EP2519732B1 - Electromagnetically actuated metering control valve, particularly for controlling the flow of a high pressure fuel pump - Google Patents
Electromagnetically actuated metering control valve, particularly for controlling the flow of a high pressure fuel pump Download PDFInfo
- Publication number
- EP2519732B1 EP2519732B1 EP10778969.5A EP10778969A EP2519732B1 EP 2519732 B1 EP2519732 B1 EP 2519732B1 EP 10778969 A EP10778969 A EP 10778969A EP 2519732 B1 EP2519732 B1 EP 2519732B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- stop
- armature
- contact surface
- control valve
- movement
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Links
- 239000000446 fuel Substances 0.000 title claims description 10
- 230000033001 locomotion Effects 0.000 claims description 65
- 239000012530 fluid Substances 0.000 claims description 42
- 238000013022 venting Methods 0.000 claims description 15
- 239000000696 magnetic material Substances 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 description 16
- 230000000694 effects Effects 0.000 description 14
- 238000013016 damping Methods 0.000 description 4
- 238000002347 injection Methods 0.000 description 4
- 239000007924 injection Substances 0.000 description 4
- 238000009423 ventilation Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 238000011161 development Methods 0.000 description 2
- 230000018109 developmental process Effects 0.000 description 2
- 239000002828 fuel tank Substances 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- VYZAMTAEIAYCRO-UHFFFAOYSA-N Chromium Chemical compound [Cr] VYZAMTAEIAYCRO-UHFFFAOYSA-N 0.000 description 1
- 241001104043 Syringa Species 0.000 description 1
- 235000004338 Syringa vulgaris Nutrition 0.000 description 1
- 238000004026 adhesive bonding Methods 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000003628 erosive effect Effects 0.000 description 1
- 238000007885 magnetic separation Methods 0.000 description 1
- 230000013011 mating Effects 0.000 description 1
- 238000007747 plating Methods 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/20—Varying fuel delivery in quantity or timing
- F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
- F02M59/366—Valves being actuated electrically
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
- F02M59/46—Valves
- F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
Definitions
- the invention relates to an electromagnetically actuated quantity control valve according to the preamble of claim 1.
- quantity control valves which have an electromagnetically actuated valve element.
- the amount of fuel supplied to a high-pressure pump can be influenced in the fuel injection system of an internal combustion engine.
- armature of the electromagnet for example, with longitudinal bores in order to adjust the damping occurring during the movement of the armature can. Through such axial bores in the armature fluid, so fuel, transported from one axial side of the armature to the other side.
- the invention provides an electromagnetically actuated quantity control valve according to claim 1.
- Advantageous developments are specified in subclaims.
- important features can be found also in the following description and in the drawings, the features both alone and in different combinations may be important for the invention, without being explicitly referred to again.
- the quantity control valve according to the invention has a movable in a housing portion in two directions armature, wherein a direction of movement is limited by a stop.
- the housing section can be filled with fluid. If the armature bears against the stop, there is a contact surface which is determined by the surfaces of the two contact elements, the armature and the stop, and which is smaller than the total area of the armature or stop.
- An advantage of the invention is that during an attraction movement, i. a movement of the armature on the stop, in the region of the contact surface before the application in conjunction with the fluid forms a pressure cushion, which reduces the speed of movement before the impact of the armature against the stop. This effect is called squeezing effect.
- Another advantage of the invention is evident in a peel, i. a movement of the armature away from the stop, starting from a concern of the armature against the stop. In the area of the contact surface, a volume is created, which is then refilled with the fluid.
- the reduction of the contact area compared to the total area of the armature or stop makes it possible to reduce a so-called hydraulic sticking of the armature to the stop, and thus to reduce switching times.
- NVH Noise, Vibration & Harshness
- the impact delay reduces the pulsation of the pressure during the tightening movement.
- Preller ie a multiple impact in the tightening movement by resilient properties of the components involved, are minimized.
- a reduction of cavitation tendency is due to the time damped pressure curve and thus a slight tendency to locally suddenly occurring pressure differences achieved.
- the design of the respective surfaces of the armature and the stop especially with regard to the size and shape of the contact surfaces, a compromise between the impact attenuation and the reduced hydraulic bonding is achieved.
- a low strength-critical load and low erosion and thus increased life of the components involved such as welds, sleeves, or similar. is reached. This also makes it possible to guarantee an exact delivery rate over the entire service life as well as over short operating times.
- a venting volume which is connected to an axial channel within the armature, leads to a rapid refilling of the volume arising in the region of the contact surface during the withdrawing movement.
- the vent volume is also advantageous in the tightening movement, since the fluid, which is located in the region of the contact surfaces, can flow off quickly.
- a dead volume which is included in the abutment of the armature at the stop between the two contact partners and has no connection to an axial channel.
- the dead volume shortly before the abutment of the armature against the stopper causes the fluid in the dead volume to be pinched off and thus also acts as a pressure cushion between the armature and the stop.
- a strong end position damping is achieved by means of effective as a pressure pad dead volume with a small contact surface.
- a first vent volume exists radially inside the contact surface and a second vent volume radially outside the contact surface.
- the embodiment with the first and second vent volumes is designed such that both vent volumes are connected via a connection and only one of the vent volumes is connected to openings of the axial channels.
- a surface of the armature or of the stop is made non-magnetic.
- a magnetic separation is achieved and prevents that when a concern of the armature to the stop a separation of the two contact partners only with great effort is possible.
- a non-magnetic material may have a higher strength than the material of the armature or the abutment, which increases the wear resistance and thus the life of the quantity control valve.
- the nature of a surface which is associated with the contact surface is characterized by a profiling. Due to the profiling, the squeezing effect and the hydraulic bonding, ie the behavior during the application and removal movement in the region of the contact of armature and stop can be precisely adjusted.
- FIG. 1 shows a fuel injection system 1 of an internal combustion engine in a highly simplified representation.
- a fuel tank 9 is connected via a suction line 4, a prefeed pump 5 and a low-pressure line 7 with a (not explained in detail) high-pressure pump 3.
- a high-pressure accumulator 13 (“common rail") is connected via a high-pressure line 11.
- a quantity control valve 14 with an electromagnetic actuator 15 - hereinafter referred to as an electromagnet 15 - is arranged hydraulically in the course of the low-pressure line 7 between the prefeed pump 5 and the high-pressure pump 3.
- Other elements, such as valves of the high pressure pump 3, are in the FIG. 1 not drawn.
- the quantity control valve 14 may be formed as a unit with the high-pressure pump 3.
- an intake valve of the high-pressure pump 3 can be forcibly opened by the quantity control valve 14.
- the prefeed pump 5 conveys fuel from the fuel tank 9 into the low-pressure line 7.
- the quantity control valve 14 determines the quantity of fuel supplied to the high-pressure pump 3.
- FIG. 2a shows in a simplified representation of a section of the quantity control valve 14, and the electromagnet 15.
- the in the FIG. 2a The elements shown essentially have a rotational symmetry about a central longitudinal axis of a housing section 20.
- the substantially hollow cylindrical housing portion 20 Shown is the substantially hollow cylindrical housing portion 20, and in this a generally denoted as a moving part, displaceable in the direction of the longitudinal axis anchor 22 and a fixedly connected to the armature 22 valve member 24.
- the housing portion 20 is limited in the right part of the drawing by a stop 26.
- a fluid 30 not visible in the drawing is located on both sides of the armature 22.
- a circumferential annular gap 36 Between an inner peripheral wall 32 of the housing section 20 and an outer peripheral wall 34 of the armature 22 a circumferential annular gap 36, which is shown exaggerated.
- the armature 22 has in the present case four axial channels 38, two of which in the sectional view of FIG. 2a are visible.
- the channels 38 can either be designed as bores in the armature 22 or as a groove on the peripheral wall 34 of the armature 22, as shown.
- the end face of the armature 22 is located on the stop 26 in the region of a contact surface directly.
- the contact surface is in the device after FIG. 2a defined by the frontal surface of the armature 22 and interrupted only by the mouths of the channels 38.
- the contact surface is generally composed of the overlapping surfaces of armature 22 and stop 26.
- the individual surfaces can be unlike those in FIG. 2a Also shown in approximately plane-parallel surfaces also have a different surface shape, such as a convex, concave or wave-like surface shape, so that they form the contact surface upon contact by a mating fit.
- the armature 22 is moved together with the valve element 24 in the drawing to the right, which corresponds to the tightening movement. This is symbolized by an arrow 42.
- the tightening movement is characterized in that the moving part, in this case the armature 22, moves toward a non-movable part, here the stop 26. After concern of the anchor 22 on the stop 26, the armature 22 is moved away from the stop 26 or pulled away. This is the stripping movement. An opening or closing of the valve is not meant with the tightening or Abziehdoch.
- the total area of the armature 22 on the front side, that is to say on the side facing the stop 26, corresponds to the plan view surface from the direction IIIa.
- the plan view surface neither takes into account the mouths of the axial channels 38 nor the annular gap 36.
- the total area is thus defined by a plan view surface from the direction of the opposite contact partner, here the armature 22 or the stopper 26.
- the squeezing effect means a hindrance to the displacement of the fluid 30. This is in the FIG. 2a indicated by double arrows 48. With the squeezing effect, an impact damping of the armature 22 is made possible. That is, the armature 22 can fly at high speed on the stop 26 and the impact of the armature 22 on the stopper 26 is damped by the squeezing effect and a resulting pressure pad.
- the crushing effect depends on the contact surface between anchor 22 and stop 26.
- the pressure pad runs at the in FIG. 2a shown quantity control valve 14 corresponding to the illustrated double arrows 48 between the overlapping surfaces of the armature 22 and the stopper 26. As shown, the surfaces of the armature 22 and the stopper 26 overlap in FIG. 2a except for the annular gap 36 and the mouths of the axial channels 38, completely.
- the operating situation in FIG. 2b corresponds to the peeling movement according to the arrow 43 against the tightening in FIG. 2a .
- an impact of the anchor 22 on the stop 26 is generated.
- the volume is filled with the fluid 30 via the axial channels 38 corresponding to the arrows 47.
- a so-called hydraulic gluing may occur, which makes the stripping movement more difficult.
- FIG. 3a shows a section of the quantity control valve 14 with an electromagnet 15 in a simplified representation, following the representation principle of FIG. 2a ,
- the armature 22 in this case has a cylindrical projection 62 with a circular surface 60.
- the circular surface 60 defines the contact surface.
- the surface 60 is smaller than the total area of the armature 22.
- the material of one of the contact surface forming surfaces of the armature 22 or the stopper 26 is made non-magnetic. This can be done for example by a chrome plating, which also represents a wear-resistant surface.
- the surface 60 may be contrary to FIG. 3a also have another shape, in which case the opposite stop 26 has a corresponding, the shape of the surface 60 receiving shape.
- the surface 60 may have a concave shape and the stopper may have a convex shape in the corresponding area.
- the surface 60 may be configured such that when a gap between the armature 22 and the stop 26 is present. For example, if a radially outwardly increasing distance from the surface 60 and stop 26 is provided in the region of the contact surface, the gap arises radially outwards. This gap allows fluid from a radial Outside the contact surface volume can flow in the region of the contact surface and hydraulic adhesion is prevented or reduced. Despite the gap, the squeezing effect can be used during the tightening movement.
- the surface 60 may be characterized by a profiling. This can be designed differently. For example, a profile in the form of concentric circles makes it difficult for the fluid 30 to flow in the radial direction during the application and removal movement. This means that in comparison with a smooth surface during the tightening movement, the pressure pad and, in the removal movement, the hydraulic bonding are more pronounced.
- a profiling radiating from a mid-point of the surface will make it easier for the fluid 30 to flow in the radial direction during the pull-on and pull-down motion. This means that in comparison to a smooth surface during the tightening movement the pressure pad and during the stripping movement the hydraulic bonding are less pronounced.
- FIG. 3b is the axial plan view of the armature 22 according to the direction of the purple after the FIG. 3a to see. For graphic reasons, only the upper half of the armature 22 is shown. The lower half, not drawn, is mirror-symmetrical. In the FIG. 3b the axial channels 38 and the cylindrical projection 62 with the circular surface 60 can be seen. Furthermore, one half of the double arrow 48 can be seen, which represents the pressure pad. The peripheral wall 34 limits the anchor 22.
- the operating situation in the FIG. 3a is as follows: According to the operating situation in FIG. 2a , the tightening movement, the armature 22 is moved to the right with a valve element 24 corresponding to an arrow 42 in the drawing. The volume of the portion 44 of the armature space 28 is continuously reduced and the fluid flows out of the section 44 in accordance with arrows 46.
- the crushing effect arises between the circular surface 60 and the overlapping part of the surface of the stop 26.
- the crushing effect creates a pressure pad according to the double arrow 48 and an impact damping of the armature 22 is ensured. Because the surface 60 is smaller than the total area of the armature 22, the pressure pad is not formed in the area of the total area of the armature 22, but only in the area of the smaller contact area.
- FIG. 4a shows a section of the quantity control valve 14 in a simplified representation, following the representation principle of FIG. 2a .
- the stop 26 has a cylindrical projection 62 with a circular surface 60.
- the circular surface 60 is smaller than the total area of the abutment 26.
- FIG. 4b is the axial plan view of the stop 26 according to a direction IIIb of FIG. 4a with the cylindrical projection 62 and the circular surface 60. Furthermore, one half of the double arrow 48 can be seen, which represents the pressure pad.
- the inner circumferential wall 32 of the housing section 20 limits the illustrated plan view of the stop 26.
- FIG. 4a The operating situation in the FIG. 4a is essentially the same as that of FIG. 3a , A pull-off movement, not shown, corresponds essentially to the explanations to Figure 3a and 3b ,
- the cylindrical projection 62 and thus the circular contact surface 60 are in the FIGS. 3a and 3b at the anchor 22, in the FIGS. 4a and 4b In contrast, formed on the stop 26.
- the contact surface and thus the pressure pad can, according to the double arrows 48 of the corresponding FIGS. 3a to 4b , So be achieved by a corresponding reverse profiling of the armature 22 and the stopper 26.
- the following exemplary embodiments are therefore to be understood as meaning that an approximately equivalent function with respect to the contact surfaces and the pressure pad can also be achieved by a correspondingly inverted shape or profiling of the opposing contact partners. When profiling a desired ventilation through the axial channels 38 is also to be considered.
- FIG. 5a shows following the representation principle of the FIG. 2a , in a simplified representation of a section of the quantity control valve 14 with an electromagnet 15.
- the armature 22 in this case has a hollow cylindrical projection 64 with an annular surface 61, wherein axial channels 38 are radially outside of the hollow cylindrical projection 64.
- the annular surface 61 is smaller than the total area of the armature 22.
- the contact surface of the FIG. 5a is compared to the contact area in FIG. 3a smaller, taking a same circular outer diameter of cylindrical projection 62 in FIG. 3a and hollow cylindrical projection 64 in FIG FIG. 5a at.
- FIG. 5b is the axial plan view of the armature 22 according to a direction of purple after the FIG. 5a with the hollow cylindrical projection 64, the annular surface 61 and the dead volume 66.
- the armature 22 is bounded by the peripheral wall 34 and further includes the axial channels 38.
- the arrows 48 represent the pressure pad.
- FIG. 5a The operating situation in the FIG. 5a is essentially the same as that of FIG. 2a , Shortly before the abutment of the armature 22 against the abutment 26, the fluid 30, which is located in the dead volume 66, is closed off by the venting volume 65 located radially outside.
- the fluid 30 in the dead volume as a pressure cushion is effective, resulting in a similar effect, as in a circular surface 60 after Figure 3a and 3b results. This means that in this case the effective pressure pad surface is greater than the contact surface.
- a pull-off movement corresponds essentially to the explanations to FIG. 3b , wherein filling in the region of the contact surface and the trapped dead volume 66 is similar to FIG. 3b radially from the outside via the vent volume 65 happens.
- FIG. 6a shows following the representation principle of the FIG. 2a , in a simplified representation of a section of the quantity control valve 14 with an electromagnet 15.
- the armature 22 in this case has a hollow cylindrical projection 64 with an annular surface 61, wherein the axial channels 38 are radially within the hollow cylindrical projection 64.
- the annular surface 61 is smaller than the total area of the armature 22.
- FIG. 6b is the axial plan view of the armature 22 according to a direction of purple after the FIG. 6a to see with the hollow cylindrical projection 64 and the annular surface 61.
- the armature 22 is bounded by a peripheral wall 34 and further includes the axial channels 38 radially inwardly of the hollow cylindrical projection 64.
- the arrows 48 represent the pressure pad.
- FIG. 6a The operating situation in FIG. 6a is as follows: Due to the movement of the armature 22 in the direction of the arrow 42 forms shortly before the concern of the armature 22 to the stop 26, a pressure pad according to the double arrows 48. In the mouths of the axial channels 38 which are located radially inside the hollow-cylindrical projection 64, a ventilation volume 65 exists within the annular surface 61.
- the armature 22 has no dead volume 66 as in FIG FIG. 5a and 5b and the fluid 30 can flow radially inside the hollow cylindrical projection 64 through the axial channels 38. Since the annular surface 61 is closed with the annular gap 36, the fluid 30 can flow when applying the armature 22 to the stop 26 substantially only in one direction, namely radially inwardly.
- the design of the armature 22 means that a filling of the volume, which arises in the removal movement in the region of the annular surface 61, is done by the fluid 30, which radially within the hollow cylindrical projection 64, ie in the vent volume 65th , is located.
- the vent volume 65 is filled via the channels 38.
- FIG. 7a shows a representation similar to that of FIG. 5a but with additional grooves 68 in the hollow cylindrical projection 64 of the armature 22.
- the annular surface 61 is thus interrupted by the radial grooves 68.
- the armature 22 has only two axial channels 38 in this case.
- the annular surface 61 is smaller than the total area of the armature 22.
- FIG. 7b is the axial plan view of the armature 22 according to the direction of the purple after the Figure 7a with the hollow cylindrical projection 64, the discontinuous annular surface 61 and the radial groove 68.
- the armature 22 is bounded by the peripheral wall 34 and further includes the axial channels 38 radially outside of the hollow cylindrical projection 64.
- the double arrows 48 represent the pressure pad.
- FIG. 7a The operating situation in the Figure 7a essentially follows the description FIG. 5a , In comparison with the FIGS. 5a and 5b reduces the effective pressure pad surface by replacing the dead volume 66 from FIGS. 5a and 5b in the form of a central first vent volume 65 within the hollow cylindrical projection 64.
- the fluid 30, which is located within the hollow cylindrical projection 64, via the radially outside of the hollow cylindrical projection 64 lying second vent volume 65 flow into the channels 38.
- the effective pressure pad surface is thus equal to the contact surface.
- the resulting volume in the region of the annular contact surface 61 radially fills in two directions: on the one hand radially from the outside through the second vent volume 65 and via the axial channels 38 tracked fluid 30, on the other radially from the inside the first venting volume 65 or the fluid 30 fed via the axial channels 38 and the grooves 68.
- FIG. 8 shows in a simplified representation of a section of the quantity control valve 14. Shown is the housing portion 20 and in this the armature 22, connected to the valve element 24 as in FIG. 2a , Furthermore, a fixed to the housing portion 20 stop body 73 is shown with a stop 27. The contact area between the armature 22 and stop 27 according to the arrows 48 is smaller than the total area of the armature 22.
- a pull-off movement of the valve element 24 with the armature 22 is characterized in that the armature 22 moves in the direction of the arrow 43 toward the stop 26. Between the armature 22 and the stopper body 73, the pressure pad according to the double arrows 48 builds up before an impact or concern of the armature 22. In this case, the fluid 30 can flow off via the vent volume 65 and the channels 38 in accordance with the arrows 46.
- FIG. 9 shows a section of a quantity control valve 14 with two fixed stop bodies 73 with the stops 26 and 27, which serve to limit the movement of the valve element 24 by a fixedly connected to the valve element 24 stop anchor 72.
- the stop anchor 72 is movable in the housing portion 20 along the longitudinal axis.
- the valve member 24 is connected in a manner not shown with the armature 22, wherein the armature 22 on the right side according to the FIG. 9 located.
- the annular contact surface between the stop anchor 72 and the stop 26 according to the arrows 48 is smaller than the total area of the stop anchor 72 by the vent volumes 65 in the stop body 73.
- Example shows the operating situation in FIG. 9 the moment just before the concerns of the stop anchor 72 on the stop 26, ie the tightening movement.
- a pressure cushion according to the double arrows 48 forms between the overlapping surfaces of the stop anchor 72 and the stopper 26 and the stopper body 73 and the fluid 30 is displaced via the venting volumes 65 into the armature space 28 corresponding to the arrows 46.
- a pressure cushion is formed on the stop 27.
- a withdrawal movement of the stop anchor 72, not shown, from the stop 26 opposite to the arrow 42 has the result that the volume arising in the region of the contact surface between stop anchor 72 and stop 26 is filled with the fluid 30 from the venting volumes 65.
- FIG. 10a Shown is the housing portion 20, and in this a displaceable along the longitudinal axis stopper anchor 72 having a peripheral wall 74.
- the slidable stop anchor 72 is fixedly connected to the valve element 24.
- the valve element 24 is guided radially in the fixed stop body 73.
- An inner circumferential wall 78 of the stopper body 73 defines with an outer peripheral wall 80 of the valve element 24 a guide gap 79 for guiding the valve element 24.
- the guide gap is shown exaggeratedly large.
- the stopper body 73 is characterized by being in a direction of lilac, i. in the direction of the stop anchor 72, a conical diameter jump 82 has.
- the conical diameter jump 82 corresponds to an increase in the inner diameter in the direction of purple starting from the peripheral wall 78 and continues until it stops 26. Furthermore, the stop body 73 on the stop armature 72 side facing a groove 68th
- the groove 68 extends from the diameter jump 82 in the radial direction over the diameter of the peripheral wall 74 of the stop armature 72 to the peripheral wall 32 of the armature space 28.
- the groove 68 connects the vent volume 65 within the diameter jump 82 with the armature space 28.
- FIG. 10b is the axial plan view of the stopper body 73 according to the direction IIIb after FIG. 10a and to see a cross section of the valve element 24.
- the radial bearing of the valve element 24 is shown with the limited by the peripheral walls 78 and 79 guide gap 79. Radially starting from the peripheral wall 78 via the diameter jump 82, the stop body 73 passes over into the stop 26.
- Double arrows 48 represent the pressure pad and, with the indicated peripheral wall 74 of the stop anchor 72, indicate the annular contact surface interrupted by the groove 68.
- the operating situation in FIGS. 10a and 10b is as follows:
- the stop armature 72 moves, in the form of a tightening movement, with the valve element 24 to the stop 26 and thus the valve body 73 to.
- the broken, annular contact surface is reduced by the diameter jump 82 and concerns the overlapping surfaces of abutment 26 and stop anchor 72.
- the fluid 30, which at the abutment of the stop anchor 72 at the Stop 26 is located in the region of the diameter jump 82, can flow via the groove 68 along the arrow 76 via venting volumes 65 in the armature space 28.
- the fluid 30 within the diameter jump 82 and within the groove 68 does not act as a pressure pad. Due to the guide gap 79, essentially no fluid 30 can flow away.
- a resulting volume in the area of the interrupted, annular contact surface is filled radially from the inside and from the outside by the venting volumes 65 with the fluid 30.
- the fluid 30 flows over the armature space 28 radially from the outside. Furthermore, the fluid 30 flows over the inside diameter jump 82 and the groove 68 to.
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- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Magnetically Actuated Valves (AREA)
Description
Die Erfindung betrifft ein elektromagnetisch betätigtes Mengensteuerventil nach dem Oberbegriff des Anspruchs 1.
Vom Markt her bekannt sind Mengensteuerventile, welche ein elektromagnetisch betätigtes Ventilelement aufweisen. Damit kann die einer Hochdruckpumpe zugeführte Kraftstoffmenge im Kraftstoffeinspritzsystem einer Brennkraftmaschine beeinflusst werden.
Ebenfalls bekannt ist es, einen Anker des Elektromagneten beispielsweise mit Längsbohrungen zu versehen, um die bei der Bewegung des Ankers auftretende Dämpfung einstellen zu können. Durch solche axialen Bohrungen im Anker wird Fluid, also Kraftstoff, von einer axialen Seite des Ankers zur anderen Seite befördert. Alternativ zu einer axialen Bohrung im Anker ist es ebenfalls bekannt, an einer Umfangswand des Ankers axiale Nuten anzubringen, welche ebenfalls einen Fluidaustausch zwischen den beiden Seiten des Ankers ermöglichen. Aus der
From the market known quantity control valves, which have an electromagnetically actuated valve element. Thus, the amount of fuel supplied to a high-pressure pump can be influenced in the fuel injection system of an internal combustion engine.
It is also known to provide an armature of the electromagnet, for example, with longitudinal bores in order to adjust the damping occurring during the movement of the armature can. Through such axial bores in the armature fluid, so fuel, transported from one axial side of the armature to the other side. As an alternative to an axial bore in the armature, it is also known to provide axial grooves on a peripheral wall of the armature, which also allow a fluid exchange between the two sides of the armature. From the
Durch die Erfindung wird ein elektromagnetisch betätigtes Mengensteuerventil nach Anspruch 1 geschaffen. Vorteilhafte Weiterbildungen sind in Unteransprüchen angegeben. Für die Erfindung wichtige Merkmale finden sich ferner in der nachfolgenden Beschreibung und in den Zeichnungen, wobei die Merkmale sowohl in Alleinstellung als auch in unterschiedlichen Kombinationen für die Erfindung wichtig sein können, ohne dass hierauf nochmals explizit hingewiesen wird.The invention provides an electromagnetically actuated quantity control valve according to claim 1. Advantageous developments are specified in subclaims. For the invention important features can be found also in the following description and in the drawings, the features both alone and in different combinations may be important for the invention, without being explicitly referred to again.
Das erfindungsgemäße Mengensteuerventil besitzt einen in einem Gehäuseabschnitt in zwei Richtungen bewegbaren Anker, wobei eine Bewegungsrichtung durch einen Anschlag begrenzt ist. Der Gehäuseabschnitt ist mit Fluid befüllbar. Liegt der Anker an dem Anschlag an, so existiert eine Kontaktfläche, die durch die Oberflächen der beiden Kontaktelemente, dem Anker und dem Anschlag, bestimmt ist und kleiner ist als die Gesamtfläche von Anker oder Anschlag.The quantity control valve according to the invention has a movable in a housing portion in two directions armature, wherein a direction of movement is limited by a stop. The housing section can be filled with fluid. If the armature bears against the stop, there is a contact surface which is determined by the surfaces of the two contact elements, the armature and the stop, and which is smaller than the total area of the armature or stop.
Ein Vorteil der Erfindung besteht darin, dass sich bei einer Anziehbewegung, d.h. einer Bewegung des Ankers auf den Anschlag zu, im Bereich der Kontaktfläche vor dem Anliegen in Verbindung mit dem Fluid ein Druckpolster ausbildet, welches die Geschwindigkeit der Bewegung vor dem Aufprall des Ankers an dem Anschlag verringert. Dieser Effekt wird Quetscheffekt genannt.An advantage of the invention is that during an attraction movement, i. a movement of the armature on the stop, in the region of the contact surface before the application in conjunction with the fluid forms a pressure cushion, which reduces the speed of movement before the impact of the armature against the stop. This effect is called squeezing effect.
Ein weiterer Vorteil der Erfindung zeigt sich bei einer Abziehbewegung, d.h. einer Bewegung des Ankers von dem Anschlag weg, ausgehend von einem Anliegen des Ankers an dem Anschlag. Im Bereich der Kontaktfläche entsteht ein Volumen, welches nun mit dem Fluid wiederbefüllt wird. Die Verminderung der Kontaktfläche im Vergleich zur Gesamtfläche von Anker oder Anschlag ermöglicht es, ein so genanntes hydraulisches Kleben des Ankers am Anschlag zu verringern, und somit Schaltzeiten zu verringern.Another advantage of the invention is evident in a peel, i. a movement of the armature away from the stop, starting from a concern of the armature against the stop. In the area of the contact surface, a volume is created, which is then refilled with the fluid. The reduction of the contact area compared to the total area of the armature or stop makes it possible to reduce a so-called hydraulic sticking of the armature to the stop, and thus to reduce switching times.
Durch eine Aufprallverzögerung bei der Anziehbewegung und eine Minderung des hydraulischen Klebens bei der Abziehbewegung werden die NVH-Eigenschaften (NVH = Noise, Vibration & Harshness) des Mengensteuerventils, d.h. die Eigenschaften bezüglich Geräusch, Vibration und Rauhigkeit, in positiver Weise beeinflusst.Impact deceleration during the tightening movement and reduction of hydraulic sticking during peel-off will increase the NVH (Noise, Vibration & Harshness) characteristics of the quantity control valve, i. the properties regarding noise, vibration and roughness, influenced in a positive way.
Die Aufprallverzögerung verringert die Pulsation des Drucks bei der Anziehbewegung. Auch Preller, d.h. ein mehrfaches Aufprallen bei der Anziehbewegung durch federnde Eigenschaften der beteiligten Bauteile, werden minimiert. Eine Verringerung der Kavitationsneigung wird durch den zeitlich abgedämpften Druckverlauf und damit einer geringen Neigung zu örtlich plötzlich auftretenden Druckunterschieden erreicht.
Durch die Gestaltung der jeweiligen Oberflächen des Ankers und des Anschlags vor allem hinsichtlich der Größe und Form der Kontaktflächen wird ein Kompromiss zwischen der Aufpralldämpfung und dem verringerten hydraulischen Kleben erreicht.
Mit den vorgenannten Vorteilen wird außerdem erreicht, dass eine geringe festigkeitskritische Belastung sowie eine geringe Erosion und damit erhöhte Lebensdauer der beteiligten Bauteile wie beispielsweise auch Schweißnähte, Hülsen, o.ä. erreicht wird.
Damit wird auch ermöglicht, dass eine genaue Fördermenge über die gesamte Lebensdauer wie auch über kurze Betriebszeiten garantiert werden kann.The impact delay reduces the pulsation of the pressure during the tightening movement. Also Preller, ie a multiple impact in the tightening movement by resilient properties of the components involved, are minimized. A reduction of cavitation tendency is due to the time damped pressure curve and thus a slight tendency to locally suddenly occurring pressure differences achieved.
The design of the respective surfaces of the armature and the stop especially with regard to the size and shape of the contact surfaces, a compromise between the impact attenuation and the reduced hydraulic bonding is achieved.
With the aforementioned advantages is also achieved that a low strength-critical load and low erosion and thus increased life of the components involved such as welds, sleeves, or similar. is reached.
This also makes it possible to guarantee an exact delivery rate over the entire service life as well as over short operating times.
In dem Mengensteuerventils führt ein Entlüftungsvolumen, welches mit einem axialen Kanal innerhalb des Ankers verbunden ist, dazu, dass bei der Abziehbewegung ein schnelles Wiederbefüllen des im Bereich der Kontaktfläche enstehenden Volumens erreicht wird. Das Entlüftungsvolumen ist ebenso bei der Anziehbewegung vorteilhaft, da das Fluid, welches sich im Bereich der Kontaktflächen befindet, schnell abfließen kann.In the quantity control valve, a venting volume, which is connected to an axial channel within the armature, leads to a rapid refilling of the volume arising in the region of the contact surface during the withdrawing movement. The vent volume is also advantageous in the tightening movement, since the fluid, which is located in the region of the contact surfaces, can flow off quickly.
Außerdem existiert ein Totvolumen, welches bei dem Anliegen des Ankers an dem Anschlag zwischen den beiden Kontaktpartnern eingeschlossen ist und keine Verbindung zu einem axialen Kanal besitzt. Bei der Anziehbewegung führt das Totvolumen kurz vor dem Anliegen des Ankers an dem Anschlag dazu, dass das Fluid in dem Totvolumen abgeschnürt wird und somit ebenso als Druckpolster zwischen Anker und Anschlag wirksam wird. Somit wird mit einer kleinen Kontaktfläche eine starke Endlagendämpfung mittels des als Druckpolster wirksamen Totvolumens erreicht.
In einer vorteilhaften Ausführungsform des Mengensteuerventils existiert radial innerhalb der Kontaktfläche ein erstes Entlüftungsvolumen und radial außerhalb der Kontaktfläche ein zweites Entlüftungsvolumen. Das heißt, dass bei der Anziehbewegung das Fluid zu beiden Seiten, also nach radial innen und radial außen, abfließen kann. Der Vorteil zeigt sich bei der Abziehbewegung. Das im Bereich der Kontaktfläche entstehende Volumen kann von zwei Seiten wiederbefüllt werden und der Effekt des hydraulischen Klebens wird weiter verringert.In addition, there is a dead volume, which is included in the abutment of the armature at the stop between the two contact partners and has no connection to an axial channel. During the tightening movement, the dead volume shortly before the abutment of the armature against the stopper causes the fluid in the dead volume to be pinched off and thus also acts as a pressure cushion between the armature and the stop. Thus, a strong end position damping is achieved by means of effective as a pressure pad dead volume with a small contact surface.
In an advantageous embodiment of the quantity control valve, a first vent volume exists radially inside the contact surface and a second vent volume radially outside the contact surface. That means that at the Tightening movement, the fluid on both sides, ie radially inward and radially outward, can flow. The advantage is evident in the removal movement. The volume created in the region of the contact surface can be refilled from two sides and the effect of the hydraulic bonding is further reduced.
In einer vorteilhaften Weiterbildung des Mengensteuerventils ist die Ausführungsform mit erstem und zweiten Entlüftungsvolumen derart ausgestaltet, dass beide Entlüftungsvolumina über eine Verbindung verbunden sind und nur eines der Entlüftungsvolumina mit Mündungen der axialen Kanäle verbunden ist. Dadurch kann die Entlüftung der beiden Entlüftungsvolumina garantiert werden und es sind keine weiteren axialen Kanäle mit Mündungen in beide Entlüftungsvolumina notwendig.In an advantageous development of the quantity control valve, the embodiment with the first and second vent volumes is designed such that both vent volumes are connected via a connection and only one of the vent volumes is connected to openings of the axial channels. As a result, the venting of the two venting volumes can be guaranteed and no further axial channels with openings in both venting volumes are necessary.
In einer weiteren vorteilhaften Ausführungsform des Mengensteuerventils ist eine Oberfläche des Ankers oder des Anschlags nicht-magnetisch ausgeführt. Dadurch wird eine magnetische Trennung erreicht und verhindert, dass bei einem Anliegen des Ankers an dem Anschlag eine Trennung der beiden Kontaktpartner nur unter großem Kraftaufwand möglich ist. Ebenso kann ein nicht-magnetisches Material eine höhere Festigkeit als das Material des Ankers oder des Anschlags aufweisen, was die Verschleißfestigkeit und damit die Lebensdauer des Mengensteuerventils erhöht.In a further advantageous embodiment of the quantity control valve, a surface of the armature or of the stop is made non-magnetic. As a result, a magnetic separation is achieved and prevents that when a concern of the armature to the stop a separation of the two contact partners only with great effort is possible. Likewise, a non-magnetic material may have a higher strength than the material of the armature or the abutment, which increases the wear resistance and thus the life of the quantity control valve.
In einer vorteilhaften Ausführungsform des Mengensteuerventils ist die Beschaffenheit einer Oberfläche, welche der Kontaktfläche zugehörig ist, durch eine Profilierung gekennzeichnet. Durch die Profilierung lassen sich der Quetscheffekt und das hydraulische Kleben, also das Verhalten bei der Anzieh- und Abziehbewegung im Bereich des Anliegens von Anker und Anschlag genau einstellen.In an advantageous embodiment of the quantity control valve, the nature of a surface which is associated with the contact surface is characterized by a profiling. Due to the profiling, the squeezing effect and the hydraulic bonding, ie the behavior during the application and removal movement in the region of the contact of armature and stop can be precisely adjusted.
Nachfolgend werden beispielhafte Ausführungsformen der Erfindung unter Bezugnahme auf die Zeichnung erläutert. In der Zeichnung zeigen:
- Figur 1
- ein vereinfachtes Schema eines Kraftstoffeinspritzsystems einer Brennkraftmaschine;
- Figur 2a
- eine Schnittansicht eines vereinfachten Schemas eines Elektromagneten (ohne Spule) eines Mengensteuerventils in einer Anziehbewegung;
- Figur 2b
- eine Schnittansicht des Elektromagneten (ohne Spule) der
Figur 2a in einer Abziehbewegung; - Figur 3a
- eine Schnittansicht gemäß
Figur 2a mit einem Anker mit einer kreisförmigen Kontaktfläche; - Figur 3b
- eine axiale Draufsicht entsprechend einer Richtung lila auf den Anker nach der
Figur 3a ; - Figur 4a
- eine Schnittansicht gemäß
Figur 2a mit einem Anschlag mit einer kreisförmigen Kontaktfläche; - Figur 4b
- eine axiale Draufsicht entsprechend einer Richtung IIIb auf den Anschlag nach der
Figur 4a ; - Figur 5a
- eine Schnittansicht gemäß
Figur 2a mit einem Anker mit einer kreisringförmigen Kontaktfläche; - Figur 5b
- eine axiale Draufsicht entsprechend einer Richtung lila auf den Anker nach der
Figur 5a ; - Figur 6a
- eine Schnittansicht gemäß
Figur 2a mit einem Anker mit einer kreisringförmigen Kontaktfläche; - Figur 6b
- eine axiale Draufsicht entsprechend einer Richtung lila auf den Anker nach der
Figur 6a ; - Figur 7a
- eine Schnittansicht gemäß
Figur 2a mit einem Anker mit einer kreisringförmigen Kontaktfläche und einer Nut; - Figur 7b
- eine axiale Draufsicht entsprechend einer Richtung lila auf den Anker nach der
Figur 7a ; - Figur 8
- eine Schnittansicht eines Anschlagkörpers;
- Figur 9
- eine Schnittansicht eines Anschlagankers;
- Figur 10a
- eine Schnittansicht eines Anschlagankers; und
- Figur 10b
- eine axiale Draufsicht auf einen Anschlagkörper gemäß einer Richtung IIIb der
Figur 10a .
- FIG. 1
- a simplified diagram of a fuel injection system of an internal combustion engine;
- FIG. 2a
- a sectional view of a simplified schematic of an electromagnet (without coil) of a quantity control valve in a tightening movement;
- FIG. 2b
- a sectional view of the electromagnet (without coil) of
FIG. 2a in a stripping motion; - FIG. 3a
- a sectional view according to
FIG. 2a with an anchor having a circular contact surface; - FIG. 3b
- an axial plan view corresponding to a direction of purple on the armature after the
FIG. 3a ; - FIG. 4a
- a sectional view according to
FIG. 2a with a stop with a circular contact surface; - FIG. 4b
- an axial plan view corresponding to a direction IIIb to the stop after the
FIG. 4a ; - FIG. 5a
- a sectional view according to
FIG. 2a with an anchor with a circular contact surface; - FIG. 5b
- an axial plan view corresponding to a direction of purple on the armature after the
FIG. 5a ; - FIG. 6a
- a sectional view according to
FIG. 2a with an anchor with a circular contact surface; - FIG. 6b
- an axial plan view corresponding to a direction of purple on the armature after the
FIG. 6a ; - Figure 7a
- a sectional view according to
FIG. 2a with an armature having an annular contact surface and a groove; - FIG. 7b
- an axial plan view corresponding to a direction of purple on the armature after the
Figure 7a ; - FIG. 8
- a sectional view of a stopper body;
- FIG. 9
- a sectional view of a stop anchor;
- FIG. 10a
- a sectional view of a stop anchor; and
- FIG. 10b
- an axial plan view of a stopper body according to a direction IIIb of
FIG. 10a ,
Es werden für funktionsäquivalente Elemente und Größen in allen Figuren die gleichen Bezugszeichen verwendet.The same reference numerals are used for functionally equivalent elements and sizes in all figures.
Beim Betrieb des Kraftstoffeinspritzsystems 1 fördert die Vorförderpumpe 5 Kraftstoff vom Kraftstofftank 9 in die Niederdruckleitung 7. Dabei bestimmt das Mengensteuerventil 14 die der Hochdruckpumpe 3 zugeführte Kraftstoffmenge.During operation of the fuel injection system 1, the
Dargestellt ist der im Wesentlichen hohlzylindrische Gehäuseabschnitt 20, und in diesem ein allgemein als Bewegungsteil bezeichenbarer, in Richtung der Längsachse verschiebbarer Anker 22 und ein mit dem Anker 22 fest verbundenes Ventilelement 24. Der Gehäuseabschnitt 20 ist im in der Zeichnung rechten Teil begrenzt durch einen Anschlag 26. In einem in dem Gehäuseabschnitt 20 gebildeten und allgemein als Bewegungsraum bezeichenbaren Ankerraum 28 befindet sich zu beiden Seiten des Ankers 22 ein in der Zeichnung nicht sichtbares Fluid 30. Zwischen einer inneren Umfangswand 32 des Gehäuseabschnitts 20 und einer äußeren Umfangswand 34 des Ankers 22 befindet sich ein umlaufender Ringspalt 36, der übertrieben groß dargestellt ist.Shown is the substantially hollow
Der Anker 22 weist vorliegend vier axiale Kanäle 38 auf, von denen zwei in der Schnittdarstellung der
In einer Endlage in Richtung des Pfeils 42 liegt die Stirnseite des Ankers 22 auf dem Anschlag 26 im Bereich einer Kontaktfläche direkt auf. Die Kontaktfläche ist bei der Vorrichtung nach
Die Kontaktfläche setzt sich allgemein aus den überlappenden Oberflächen von Anker 22 und Anschlag 26 zusammen. Die einzelnen Oberflächen können im Gegensatz zu den in
In der in
Die Gesamtfläche des Ankers 22 an der Stirnseite, also an der dem Anschlag 26 zugewandten Seite, entspricht der Draufsichtfläche aus der Richtung lila. Die Draufsichtfläche berücksichtigt weder die Mündungen der axialen Kanäle 38 noch den Ringspalt 36. Für den Anschlag 26existiert eine weitere Draufsichtfläche aus der Richtung Illb und damit auch eine weitere Gesamtfläche. Die Gesamtfläche ist somit durch eine Draufsichtfläche aus der Richtung des entgegengesetzten Kontaktpartners, hier dem Anker 22 oder dem Anschlag 26, definiert.The total area of the
Bei der Anziehbewegung wird das Volumen eines Teilabschnitts 44 des Ankerraums 28 stetig verkleinert. Damit wird das in dem Teilabschnitt 44 vorhandene Fluid 30 verdrängt. Das Fluid 30 fließt hierbei entsprechend den gezeichneten Pfeilen 46 aus diesem Teilabschnitt 44 heraus.When tightening the volume of a
Durch eine Viskosität des Fluids 30 sowie die Bewegung des Ankers 22 in Richtung des Anschlags 26 erfolgt ein so genannter Quetscheffekt. Der Quetscheffekt bedeutet eine Behinderung der Verdrängung des Fluids 30. Dies ist in der
Der Quetscheffekt hängt ab von der Kontaktfläche zwischen Anker 22 und Anschlag 26. Das Druckpolster verläuft bei dem in
Die Betriebssituation in
In den folgenden Figuren ist meist lediglich die Anziehbewegung dargestellt.In the following figures, usually only the tightening movement is shown.
Die Schnittansicht der
Das Material einer der die Kontaktfläche bildenden Oberflächen des Ankers 22 oder des Anschlags 26 ist nicht-magnetisch ausgeführt. Dies kann beispielsweise durch eine Verchromung geschehen, die ebenso eine verschleißfeste Oberfläche darstellt.The material of one of the contact surface forming surfaces of the
Die Oberfläche 60 kann im Gegensatz zur
Ebenso kann die Oberfläche 60 derart ausgestaltet sein, dass beim Anliegen ein Spalt zwischen dem Anker 22 und dem Anschlag 26 vorhanden ist. Ist beispielsweise ein radial nach außen größer werdender Abstand von Oberfläche 60 und Anschlag 26 im Bereich der Kontaktfläche vorgesehen, so entsteht radial nach außen der Spalt. Dieser Spalt ermöglicht es, dass Fluid aus einem radial außerhalb der Kontaktfläche liegenden Volumen in den Bereich der Kontaktfläche fließen kann und ein hydraulisches Kleben verhindert bzw. verringert wird. Trotz des Spaltes kann bei der Anziehbewegung der Quetscheffekt genutzt werden.Likewise, the
Die Oberfläche 60 kann durch eine Profilierung gekennzeichnet sein. Diese kann unterschiedlich ausgeführt sein. Beispielsweise führt eine Profilierung in Form von konzentrischen Kreisen dazu, dass es dem Fluid 30 bei der Anzieh- und Abziehbewegung erschwert wird, in radialer Richtung zu fließen. Das heißt, dass im Vergleich zu einer glatten Oberfläche bei der Anziehbewegung das Druckpolster und bei der Abziehbewegung das hydraulische Kleben stärker ausgeprägt sind.The
Im Gegensatz dazu führt eine strahlenförmig von einem Mittelpunkt der Oberfläche ausgehende Profilierung dazu, dass es dem Fluid 30 bei der Anzieh- und Abziehbewegung erleichtert wird, in radialer Richtung zu fließen. Das heißt, dass im Vergleich zu einer glatten Oberfläche bei der Anziehbewegung das Druckpolster und bei der Abziehbewegung das hydraulische Kleben schwächer ausgeprägt sind.In contrast, a profiling radiating from a mid-point of the surface will make it easier for the fluid 30 to flow in the radial direction during the pull-on and pull-down motion. This means that in comparison to a smooth surface during the tightening movement the pressure pad and during the stripping movement the hydraulic bonding are less pronounced.
In
Die Betriebssituation in der
Der Quetscheffekt entsteht zwischen der kreisförmigen Oberfläche 60 und dem überlappenden Teil der Oberfläche des Anschlags 26. Durch den Quetscheffekt entsteht ein Druckpolster entsprechend dem Doppelpfeil 48 und eine Aufpralldämpfung des Ankers 22 ist dadurch gewährleistet. Dadurch, dass die Oberfläche 60 kleiner als die Gesamtfläche des Ankers 22 ist, entsteht das Druckpolster nicht im Bereich der Gesamtfläche des Ankers 22, sondern nur im Bereich der kleineren Kontaktfläche.The crushing effect arises between the
Bei einer nicht dargestellten Abziehbewegung des Ankers 22 entsteht ein Volumen im Bereich der Kontaktfläche, welche über die kreisförmigen Oberfläche 60 definiert ist. Dieses Volumen füllt sich über ein Entlüftungsvolumen 65 radial von außen, wobei sich das Entlüftungsvolumen 65 wiederum über die axialen Kanäle 38 füllt. Dadurch, dass die Oberfläche 60 kleiner als die Gesamtfläche des Ankers 22 ist, wird das hydraulische Kleben im Vergleich zur
Die im Vergleich zur
Die Schnittansicht der
In der
Die Betriebssituation in der
Der zylindrische Vorsprung 62 und damit die kreisförmige Kontaktfläche 60 sind in den
Die Schnittansicht der
Die Kontaktfläche der
Des Weiteren existiert ein Totvolumen 66, welches durch den hohlzylindrischen Vorsprung 64 begrenzt ist.Furthermore, there is a
In der
Die Betriebssituation in der
Eine nicht dargestellte Abziehbewegung entspricht im Wesentlichen den Erläuterungen zu
Die Schnittansicht der
In der
Die Betriebssituation in
Für die nicht dargestellte Abziehbewegung bedeutet die Ausgestaltung des Ankers 22, dass ein Befüllen des Volumens, welches bei der Abziehbewegung im Bereich der kreisringförmigen Oberfläche 61 entsteht, durch das Fluid 30 geschieht, welches sich radial innerhalb des hohlzylindrischen Vorsprungs 64, also in dem Entlüftungsvolumen 65, befindet. Das Entlüftungsvolumen 65 wird über die Kanäle 38 befüllt.For the withdrawal movement, not shown, the design of the
Die Schnittansicht der
In der
Die Betriebssituation in der
Durch den Pfeil 67 in
Bei einer nicht dargestellten Abziehbewegung des Ankers 22 befüllt sich das entstehende Volumen im Bereich der kreisringförmigen Kontaktfläche 61 radial aus zwei Richtungen: Zum einen radial von außen durch das zweite Entlüftungsvolumen 65 und über die axialen Kanäle 38 nachgeführtes Fluid 30, zum anderen radial von innen durch das erste Entlüftungsvolumens 65 bzw. das über die axialen Kanäle 38 und die Nuten 68 nachgeführte Fluid 30.In a pull-off movement of the
Eine Abziehbewegung des Ventilelements 24 mit dem Anker 22 ist dadurch gekennzeichnet, dass sich der Anker 22 in die Richtung des Pfeils 43 auf den Anschlag 26 zu bewegt. Zwischen dem Anker 22 und dem Anschlagkörper 73 baut sich vor einem Aufprall bzw. Anliegen des Ankers 22 das Druckpolster gemäß der Doppelpfeile 48 auf. Das Fluid 30 kann in diesem Fall über das Entlüftungsvolumen 65 und die Kanäle 38 entsprechend den Pfeilen 46 abfließen.A pull-off movement of the
Bei einer nicht dargestellten Anziehbewegung des Ankers 22, d.h. einer Bewegung des Ankers 22 von dem Anschlag 27 weg, muss das Volumen zwischen der Kontaktfläche zwischen Anker 22 und Anschlag 27 wieder mit dem Fluid 30 befüllt werden. Hierzu fließt das Fluid 30 aus dem Entlüftungsvolumen 65 und den Kanälen 38 nach.In an unillustrated tightening movement of the
Beispielhaft zeigt die Betriebssituation in
Eine nicht dargestellte Abziehbewegung des Anschlagankers 72 von dem Anschlag 26 entgegengesetzt zu dem Pfeil 42 hat zur Folge, dass das im Bereich der Kontaktfläche entstehende Volumen zwischen Anschlaganker 72 und Anschlag 26 mit dem Fluid 30 aus den Entlüftungsvolumina 65 befüllt wird.A withdrawal movement of the
Die
Der Anschlagkörper 73 ist dadurch gekennzeichnet, dass er in einer Richtung lila, d.h. in Richtung des Anschlagankers 72, einen konischen Durchmessersprung 82 aufweist. Der konische Durchmessersprung 82 entspricht einer Vergrößerung des inneren Durchmessers in die Richtung lila ausgehend von der Umfangswand 78 und setzt sich bis zum Anschlag 26 fort. Des Weiteren besitzt der Anschlagkörper 73 auf der dem Anschlaganker 72 zugewandten Seite eine Nut 68.The
Die Nut 68 verläuft ausgehend von dem Durchmessersprung 82 in radialer Richtung über den Durchmesser der Umfangswand 74 des Anschlagankers 72 hinaus bis zur Umfangswand 32 des Ankerraums 28. Die Nut 68 verbindet das Entlüftungsvolumen 65 innerhalb des Durchmessersprungs 82 mit dem Ankerraum 28. Durch den Durchmessersprung 82 sowie die Nut 68 ergibt sich eine durch die Nut 68 unterbrochene, kreisringförmige Kontaktfläche. Die Kontaktfläche ist kleiner als die Gesamtfläche des Ankers 22.The
In der
Die Betriebssituation in
Bei einer nicht dargestellten Abziehbewegung wird ein entstehendes Volumen im Bereich der unterbrochenen, kreisringförmigen Kontaktfläche radial von innen und von außen durch die Entlüftungsvolumina 65 mit dem Fluid 30 befüllt. Das Fluid 30 fließt über den Ankerraum 28 radial von außen zu. Des Weiteren fließt das Fluid 30 über den innen liegenden Durchmessersprung 82 und die Nut 68 zu.In a pull-off movement, not shown, a resulting volume in the area of the interrupted, annular contact surface is filled radially from the inside and from the outside by the venting
Claims (6)
- Electromagnetically actuated quantity control valve (14), in particular for controlling the delivery quantity of a high-pressure pump (3), having a movement space (28) which is able to be filled with a fluid (30), having a movement part (22, 72), arranged in said space, of an electromagnetic actuation device (15), and having a stop (26, 27), wherein, when the movement part (22, 72) abuts against the stop (26, 27), a contact surface is present between the movement part (22, 72) and the stop (26, 27), wherein the contact surface is defined by a surface of the movement part (22, 72) and a surface of the stop (26, 27), and wherein the contact surface is smaller than the entire surface of the movement part (22, 72) or of the stop (26, 27), wherein a dead volume exists, which, when the movement part (22, 72) abuts against the stop (26, 27), is enclosed between the movement part (22, 72) and the stop (26, 27) and is not able to be filled, characterized in that the dead volume is formed by a hollow cylindrical projection (64), in that, in the movement part (22, 72), axial ducts (38) which connect the regions of the movement space (28) situated on both sides of the movement part (22, 72) to one another are present, in that, when the movement part (22, 72) abuts against the stop (26, 27), a venting volume (65) which is able to be filled via the ducts (38) is present, in that the axial ducts (38) are situated radially outside the hollow cylindrical projection (64), and in that the contact surface is of circular-ring-shaped form radially between the hollow cylindrical projection (64) and the venting volume (65).
- Electromagnetically actuable quantity control valve (14) according to Claim 1, wherein venting volumes (65, 67) are present radially outside and radially inside the contact surface.
- Electromagnetically actuable quantity control valve (14) according to Claim 2, wherein a first venting volume (67) is able to be filled during the abutment from the movement space (28) with the fluid (30) via a connection (38, 68) from a second venting volume (65) .
- Electromagnetically actuable quantity control valve (14) according to one of the preceding claims, wherein one of the surfaces of the contact surface consists of a non-magnetic material.
- Electromagnetically actuable quantity control valve (14) according to one of the preceding claims, wherein the condition of a surface which belongs to the contact surface is characterized by a profiling.
- High-pressure fuel pump (3) comprising a quantity control valve (14) according to one of the preceding claims.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009055356A DE102009055356A1 (en) | 2009-12-29 | 2009-12-29 | Electromagnetically actuated quantity control valve, in particular for controlling the delivery rate of a high-pressure fuel pump |
PCT/EP2010/066797 WO2011079989A1 (en) | 2009-12-29 | 2010-11-04 | Electromagnetically actuated volume control valve, in particular for controlling the delivery volume of a high-pressure fuel pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2519732A1 EP2519732A1 (en) | 2012-11-07 |
EP2519732B1 true EP2519732B1 (en) | 2018-10-10 |
Family
ID=43478290
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10778969.5A Active EP2519732B1 (en) | 2009-12-29 | 2010-11-04 | Electromagnetically actuated metering control valve, particularly for controlling the flow of a high pressure fuel pump |
Country Status (6)
Country | Link |
---|---|
EP (1) | EP2519732B1 (en) |
KR (2) | KR101506475B1 (en) |
CN (1) | CN102686868B (en) |
DE (1) | DE102009055356A1 (en) |
ES (1) | ES2704993T3 (en) |
WO (1) | WO2011079989A1 (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011089288A1 (en) | 2011-12-20 | 2013-06-20 | Robert Bosch Gmbh | Flow control valve, and high pressure pump with flow control valve |
FR2991728B1 (en) * | 2012-06-08 | 2016-04-29 | Bosch Gmbh Robert | ELECTROMAGNETIC VALVE OF FUEL INJECTION SYSTEM |
SE536848C2 (en) * | 2012-12-20 | 2014-09-30 | Pmc Lubrication Ab | Valve for controlling fat supply |
DE102016214884A1 (en) * | 2016-08-10 | 2018-02-15 | Robert Bosch Gmbh | Electromagnetically operated suction valve and high-pressure fuel pump |
WO2019051767A1 (en) * | 2017-09-15 | 2019-03-21 | Robert Bosch Gmbh | Fuel injector and control valve thereof |
Family Cites Families (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19834120A1 (en) * | 1998-07-29 | 2000-02-03 | Bosch Gmbh Robert | Fuel supply system of an internal combustion engine |
JP2005299683A (en) * | 2001-11-27 | 2005-10-27 | Bosch Corp | Liquid flow control valve and needle anchor |
DE10220717A1 (en) * | 2002-05-10 | 2003-11-27 | Bosch Gmbh Robert | Solenoid valve, in particular quantity control valve for fuel systems of internal combustion engines |
JP3778882B2 (en) * | 2002-08-26 | 2006-05-24 | 株式会社日本自動車部品総合研究所 | Electromagnetic actuator |
DE10247145A1 (en) * | 2002-10-09 | 2004-04-22 | Robert Bosch Gmbh | Flow control device, in particular for a fuel injection device of an internal combustion engine |
DE10251014A1 (en) * | 2002-11-02 | 2004-05-19 | Robert Bosch Gmbh | Fuel dispensing unit for fuel injection system for internal combustion engine has shutoff sleeve in interior of valve piston and valve piston and shutoff sleeve form shutoff device |
JP2005511952A (en) * | 2002-11-27 | 2005-04-28 | 株式会社ボッシュオートモーティブシステム | Anchor for liquid flow control valve and mover, and fuel injection system |
JP2004301295A (en) | 2003-03-31 | 2004-10-28 | Denso Corp | Solenoid valve |
JP4293133B2 (en) | 2005-01-12 | 2009-07-08 | トヨタ自動車株式会社 | solenoid valve |
US7415969B2 (en) * | 2006-02-28 | 2008-08-26 | Caterpillar Inc. | Fuel injector having recessed check top |
JP4833820B2 (en) | 2006-12-25 | 2011-12-07 | 株式会社鷺宮製作所 | Capacity control valve, capacity variable compressor and air conditioner |
DE102008018018A1 (en) * | 2008-04-09 | 2009-10-15 | Continental Automotive Gmbh | Pump for conveying a fluid |
-
2009
- 2009-12-29 DE DE102009055356A patent/DE102009055356A1/en not_active Ceased
-
2010
- 2010-11-04 KR KR1020127016448A patent/KR101506475B1/en active IP Right Grant
- 2010-11-04 KR KR1020147032072A patent/KR101736081B1/en active IP Right Grant
- 2010-11-04 WO PCT/EP2010/066797 patent/WO2011079989A1/en active Application Filing
- 2010-11-04 EP EP10778969.5A patent/EP2519732B1/en active Active
- 2010-11-04 CN CN201080059939.5A patent/CN102686868B/en active Active
- 2010-11-04 ES ES10778969T patent/ES2704993T3/en active Active
Non-Patent Citations (1)
Title |
---|
None * |
Also Published As
Publication number | Publication date |
---|---|
CN102686868B (en) | 2015-06-17 |
CN102686868A (en) | 2012-09-19 |
KR101506475B1 (en) | 2015-03-27 |
DE102009055356A1 (en) | 2011-06-30 |
EP2519732A1 (en) | 2012-11-07 |
WO2011079989A1 (en) | 2011-07-07 |
KR20120096934A (en) | 2012-08-31 |
ES2704993T3 (en) | 2019-03-21 |
KR20140140131A (en) | 2014-12-08 |
KR101736081B1 (en) | 2017-05-16 |
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