KR101736081B1 - Electromagnetically actuated volume control valve for controlling the delivery volume of a high-pressure fuel pump - Google Patents

Abstract

The present invention relates in particular to an electromagnetically actuated capacity control valve for controlling the delivery rate of a high-pressure fuel pump. The capacity control valve includes a moving chamber 28 that can be filled with fuel 30, a moving part 22 of the electromagnetic actuating device and a stopper 26 disposed in the moving chamber. A contact surface is provided between the moving part 22 and the stopper 26 when the moving part contacts the stopper 26. [ The contact surface is defined by the surface of the moving part 22 and the surface of the stopper 26. The contact surface is smaller than the entire surface of the moving part 22 or the stopper 26. [

Description

TECHNICAL FIELD [0001] The present invention relates to an electromagnetic operated capacity control valve for controlling the discharge amount of a high-pressure fuel pump. BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an electromagnetically-

The present invention relates to an electromagnetically operated capacity control valve according to the preamble of claim 1.

Capacity control valves including an electromagnetically actuated valve member are disclosed in the art. The amount of fuel supplied to the high-pressure fuel pump in the fuel injection system of the internal combustion engine by the valve can be influenced.

It is known to arrange, for example, a longitudinal bore in an armature of an electromagnet so as to be able to control the damping that appears when moving the armature. Fluid, i.e. fuel, is delivered from the axial side of the armature to the other side through the axial bore in the armature. As an alternative to the axial bore in the armature, it is known to provide an axial groove in the circumferential wall of the armature, which allows fluid exchange between the two sides of the armature.

It is an object of the present invention to provide an electromagnetically operated capacity control valve for controlling the discharge amount of a high pressure pump, which can ensure an accurate delivery amount over the entire lifetime and over a short operation time.

The above problem is solved by the electromagnetic operated capacity control valve according to claim 1.

An electromagnetic operated capacity control valve according to claim 1 is provided by the present invention. Preferred improvements are set forth in the dependent claims. Further, the main features of the present invention are set forth in the following detailed description and drawings, which individually and variously combined features may be important to the present invention and are not mentioned in further detail in this regard.

The capacity control valve according to the present invention includes an armature movable in two directions in a housing section, the movement direction being limited by a stopper. The housing section may be filled with fluid. When the armature contacts the stopper, a contact surface defined by the upper surface of the armature, which is two contact members, and the stopper is formed, and the contact surface is smaller than the entire surface of the armature or stopper.

An advantage of the present invention is that a pressure pad is formed with the fluid prior to contact with the area of the contact surface upon entry movement, that is, when the armature moves onto the stopper, and the pressure pad reduces the travel speed before the armature impacts the stopper. This effect is called the squeeze effect.

Another advantage of the present invention is that the armature moves from the stopper to the stopper when the armature is in contact with the stopper. A volume is formed in the area of the contact surface, and the volume is refilled with fluid. The reduction of the contact surface relative to the entire surface of the armature or stopper allows the reduction of the so-called hydraulic bonding of the armature to the stopper and, consequently, the reduction of the switching time.

The NVH characteristics (NVH = Noise, Vibration, Harshness) of the capacity control valve, that is, noise, vibration and noise characteristics can be positively influenced by the reduction of the hydraulic adhesion when the intake delay is moved and the collision delay is increased.

The collision delay reduces the pressure pulsation during the intake stroke. Bouncing pulses, ie, multiple collisions during entry movement, are minimized by the elasticity of the associated components. The reduction of the cavitation phenomena is achieved by a pressure change damped over time and by a decrease in the tendency of the pressure difference to appear locally abruptly.

Particularly in terms of the size and shape of the contact surfaces, a trade-off between impact damping and reduced hydraulic bonding is achieved by the design of the respective surfaces of the armature and stopper.

In addition, the advantages described above achieve low intensity critical loads and weak corrosion and extended service life of the associated components such as weld seams, sleeves, and the like.

This makes it possible to ensure accurate delivery over the entire lifetime as well as accurate delivery over short operating hours.

In a preferred embodiment of the capacity control valve, the ventilation volume connected to the axial channel in the armature results in a rapid recharge of the volume formed in the area of the contact surface during withdrawal movement. The ventilation volume is also desirable for incoming movement because the fluid in the area of the contact surface can be quickly ejected.

In another preferred embodiment of the displacement control valve, a dancing volume is provided which, when the armature contacts the stopper, is contained between the two contacts and does not include a connection to the axial channel. The dead volume causes the fluid in the dead volume to be blocked just before the armature comes into contact with the stopper to act as a pressure pad between the armature and the stopper. Thus, a strong end position damping by the dead volume acting as a pressure pad by the small contact surface is achieved.

In a preferred embodiment of the capacity control valve, a first ventilating volume is disposed radially inwardly of the contact surface, and a second ventilating volume is radially disposed outside the contact surface. That is, the fluid can be discharged on two sides, i.e., radially inward and radially outwardly, upon entry movement. The above advantages also appear when moving out. The volume formed in the area of the contact surface can be refilled from two sides and the hydraulic bonding effect is further reduced.

In a preferred refinement of the capacity control valve, an embodiment is embodied which comprises first and second ventilation volumes such that the two ventilation volumes are connected via a connection and only one of the ventilation volumes is connected to the inlet of the axial channel. This allows ventilation of two ventilation volumes to be ensured and no other axial channel with inlet in the two ventilation volumes is required.

In another preferred embodiment of the capacity control valve, the surface of the armature or stopper is non-magnetic. This results in magnetic separation, and when the armature contacts the stopper, the separation of the two contacts is only possible with a lot of force. In addition, nonmagnetic materials can have higher strength than amateur or stopper materials, which increases wear resistance and lifetime of the capacity control valve.

In a preferred embodiment of the capacity control valve, the condition of the surface corresponding to the contact surface is characterized by profiling. The profiling can precisely control the squeeze effect and hydraulic bonding, ie, the movement of the inlet and outlet in the contact area of the armature and the stopper.

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.

1 is a schematic view of a fuel injection system of an internal combustion engine;
FIG. 2A is a schematic cross-sectional view of a (coilless) electromagnet of a capacity control valve at the time of entry movement; FIG.
Fig. 2b is a cross-sectional view of the electromagnet (without coils) of Fig. 2a when pulling out. Fig.
Figure 3a is a cross-sectional view according to Figure 2a, including an armature having a circular contact surface;
Figure 3b is an axial plan view in direction IIIa towards the armature according to Figure 3a.
Figure 4a is a cross-sectional view according to Figure 2a including a stopper having a circular contact surface.
Figure 4b is an axial plan view in direction IIIb towards the stopper according to Figure 4a;
Figure 5a is a cross-sectional view according to Figure 2a including an armature having a circular contact surface.
Figure 5b is an axial plan view in direction IIIa towards the armature according to Figure 5a;
6A is a cross-sectional view according to FIG. 2A including an armature having a circular contact surface. FIG.
Fig. 6b is an axial plan view in direction IIIa towards the armature according to Fig. 6a. Fig.
7A is a cross-sectional view according to FIG. 2A including an armature having a circular contact surface and a groove; FIG.
Figure 7b is an axial plan view in direction IIIa towards the armature according to Figure 7a;
8 is a sectional view of the stopper body.
9 is a sectional view of the stopper armature.
10A is a sectional view of a stopper armature.
FIG. 10B is an axial plan view of the stopper body according to the direction IIIb of FIG. 10A. FIG.

Members and sizes having the same function in all the drawings have the same reference numerals.

1 schematically shows a fuel injection system 1 of an internal combustion engine. The fuel tank 9 is connected to the high pressure pump 3 (not shown in detail) through the suction line 4, the preliminary delivery pump 5 and the low pressure line 7. Pressure accumulator 13 ("common rail") is connected to the high-pressure pump 3 through the high-pressure line 11. A capacity control valve 14 having an electromagnetic actuating device 15 also referred to hereinafter as an electromagnet 15 is hydraulically disposed in the path of the low pressure line 7 between the preliminary delivery pump 5 and the high pressure pump 3. Other members, such as the valves of the high-pressure pump 3, are not shown in Fig. The capacity control valve 14 may be formed as a unit including the high-pressure pump 3. The inlet valve of the high-pressure pump 3 can be forcibly opened by the capacity control valve 14, for example.

In operation of the fuel injection system 1, the pre-delivery pump 5 delivers fuel from the fuel tank 9 to the low-pressure line 7. The capacity control valve 14 determines the amount of fuel supplied to the high-pressure pump 3.

2A schematically shows a portion of a capacity control valve 14 or electromagnet 15. The members shown in FIG. 2A have a rotationally symmetric shape substantially centering on the central longitudinal axis of the housing section 20.

There is shown a valve member 24 fixedly connected to the armature 22 and an armature 22 movable substantially in the direction of the longitudinal axis, which may be referred to as a hollow cylindrical housing section 20 and a generally movable section in the housing section. The housing section 20 is limited by the stopper 26 in the right-hand portion of the figure. Fluid 30, not shown in the figures, is provided on two sides of the armature 22 in the armature chamber 28, which is formed in the housing section 20 and is generally referred to as a transfer chamber. An annular ring gap 36 is disposed between the inner circumferential wall 32 of the housing section 20 and the outer circumferential wall 34 of the armature 22 and the ring gap is shown in an oversized dimension.

The armature 22 here includes four axial channels 38, only two of which are shown in the cross-section of Figure 2a. The channels 38 may be embodied as bores in the armature 22 as shown or as grooves on the circumferential wall 34 of the armature 22 as shown.

The end face of the armature 22 at the end position in the direction of the arrow 42 is disposed directly on the stopper 26 in the contact surface area. The contact surface is defined by the end side surface of the armature 22 in the arrangement according to Figure 2a and is only interrupted by the inlet of the channel 38.

The contact surface generally comprises an overlapping surface of the armature 22 and the stopper 26. The individual surfaces may have different surface shapes, such as concave, convex or corrugated surface shapes, as opposed to the substantially parallel planes shown in FIG. 2A, so that the surfaces are fitted to each other at the time of contact to form a contact surface.

In the operating position of the electromagnet 15 shown in Fig. 2A, the armature 22 is moved with the valve member 24 to the right in the figure, which corresponds to the incoming movement. This is shown by arrow 42. The incoming movement is characterized in that the moving part, here the armature 22, is moved over the non-moving part, here the stopper 26. After the armature 22 contacts the stopper 26, the armature 22 separates from the stopper 26 or moves away. This is the withdrawal movement. The opening or closing of the valve does not imply an incoming or outgoing movement.

The entire surface of the armature 22 on the end side, that is, the side surface facing the stopper 26, corresponds to the plan view seen in the direction IIIa. The plan view does not take into account the inlet of the axial channel 38 and the ring gap 36. In the case of the stopper 26, there is another plan view as seen in the direction IIIb and therefore another entire surface. Thus, the entire surface is defined by the direction of the opposite contact, here the plan view seen from the armature 22 or the stopper 26.

The volume of the partial section 44 of the armature chamber 28 is constantly reduced. Whereby the fluid 30 in the partial section 44 is discharged. In this case, the fluid 30 flows out of the partial section 44 along the arrow 46.

The so-called squeeze effect is achieved by the viscosity of the fluid 30 and by the movement of the armature 22 in the direction of the arrow of the stopper 26. The squeeze effect means that the fluid 30 is prevented from being discharged. This is illustrated by the double arrow 48 in Fig. The impact damping of the armature 22 becomes possible by the squeeze effect. That is, the armature 22 can be moved over the stopper 26 at a high speed, and the collision of the armature 22 over the stopper 26 is damped by the squeeze effect and thereby the pressure pad.

The squeeze effect depends on the contact surface between the armature 22 and the stopper 26. The pressure pad extends between the overlapping surfaces of the armature 22 and the stopper 26 along the double arrow 48 shown in the capacity control valve 14 shown in Fig. 2A. 2A, the surfaces of the armature 22 and the stopper 26 are completely overlapped except for the inlet of the ring gap 36 and the axial channel 38. As shown in Fig.

The operating state of FIG. 2B corresponds to the pulling movement according to the arrow 43 opposite to the pulling movement of FIG. 2A. 2A and 2B, the armature 22 collides with the stopper 26. As shown in Fig. A volume is formed in the contact surface area between the armature 22 and the stopper 26 again after the impact according to the operating state of Fig. The volume is filled with fluid (30) through axial channel (38) along arrow (47). Depending on the viscosity of the fluid 30 and the profile of the armature 22 and the stopper 26, so-called hydraulic bonding can be made, which makes the pulling movement difficult.

Only the incoming movement is shown in the following figures.

The cross-sectional view of FIG. 3a simply shows the portion of the capacity control valve 14 with the electromagnet 15, following the basic diagram of FIG. In this case, the armature 22 includes a cylindrical protrusion 62 having a circular surface 60. Circular surface 60 defines a contact surface. The surface 60 is smaller than the entire surface of the armature 22.

The material of one of the surfaces of the armature 22 or the stopper 26 forming the contact surface is implemented non-magneticly. This can be done, for example, by chromium plating to form a wear resistant surface.

The surface 60 may have a different shape than that of FIG. 3A, in which case the oppositely disposed stopper 26 has a corresponding shape that accommodates the shape of the surface 60. For example, the surface can have a concave shape, and the stopper can have a convex shape in the corresponding area.

The surface 60 may also be formed to provide a gap between the armature 22 and the stopper 26 upon contact. For example, if a radially outwardly spaced gap is provided between the surface 60 and the stopper 26 in the area of the contact surface, a gap occurs radially outward. The gap allows the fluid to flow from the volume radially disposed outside the contact surface into the area of the contact surface and allows the hydraulic attachment to be inhibited or reduced. Despite the gap, a squeeze effect can be used when moving in.

Surface 60 is characterized by profiling. The surface can be implemented differently. For example, concentric profile profiling makes it difficult for the fluid 30 to flow in the radial direction during entry and exit movement. That is, unlike a smooth surface, the hydraulic pressure bonding is more strongly exhibited when the pressure pad and the withdrawal are moved during the intake movement.

Alternatively, the profiling, starting from the center point of the surface in the form of a radiation, facilitates the flow of the fluid 30 in the radial direction during entry and exit movement. That is, unlike a smooth surface, the hydraulic pressure adherence is weaker when the pressure pad and the withdrawal movement are made during the intake movement.

Figure 3b shows an axial plan view of the armature 22 in direction IIIa according to Figure 3a. Only the upper half of the armature 22 is shown for illustration purposes. Only the lower section not shown is mirror-symmetrically disposed relative thereto. 3B shows a cylindrical protrusion 62 having an axial channel 38 and a circular surface 60. The cylindrical protrusion 62 shown in Fig. Also shown is a half of the double arrow 48 representing the pressure pad. The circumferential wall 34 limits the armature 22.

3A is as follows: The operating state of FIG. 2A, that is, the armature 22 including the valve member 24 according to the drawing movement, is moved to the right in the drawing along arrow 42. The volume of the partial section 44 of the armature chamber 28 is constantly reduced and the fluid flows out of the partial section 44 along the arrow 46.

A squeeze effect appears between the overlapping portion of the surface of the stopper 26 and the circular surface 60. A pressure pad is formed along the arrow 48 by the squeeze effect, thereby ensuring collision damping of the armature 22. The pressure pad is formed only in the area of the smaller contact surface rather than the entire surface area of the armature 22 because the surface 60 is smaller than the entire surface of the armature 22. [

A volume is formed in the area of the contact surface defined by the circular surface 60 when the amateur 22 is not shown in the drawing. The volume is filled by the ventilation volume 65 radially outward, in which case the ventilation volume 65 is again filled by the axial channel 38. As the surface 60 is smaller than the entire surface of the armature 22, the hydraulic bonding is reduced compared to Figures 2A and 2B.

Therefore, the contact surface of FIG. 3A reduced in size as compared with FIG. 2A can reduce the collision speed when the armature 22 is moved in and out by the squeeze effect, and the hydraulic adhesion is reduced when the armature 22 is pulled out by the ventilation of the contact surface .

The cross-sectional view of Figure 4a is a simplified view of the portion of the capacity control valve 14, following the basic diagram of Figure 2a. The stopper 26 includes a cylindrical protrusion 62 having a circular surface 60. The circular surface (60) is smaller than the entire surface of the stopper (26). Therefore, the contact surface is reduced as compared to FIG. 2A as in FIGS. 3A and 3B.

4B shows an axial plan view of the stopper 26 according to direction IIIb of Fig. 4A, with a cylindrical projection 62 and a circular surface 60. Fig. Also shown is a half of the double arrow 48 representing the pressure pad. The inner circumferential wall 32 of the housing section 20 limits the illustrated top view of the stopper 26.

The operating state of Figure 4A substantially corresponds to the operating state of Figure 3A. An unillustrated withdrawal movement corresponds substantially to the description of Figs. 3A and 3B.

The cylindrical protrusion 62 and the circular contact surface 60 are formed in the armature 22 in Figures 3a and 3b and in the stopper 26 unlike those in Figures 4a and 4b. The contact surface and the pressure pad can be achieved according to the double arrows 48 of FIGS. 3A-4B, i.e., by opposing profiling of the armature 22 and the stopper 26. Thus, the following embodiments can also be achieved by the opposite form or profiling of the contact portions with approximately the same function with respect to the contact surface and the pressure pad. Any venting through the axial channel 38 in addition to profiling can also be considered.

The cross-sectional view of FIG. 5A, following the basic diagram of FIG. 2A, simply illustrates the portion of the capacity control valve 14 with the electromagnet 15. In this case, the armature 22 includes a hollow cylindrical projection 64 having a circular surface 61 and axial channels 38 are disposed radially outwardly of the hollow cylindrical projection 64. The surface 61 in the form of a circular ring is smaller than the entire surface of the armature 22.

The contact surface of Fig. 5A is smaller than the contact surface of Fig. 3A, and the cylindrical protrusion 62 of Fig. 3A and the hollow cylindrical protrusion 64 of Fig. 5A have the same outer diameter.

Also provided by the hollow cylindrical projection 64 is a restricted volume 66.

5B shows an axial plan view of the armature 22 according to the direction IIIa according to FIG. 5a, including a cylindrical projection 64, a circular ring-shaped surface 61 and a dead volume 66. FIG. The armature 22 is limited by the circumferential wall 34 and includes an axial channel 38. Arrow 48 represents the pressure pad.

The operating state of Figure 5A substantially corresponds to the operating state of Figure 2A. Immediately before the armature 22 contacts the stopper 26, the fluid 30 in the dead volume 66 is blocked by the ventilation volume 65 disposed outside the radial direction. This causes the fluid 30 in the dead volume to additionally act as a pressure pad, thus exhibiting a similar action as in the circular surface 60 according to Figures 3a and 3b. That is, in this case, the surface acting as the pressure pad is larger than the contact surface.

An unillustrated withdrawal movement corresponds substantially to the description of FIG. 3B, and the filling of the area of the contact surface and the included dead volume 66 is effected by the ventilation volume 65 radially outward similarly to FIG. 3b.

The cross-sectional view of Figure 6a is a simplified view of the portion of the capacity control valve 14 with the electromagnet 15, following the basic diagram of Figure 2a. In this case the armature 22 comprises a hollow cylindrical projection 64 with a surface 61 in the form of a circular ring and the axial channels 38 are arranged radially inside the hollow cylindrical projection 64. The surface 61 in the form of a circular ring is smaller than the entire surface of the armature 22.

6B shows an axial plan view of the armature 22 along the direction IIIa according to FIG. 6a with a hollow cylindrical projection 64 and a circular ring shaped surface 61. FIG. The armature 22 is limited by the circumferential wall 34 and also includes an axial channel 38 radially inside the hollow cylindrical projection 64. Arrow 48 represents the pressure pad.

6A is as follows: A pressure pad along the double arrow 48 is formed immediately before the armature 22 comes into contact with the stopper 26 as the armature 22 moves in the direction of the arrow 42. A ventilation volume 65 is provided inside the circular ring shaped surface 61 in the case of the inlet of the axial channel 38 radially arranged inside the hollow cylindrical projection 64. The armature 22 does not have a dancing volume 66 as in Figures 5a and 5b and the fluid 30 can be discharged radially in the interior of the hollow cylindrical projection 64 through the axial channel 38 have. Since the surface 61 in the form of a circular ring is blocked by the ring gap 36, the fluid 30 is prevented from moving in substantially one direction only when the armature 22 contacts the stopper 26, Can be discharged.

An embodiment of the armature 22 for unillustrated withdrawal movement is characterized in that the volume formed in the area of the surface 61 in the form of a circular ring at the time of withdrawal movement is radially inside the hollow cylindrical projection 64, 65, respectively. The ventilation volume 65 is filled through the channel 38.

The cross-sectional view of Figure 7a is shown similar to the cross-sectional view of Figure 5a, but has an additional groove 68 in the hollow cylindrical projection 64 of the armature 22. The surface 61 in the form of a circular ring is interrupted by the radial grooves 68. The armature 22 includes only two axial channels 38 in this case. The surface 61 in the form of a circular ring is smaller than the entire surface of the armature 22.

7B shows an axial plan view of the armature 22 along the direction IIIa according to FIG. 7A, including the hollow cylindrical projection 64, the interrupted circular ring shaped surface 61, and the radial groove 68. FIG. The armature 22 is restricted by the circumferential wall 34 and has an axial channel 38 radially outwardly of the hollow cylindrical projection 64. The double arrow 48 represents the pressure pad.

The operating state of FIG. 7A substantially follows the description of FIG. 5A. 5A and 5B, the surface acting as a pressure pad is reduced by replacing the dead volume 66 of FIGS. 5A and 5B in the form of the central first ventilation volume 67 inside the hollow cylindrical projection 64. [ Whereby the fluid 30 in the hollow cylindrical projection 64 can be discharged to the channel 38 through the second ventilation volume 65 disposed radially outwardly of the hollow cylindrical projection 64. Whereby the surface acting as a pressure pad is the same as the contact surface.

The arrows 76 in Figure 7b show how the fluid 30 exits the first ventilation volume 67 and into the second ventilation volume 65 upon entry of the armature 22, Is displayed.

The volume created in the area of the contact surface 61 in the form of a circular ring in the unillustrated withdrawal of the armature 22 is radially filled in from two directions: on the one hand, the second ventilation volume 65 outside the radial direction On the other hand radially inwardly through the first ventilation volume 67 or through the axial channel 38 and the groove 68 to the fluid 30 following the axial channel 38, (30).

Fig. 8 simply shows a section of the capacity control valve 14. Fig. A housing section 20 is shown in which the armature 22 is connected to a valve member 24 as in Fig. A stopper body 73 having a stopper 27 fixedly connected to the housing section 20 is shown. The contact surface between the armature 22 and the stopper 27 along the arrow 48 is smaller than the entire surface of the armature 22.

The withdrawal movement of the valve member 24 including the armature 22 is characterized in that the armature 22 is moved onto the stopper 27 in the direction of the arrow 43. A pressure pad according to the double arrow 48 is formed before the armature 22 collides or contacts between the armature 22 and the stopper body 73. Fluid 30 may in this case be vented along arrow 46 through ventilation volume 65 and channel 38.

The volume between the contact surfaces between the armature 22 and the stopper 27 when the armature 22 is moved away from the stopper 27 is not filled with the fluid 30 again Should be. To this end, the fluid 30 flows out of the ventilation volume 65 and the channel 38.

9 shows a portion of the displacement control valve 14 that includes two fixed stopper bodies 73 with stoppers 26 and 27 which stopper armature 72 fixedly connected to the valve member 24 To restrict the movement of the valve member 24. The stopper armature 72 can be moved along the longitudinal axis in the housing section 20. The valve member 24 is connected to the armature 22 in a manner not shown, in which case the armature 22 is disposed on the right side according to FIG. The contact surface in the form of a circular ring between the stopper armature 72 and the stopper 26 according to the arrow 48 is smaller than the entire surface of the stopper armature 72 due to the ventilation volume 65 in the stopper body 73. [

9 shows, for example, an instant before the stopper armature 72 contacts the stopper 26, that is, an incoming movement. In this case, the pressure pad is formed between the overlapping surfaces of the stopper armature 72 and the stopper 26 or the stopper body 73 according to the double arrow 48, and the fluid 30 passes through the ventilation volume 65, (28). Similarly, in contrast to the arrow 42, the pressure pad is formed in the stopper 27 when the valve member 24 is moved.

The volume between the stopper armature 72 and the stopper 26 formed in the contact surface area as a result of the unillustrated withdrawal of the stopper armature 72 from the stopper 26 as opposed to the arrow 42 is reduced from the ventilation volume 65 Is filled with the fluid (30).

10A schematically shows a section of the capacity control valve 14, or the electromagnet 15. A housing section 20 is shown and a stopper armature 72 is shown having a circumferential wall 74 that is movable along the longitudinal axis in the housing section. The movable stopper armature 72 is fixedly connected to the valve member 24. The valve member 24 is radially guided by the fixed stopper body 73. The inner circumferential wall 78 of the stopper body 73 restricts the guide gap 79 for guiding the valve member 24 by the outer circumferential wall 80 of the valve member 24. The guide gap is shown in excess size.

The stopper body 73 is characterized in that it includes a conical diameter step 82 in the direction IIIa, i.e. in the direction of the stopper armature 72. [ The conical diameter step 82 corresponds to the extension of the inner diameter in the direction IIIa from the circumferential wall 78 and extends to the stopper 26. [ The stopper body 73 also has a groove 68 on the side facing the stopper armature 72.

The groove 68 extends radially from the diametric step 82 through the diameter of the circumferential wall 74 of the stopper armature 72 to the circumferential wall 32 of the armature chamber 28. The groove 68 connects the ventilation volume 65 in the diametric step 82 to the armature chamber 28. A contact surface in the form of a circular ring, which is interrupted by the groove 68, is provided by the diameter step 82 and the groove 68. The contact surface is smaller than the entire surface of the armature 22.

Fig. 10B shows an axial plan view of the stopper body 73 and a cross section of the valve member 24 in the direction IIIb according to Fig. 10a. The radial support of the valve member 24 is shown as a guide gap 79 limited by the circumferential walls 78, 80. The stopper body 73 extends from the circumferential wall 78 through the diameter step 82 to the stopper 26 in the radial direction. The arrow 48 represents the pressure pad and is represented by the illustrated circumferential wall 74 of the stopper armature 72 in the form of a circular ring shaped contact surface interrupted by the groove 68.

10A and 10B are as follows: The stopper armature 72 is moved over the stopper 26 and the stopper body 73 by the valve member 24 in the form of an inflow movement. A circular pressure pad is formed along the contact surface and double arrow 48 which is interrupted by the groove 68 by the fluid 30 just before the stopper armature 72 contacts the stopper 26. [ The abutted circular ring contact surface is reduced by the diameter step 82 and corresponds to the overlapping surface of the stopper 26 and the stopper armature 72. The fluid 30 in the area of the diametric step 82 when the stopper armature 72 contacts the stopper 26 passes through the groove 68 through the venting volume 65 along the arrow 76 into the armature chamber 28 Can be discharged. So that the fluid does not act as a pressure pad in the diameter step (82) and in the groove (68). The fluid 30 can not be substantially discharged through the guide gap 79.

The volume formed in the area of the contact surface in the form of a circular ring, which is not shown in the drawing movement, which is not shown, is filled with the fluid 30 by the ventilation volume 65 radially inward and outward. The fluid 30 flows out of the radial direction through the armature chamber 28. The fluid 30 also flows through the inwardly positioned diameter step 82 and groove 68.

14 Capacity control valve
15 Actuator
22 moving part
26, 27 Stopper
38 channels
65 Ventilation volume
66 Dance volume
72 moving part

Claims (8)

An electromagnetic operated capacity control valve (14) for controlling the delivery rate of a high pressure pump (3), said capacity control valve (14) comprising a moving chamber (28) which can be filled with a fluid (30) Moving parts 22 and 72 of the electromagnetic actuating device 15, and stoppers 26 and 27,
A contact surface is provided between the moving part (22, 72) and the stopper (26, 27) when the moving part (22, 72) contacts the stopper (26, 27) (22, 72) or the surfaces of the stoppers (26, 27), wherein the contact surface is defined by an electromagnetic operated In the capacity control valve,
Axial channels 38 connecting the areas of the moving chamber 28 arranged toward two sides of the moving part 22 are provided in the moving part 22 and 72 and the moving part 22 , 72) is provided with a ventilation volume (65) which can be filled through the channels (38) when the stoppers (26, 27)
The axial channels 38 are located outside the radial direction of the hollow cylindrical projection 64 and the contact surface is formed in the shape of a circular ring on the hollow cylindrical projection 64,
Wherein the ventilation volume (65) is between the moving part and the stopper (26, 27). delete 2. A method according to claim 1, characterized in that the dead volume (66) can not be ventilated when the moving part (22) contacts the stoppers (26, 27) and the dead volume (66) Wherein the electromagnetic control valve is a solenoid valve. 2. The electromagnetic operated displacement control valve according to claim 1, wherein ventilation volumes (65, 67) are provided radially and radially inwardly of the contact surface. 5. A device according to claim 4, characterized in that the first ventilation volume (67) is capable of being filled with fluid (30) from the second ventilation volume (65) via the connection (38, 68) Electromagnetic-operated capacity control valve. 4. The electromagnetically actuated capacity control valve according to claim 1 or 3, wherein one of the surfaces of the contact surface is made of a non-magnetic material. 4. The electromagnetic operated capacity control valve according to claim 1 or 3, wherein the surface included in the contact surface is profiled to have a predetermined pattern. A high-pressure fuel pump (3) comprising a displacement control valve (14) according to claims 1 or 3.

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