it does not contact the ring section 117 of the screw head 111.

At the same time as the control valve member 45 is moved to close the first valve seat 59, the second flow passage chamber 63 is closed.
The connection between the second pressure chamber 41 and the third flow passage chamber 74 formed by the blind hole 73 and connected to the pressure release conduit 77 is controlled to be opened, so that the pressure in the second pressure chamber 41 is reduced. As a result, the outflow from the second pressure chamber 41, throttled by a slight flow cross section in the area 55,
Due to the resulting pressure drop, the first
The force acting on the injection valve member 21 in the pressure chamber 44 is
The injection valve member 21 is moved to the valve seat 29 against the force of the valve spring 39.
, The fuel injection opening 17 is opened, and the fuel is injected into the injection opening 27.
Large enough to be injected from the

When it is desired to terminate the injection, the electric adjusting magnet 49 is switched again to no current through the control device 93, and the control valve member 45 is renewed by the return spring 91, so that the first valve sealing surface 57 is closed. To make contact with the first valve seat 59. Therefore, the second flow chamber 63 is connected to the high-pressure conduit 13 again, and a high pressure is formed again in the second pressure chamber 41 of the injection valve 17 to press the injection valve member 21 to the valve seat 29 at the sealing surface 25. . This high pressure is
7 is kept closed against the pressure in the first pressure chamber 33. In this case, based on the spring stroke formed by the intermediate chamber A, after the closing movement, the anchor plate 81
Can be moved in the closing direction, so that a buffered closing movement is possible. As a result, the control valve member 45 is prevented from jumping from the first valve seat 59 in this case as well. In this case, the damping action is made softer because a larger adjusting force acts. This is particularly true when the flexible member 104 is
This is achieved in that the spring member 102 is configured to be less than 5 so as to allow greater cushioning or greater deflection.

[Brief description of the drawings]

FIG. 1 is a schematic cross-sectional view of a fuel injection unit according to the present invention.

FIG. 2 is an enlarged detailed view of a shock absorber arranged between a control member and an anchor plate.

[Explanation of symbols]

REFERENCE SIGNS LIST 1 fuel high-pressure pump, 3 low-pressure chamber, 7 high-pressure collecting chamber, 9 pressure control valve, 11 return conduit, 13 high-pressure conduit, 15 injection valve unit, 17 injection valve, 1
9 three-way control valve, 21 injection valve member, 23 guide hole, 25 sealing surface, 27 injection opening, 29 valve seat, 31 pressure shoulder, 33 pressure chamber, 37 spring chamber,
39 valve spring, 40 spring receiver, 41 pressure chamber,
42 blind hole, 43 connection passage, 45 control valve member, 47 casing hole, 48 end face, 49 adjusting magnet, 50 ring web, 51 notch, 53
Notch, 55, 56 valve member section, 59 valve seat,
61 Flow chamber, 63 Flow chamber, 65 Valve seat, 67
Valve sealing surface, 69 filling member, 71 tightening screw,
73 blind hole, 74 flow chamber, 75 side hole, 7
7 pressure relief conduit, 81 anchor plate, 85 intermediate plate, 91 return spring, 101 shock absorber, 1
02 spring member, 103 spacer disk, 104,
105 flexible member, 106 fixing member, 107
Screw section, 108 shaft, 109 Ring section, 111 Screw head, 112 Through hole, 11
3 holes, 114 holes, 116 shoulders, 117 ring section

 ──────────────────────────────────────────────────の Continued on the front page (72) Inventor Franz Guggenbichler Golling Tren 4 Austria (72) Inventor Jaroslav Lousek Golling Markt 295 Austria

Claims (14)

[Claims] An injection valve member (21) having at least one injection valve each protruding into a combustion chamber of an internal combustion engine, said injection valve cooperating with a valve seat (29) to control injection. The injection valve member (21) has a pressure surface (31) in a first pressure chamber (33), and the pressure surface (31) is
A second pressure chamber (41) in which the injection valve member is at least indirectly loaded with pressure on the back side opposite to the valve seat (29). ), And the first pressure chamber (33) has a high-pressure conduit (1).
3) is always connected to the high-pressure collecting chamber (7) via a connection conduit (35) to the electric control device (9).
3) a three-way control valve (19) controlled by an adjusting magnet (49), the two-way control valve (19) cooperating with one valve seat (59, 65) each; A control valve member (45) having (57, 67), said control valve member (45) being in one position and one valve seat (4).
9) with one sealing surface (57) to close the connection of the high pressure conduit (13) to the second pressure chamber (41) and to connect the second pressure chamber (41) to the pressure relief conduit (77). A position for opening the connection and for opening or closing this connection in the other position, wherein said control valve member (45) makes a connection of the second pressure chamber (41) to the pressure relief conduit (77). In a fuel injection unit of the type which forms a free connection in both flow directions, which restricts the throttle cross-section and is not throttled from the second pressure chamber (41) to the high-pressure conduit (13) at the other position. The control valve member (45);
An end facing the adjusting magnet (49) and a control valve member (45)
A shock absorber (101) is provided between the control valve member (45) and the control valve member (45) in at least one direction of movement of the control valve member (45). A fuel injection unit characterized by buffering the closing process of (45). 2. A spring member (10) in which said shock absorber (101) is fixedly connected on the one hand to said control valve member (45) and on the other hand to said anchor plate (81).
2. The fuel injection unit according to claim 1, comprising (2). 3. The control valve member (45), wherein the spring member (102) is configured as a spring plate arranged substantially parallel to the anchor plate (81) and by means of fixing means (106), preferably by screws. 3. The fuel injection unit according to claim 2, wherein 4. The spring plate (102) is connected to the anchor plate (8) by coupling means (115) in the outer edge region.
4. The fuel injection unit according to claim 3, wherein the fuel injection unit is fixed to (1) and at least one spacer member (103) is provided between the anchor plate (81) and the spring plate. 5. At least one flexible member (10)
4, 105) are arranged parallel to said spring member (102) and are positioned relative to said control valve member (45) via fixing means (106).
The fuel injection unit according to any one of claims 1 to 4. 6. The control member (45) wherein the spring member (102) is located between two flexible members (105, 106).
The fuel injection unit according to claim 5, wherein 7. The thickness of the spacer member (103) is greater than the thickness of a flexible member (105) disposed between the spring member (102) and the anchor plate (81). 4. The fuel injection unit according to claim 3, wherein the spring stroke is adjustable in one of the directions of movement of the control member (45) in the intermediate chamber (A) formed thereby. 8. An aperture (1) in which said anchor plate (81) is stepped for receiving a fixing means (106).
02), the first hole (113) and the second hole (11).
4) a fixing means (106) having a diameter disposed therein.
The fuel injection unit according to claim 3, wherein the fuel injection unit is configured to be larger than the fuel injection unit. 9. The fixing member (106) has a cylindrical shaft (108) which is configured as a screw and which follows the screw head (111) and has a reduced diameter. To the threaded section (107), which is configured smaller, and the shaft range (10
The fuel injection unit according to any one of claims 3 to 8, wherein a length of the intermediate chamber (A) and the second hole (114) is larger than a length of the intermediate chamber (A) and the second hole (114). 10. The stepped through-hole (112) has a shoulder (116), said shoulder (116) being attached to the shaft (10).
8) with a distance (B) to a ring section (117) formed between the screw head (111) and thereby adjustable for a second direction of movement of the control valve member (45). The fuel injection unit according to claim 8, wherein: 11. The fuel injection system according to claim 2, wherein the stiffness of the spring member (102) is adjustable in relation to the size of the flexible member (104, 105). unit. 12. The rigidity of the spring element (102) depends on the thickness of the spring element and in particular on the flexible element (104, 10).
12. Adjustable by the thickness of 5).
The fuel injection unit according to claim 1. 13. The method according to claim 1, wherein the spring travel of the control valve member is adjustable by the size of the intermediate chamber and the distance. Fuel injection unit. 14. The reciprocating motion of the control valve member (45) depends on the mass of the anchor plate (81) and the shock absorber (101) and the free spring stroke between the intermediate chamber (A) and the interval (B). 14. The fuel injection unit according to claim 1, which is adjustable in both directions.