EP3390804A1 - Valve, in particular suction valve, in a high-pressure pump of a fuel injection system - Google Patents
Valve, in particular suction valve, in a high-pressure pump of a fuel injection systemInfo
- Publication number
- EP3390804A1 EP3390804A1 EP16784928.0A EP16784928A EP3390804A1 EP 3390804 A1 EP3390804 A1 EP 3390804A1 EP 16784928 A EP16784928 A EP 16784928A EP 3390804 A1 EP3390804 A1 EP 3390804A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- anchor bolt
- armature
- recess
- valve
- outer diameter
- 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.)
- Withdrawn
Links
- 239000000446 fuel Substances 0.000 title claims abstract description 27
- 238000002347 injection Methods 0.000 title claims abstract description 11
- 239000007924 injection Substances 0.000 title claims abstract description 11
- 238000000034 method Methods 0.000 claims description 33
- 238000003780 insertion Methods 0.000 claims description 20
- 230000037431 insertion Effects 0.000 claims description 20
- 230000008569 process Effects 0.000 claims description 15
- 230000008859 change Effects 0.000 claims description 9
- 238000004519 manufacturing process Methods 0.000 claims description 6
- 230000002441 reversible effect Effects 0.000 claims description 4
- 238000001816 cooling Methods 0.000 claims description 3
- 230000006835 compression Effects 0.000 description 11
- 238000007906 compression Methods 0.000 description 11
- 230000008901 benefit Effects 0.000 description 10
- 230000003247 decreasing effect Effects 0.000 description 5
- 230000015572 biosynthetic process Effects 0.000 description 4
- 238000005304 joining Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000001419 dependent effect Effects 0.000 description 3
- 238000003825 pressing Methods 0.000 description 3
- 230000003746 surface roughness Effects 0.000 description 3
- 238000009826 distribution Methods 0.000 description 2
- 238000010297 mechanical methods and process Methods 0.000 description 2
- 230000000717 retained effect Effects 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 230000004323 axial length Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000012512 characterization method Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000003754 machining Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 230000005226 mechanical processes and functions Effects 0.000 description 1
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
- F02M59/368—Pump inlet valves being closed when actuated
-
- 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
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
- B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
- B23P11/00—Connecting or disconnecting metal parts or objects by metal-working techniques not otherwise provided for
-
- 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
- F02M59/367—Pump inlet valves of the check valve type being open when actuated
-
- 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
- F02M59/48—Assembling; Disassembling; Replacing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
- F04B7/0076—Piston machines or pumps characterised by having positively-driven valving the members being actuated by electro-magnetic 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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8061—Fuel injection apparatus manufacture, repair or assembly involving press-fit, i.e. interference or friction fit
Definitions
- Valve in particular suction valve, in a high-pressure pump of a fuel injection system
- the invention relates to a valve, in particular a suction valve, in particular in a high-pressure pump of a fuel injection system having a valve element which is movable between an open position and a closed position, with a magnet armature which is in mechanical contact with the valve element via an anchor bolt, wherein the Anchor bolt is connected by means of a press fit with the armature, wherein an actuating force is transmitted to the valve member by the anchor bolt.
- the invention relates to a pump, in particular a high pressure pump of a fuel injection system, in which the suction valve is used.
- the invention relates to a method for producing a valve.
- An electromagnetically controllable intake valve for a high pressure pump of a fuel injection system, in particular a common rail injection system, is known from DE 10 2013 220 593 AI. Furthermore, a high-pressure pump with such a suction valve from this document is known.
- the suction valve has a valve element which is movable between an open and a closed position and which is at least indirectly in contact with a magnet armature via an anchor bolt. By the magnet armature thus an actuating force can be transmitted to the valve element.
- the high-pressure pump has a pump housing with a housing part, in which a cylinder bore a pump piston is mounted hubbweweglich, which limits a pump working space in the cylinder bore.
- the pump working chamber can be connected to a fuel inlet via the suction valve and can be connected to a high-pressure accumulator via a check valve.
- the armature is part of an electromagnetic actuator, which also includes a magnetic coil.
- an electromagnetic actuator which also includes a magnetic coil.
- valve according to the invention, the pump according to the invention and the method according to the invention with the features of the independent claims have the advantage over the prior art that the anchor bolt is partially inserted into a recess of the magnet armature and the armature bolt and the magnet armature by means of a press fit in a contact region are connected to each other, and that the anchor bolt along the contact region has a, in particular continuously changing outer diameter.
- damage to the armature due to an inhomogeneous stress distribution can be avoided and the total surface area in the area of the press fit is increased.
- the connection of magnet armature and anchor bolt has an increased holding force and thus an increased strength, which in turn has an increase in the mechanical load capacity and thus an increased service life of the suction valve and thus of the entire high-pressure pump to the advantage.
- the inventive design of the valve or the pump further advantages over the prior art: It is advantageous that the magnet armature has a changing inner diameter in the region of the depression along the contact region. In this way, the total surface increases in the region of the press fit and thus the holding force between the armature and the anchor bolt can be increased, resulting in an increase of the mechanical load capacity.
- the outer diameter of the anchor bolt becomes smaller along the contact area in the direction of the depression of the magnet armature.
- the total surface of the interference fit and thus the holding force between the armature and the anchor bolt can be increased, which leads to an increase in mechanical strength.
- this advantageous expression of the anchor bolt it is possible by this advantageous expression of the anchor bolt to improve the assembly process and simplify, since this expression improves the leadership during assembly and the risk of tilting the component anchor bolt is reduced. As a result, the risk of accident during assembly is reduced and a possible pre-damage of the components anchor bolts and armature reduced by tilting during assembly, which in turn leads to reduced costs.
- the outer diameter of the anchor bolt along the contact area in the direction of the recess of the armature is larger. In this way, the surface of the formed pressing bandage can be increased while at the same time the surface tension per respective unit area on the component anchor bolt is reduced. This results in a better stress distribution on the component and thus a reduced risk of material fatigue and component failure.
- the inner diameter of the magnet armature in the region of the depression along the contact region in the direction of the anchor bolt is larger.
- the overall surface of the press fit and thus the holding force between the armature and the anchor bolt can be increased, which leads to an increase in the mechanical load capacity and thus leads to an increase in the life of the valve and thus of the pump.
- this advantageous expression of the magnet armature it is possible by this advantageous expression of the magnet armature to improve the assembly process and simplify, since this expression improves the leadership during assembly and the risk of tilting the component anchor bolt is reduced. hereby reduces the risk of accident during assembly and reduces possible damage to the components anchor bolts and armature by tilting during assembly, which in turn leads to reduced costs.
- the change in the outer diameter of the anchor bolt and / or the change in the inner diameter of the armature in the region of the recess has a linear course. This makes it possible to tune the components magnet armature and anchor bolt in the contact area of the interference fit to each other so that the interference fit forms a maximum frictional connection, while the press-in force can be kept low.
- the change in the outer diameter of the anchor bolt and / or the change in the inner diameter of the armature in the region of the recess has a curved course. This makes it possible that the surface is further increased in the region of the formed interference fit. Due to this further enlarged surface, the holding force between the component armature and anchor bolt can be further increased.
- the anchor bolt with the outer diameter changing in the direction of the longitudinal axis into the depression of the magnet armature which has a small inside diameter relative to the outer diameter of the anchor bolt, at least with respect to a subsection of the part of the anchor bolt to be inserted into the depression Armature before, during or after the insertion of the anchor bolt is widened to form a non-positive connection by a press fit in the contact area to the anchor bolt.
- This advantageous embodiment of the method makes it possible to reduce the press-in force required to bring the anchor bolt into the depression of the magnet armature either to a much smaller value, which is required without the use of this method, or to completely reduce the press-in force ,
- the inner diameter of the magnet armature is increased in the contact region before the insertion of the anchor bolt, in particular, the process of increasing the inner diameter reversible is and temporarily limited and the inner diameter moves back elastically after the successful insertion of the anchor bolt.
- a further advantageous embodiment of the method for producing a valve is that an enlargement of the inner diameter of the armature takes place in particular by a thermal process. This allows the press-fit forces to be reduced during assembly and to reduce assembly costs.
- a further advantage of the embodiment of the method according to the invention is that the anchor bolt is reduced in its outer diameter by a thermal process, in particular by cooling, in particular in the region forming the interference fit, wherein the process of reducing the outer diameter is reversible and temporary limited occurs.
- FIG. 2 shows a section of the pump, designated II in FIG. 1, in an enlarged view with a suction valve,
- FIG. 3 shows a section of the suction valve designated III in FIG. 2 in an enlarged view.
- FIG. 4 shows a section of the magnet armature according to a first embodiment.
- Figure 5 shows a section of the armature according to a second embodiment.
- 6 shows a section of the magnet armature according to a third embodiment.
- Figure 7 shows a section of the anchor bolt according to a first embodiment.
- FIG 8 shows a section of the anchor bolt according to a second embodiment.
- FIG 9 shows a section of the anchor bolt according to a third exemplary embodiment.
- Figure 11 is a section of the anchor bolt according to a fifth embodiment, which corresponds to the prior art
- Figure 12 shows an inventive method for joining the components armature and anchor bolt
- FIG. 1 shows a sectional view of a high-pressure pump 1 shown schematically, which is designed as a high-pressure fuel pump and is preferably installed in a common-rail injection system.
- the high pressure pump 1 is provided by a fuel low pressure system having at least one tank, a filter and a low pressure pump, provided fuel in a high-pressure accumulator, from which the fuel stored there is taken from fuel injectors for injection into the associated combustion chambers of an internal combustion engine.
- the supply of the fuel to the pump working space via an electro-magnetic controllable suction valve 2, wherein the electromagnetically controllable suction valve is installed on the high-pressure pump.
- the high-pressure pump 1 has a pump housing 3 with a camshaft space 5.
- a camshaft space 5 protrudes a camshaft 7 with a trained example as a double cam cam 9 in.
- the camshaft 7 is mounted in two radial bearings arranged on both sides of the cam 9. The one
- the Bearing is arranged in the pump housing 3 housing bearing 11 and the second bearing is a Flantschers 13.
- the flange 13 is disposed in a connected to the pump housing 3 flange 15 which closes the camshaft space 5 to the environment tight.
- the flange 15 has a continuous opening through which a drive-side end section 17 of the camshaft 7 protrudes.
- the drive-side end portion 17 has, for example, a cone on which a drive wheel is placed and secured.
- the drive wheel is formed for example as a pulley or gear.
- the drive wheel is driven by the internal combustion engine directly or indirectly, for example via a belt drive or a gear transmission.
- a tappet guide 19 is further inserted, in which a roller 21 having a roller tappet 23 is inserted.
- roller 21 runs on the cam 9 of the camshaft 7 during a rotational movement of the same and the roller tappet 23 is thus in the tappet guide 19 translationally moved up and down.
- the roller tappet 23 cooperates with a pump piston 18, which is also arranged to be movable up and down in a translatable manner in a cylinder bore 29 formed in a pump cylinder head 27.
- a plunger spring chamber 31 formed by the plunger guide 19 and the pump bore 29 a plunger spring 33 is arranged, which is supported on the one hand on the pump cylinder head 27 and on the other hand on the roller plunger 23 and a permanent contact of the roller 21 on the cam 9 in the direction of the camshaft 7 ensures.
- a pump working space 35 is formed in extension of the pump piston 18, into which fuel is introduced via the electro-magnetic controllable intake valve 2.
- the introduction of the fuel takes place during a downward movement of the pump piston 18, while in an upward movement of the pump piston 18 in the pump working space 35 befindaji fuel is conveyed via a high-pressure outlet 39 with an inserted outlet valve 16 via a further high-pressure line into the high-pressure accumulator.
- the high-pressure pump 1 is fuel-lubricated as a whole, with the fuel being conveyed by the low-pressure system into the camshaft space 5, which is fluidly connected to the intake valve 2.
- This electro-magnetic controllable suction valve 2 and its functionality will be described below. The illustrated in Fig.
- the piston-shaped valve element 14 attached to the high pressure pump 1 electromagnetically controllable suction valve 2, has a piston-shaped valve member 14 which is acted upon in the closing direction by the spring force of a second compression spring 12.
- the piston-shaped valve element 14 has a shaft 25, in particular a cylindrically shaped shaft 25, and an enlarged head 34.
- the enlarged head 34 of the valve element 14 is arranged on the pump piston 18 side facing.
- the pump cylinder head 27 has a valve seat 36 in the contact region to the closed valve element 14.
- the piston-shaped valve element 14 is guided via the shaft 25 in a bore 38 in the pump cylinder head 27 and has the enlarged head 34 in diameter relative to the shaft 25.
- valve element 14 is a sealing surface 37 is formed, which comes in the closed position of the valve element 14 to the valve seat 36 in the pump cylinder head 27 to the plant.
- the pump working space 35 is disconnected from the fuel inlet 26 and no fuel can flow back.
- FIG. 2 which serves to actuate the suction valve 2 of the high-pressure pump 1:
- This has a magnetic armature 10 with a cylindrical outer contour and a central bore 32.
- a first compression spring 4 also protrudes into this central bore 32 of the armature 10, which exerts an axial force on the armature 10 to the valve member 14 out.
- the magnet armature 10 is also guided in a liftable axially movable in a carrier element 40. In the radial direction, the magnet armature 10 surrounds a magnetic coil 6, which forms a magnetic field when energized and thus can exert a magnetic force on the magnet armature 10.
- the valve element 14 is connected via an anchor bolt 8 in contact with the armature 10, wherein both elements are not connected to each other in the axial direction, but are held together only by magnetic forces and spring forces in abutment.
- the anchor bolt 8 is connected to the magnet armature 10 in that the armature bolt 8 is partially inserted into the magnet armature 10 and is non-positively connected to the armature 10 by means of a press fit 20.
- the elements magnet armature 10 and anchor bolt 8 form in particular a contact region 48.
- the first compression spring 4 presses on the anchor bolt 8 and the armature 10.
- the first compression spring 4 ensures in the de-energized state that the anchor bolt 8 acts on the valve element 14 and holds it in the open position. Although this acts against the second compression spring 12, but since the first compression spring 4 has a higher spring force than the second compression spring 12, the valve element 14 is held in the open state.
- the armature 10 moves against the force of the first compression spring 4 away from the valve member 14 to close the working air gap 28.
- By moving away the anchor bolt 8 loses the frictional contact with the valve element 14 whereby the valve element 14 moves by the force of the second compression spring 12 toward the closed state. In fully closed state of the valve element 14th this is the sealing surface 37 on the valve seat 36 and seals the pump chamber 35 from the fuel inlet 26 from.
- the electro-magnetically controllable suction valve 2 is opened and a connection of the pump working chamber 35 made with the fuel inlet 26, so that the pump working chamber 35 via the
- Suction valve 2 fuel is supplied.
- the fuel supplied to the pump working chamber 35 is compressed and fed to a high-pressure accumulator (not shown) via the outlet valve 16 arranged in the high-pressure outlet 39.
- a high-pressure accumulator not shown
- Suction valve 2 is closed when fuel delivery is to take place, and seals the pump working space 35 from the fuel inlet 26 from.
- the section III shown in Fig. 3 shows in detail that the anchor bolt 8 is pressed into the armature 10 to form a positive connection in the form of a press fit 20.
- the outer diameter 47 of the anchor bolt 8 in the contact region 48 at least at one point of its length in the insertion direction (V), must have a larger diameter than the smallest Inner diameter 45 of the armature 10 in the contact area.
- the carrier element 40 which serves as a guide and receiving element for the armature 10 and the anchor bolt 8.
- annular shoulder 30 is shown, which is in contact with the magnet armature 10 and prevents the anchor bolt 8 is pressed too far into the magenta tanker.
- the annular shoulder 30 ensures that the anchor bolt 8 can not be further pressed into the recess 24 of the magnet armature 10. It thus serves as an assembly aid to prevent too far pressing the anchor bolt 8 in the armature 10.
- the anchor bolt 8 in its interior a recess 22 which, with the magnet armature 10 facing side, is open.
- the anchor bolt 8 is in contact with the valve element 14 on the egg nen side and the anchor bolt 8 is in contact with the first compression spring 4 on the other side.
- the inner diameter 45 of the magnetic anchor 10 can be expanded prior to assembly of the anchor bolt 8 to a to ensure improved and simplified assembly process. This can be ensured in particular by a thermal process.
- FIGS. 4, 5 and 6 show different embodiments of the recess 24 of the armature 10, in which the anchor bolt 8 is inserted.
- 7 to 10 show sectional views of the anchor bolt 8, in which various embodiments of the outer diameter 47 of the anchor bolt 8 in the region of the press band 20 are shown.
- FIGS. 4 to 11 each show a center line 41 which at the same time forms the axis of rotation of the sectional view.
- two reference lines 43 extend parallel to the center line 41
- the two reference lines 49 are shown in FIGS. 7, 8 and 9.
- the reference lines 43 extend in FIG. 5 parallel to the center line 41 and extend the line in a continuation of the inner diameter 42 of the armature 10 in the sectional view forms.
- the reference lines 49 each extend parallel to the center line 41 and in extension of the line, which would form or form the constant course of the outer diameter 47 of the anchor bolt 8.
- the center line 41 and the reference lines 43 and the reference lines 49 are parallel to the insertion direction (V) of the anchor bolt. 8
- FIG. 4 shows, as a first exemplary embodiment in a sectional illustration of the magnet armature 10, that the region of the recess 24 of the magnet armature 10 in the insertion direction (V) of the armature bolt 8 has a constant profile 42 of the inside diameter 45 over the entire axial length.
- This shape of the magnet armature 10 in the contact region 48 of the press fit 20 has the function that the magnet armature 10 does not have to be additionally reworked by another Fertiguns Marin to change the contour of the inner diameter 45 of the armature 10.
- the formation of the interference fit 20 improving geometric expression can thus be moved into the anchor bolt 8.
- Fig. 5 shows a section of the armature 10 according to a second
- Embodiment wherein the magnet armature 10 in the insertion direction (V) of the Anchor bolt 8 over a portion of the length has a changing inner diameter 45 which discloses a linearean course 44.
- the part of the length of the magnet armature 10 which has a changing inside diameter 45 is the area facing the armature bolt 8.
- the linear course 44 of the changing inner diameter 45 extends at an angle ⁇ in relation to the reference line 43.
- FIG. 6 shows a section of the magnet armature 10 according to a third exemplary embodiment, wherein the magnet armature 10 has a changing inside diameter 45 in the direction of insertion (V) of the armature pin 8 over part of its length.
- the part of the length of the magnet armature 10 which has a changing inside diameter 45 is the area facing the armature bolt 8.
- This changing inner diameter 45 has an arbitrary nature, but in the insertion direction over the entire length has a decreasing inner diameter 45. In particular, this can be realized by a curved course 46.
- the function can be achieved that the strength of the connection between the anchor bolt 8 and the armature 10 is significantly increased. This is especially true for the expression of the interference fit 20 in the contact region 48, whereby the effect of the surface roughness of both elements is utilized to form the interference fit 20.
- FIG. 7 shows a section of the anchor bolt 8 according to a first embodiment, wherein the anchor bolt 8 in the insertion direction (V) over the entire length of the contact portion 48 of the press fit 20 has a decreasing outer diameter 47, however, has a linear course 44.
- the linear course 44 of the changing outer diameter 47 extends at an angle ⁇ in relation to the reference line 49.
- the recess 22 of the armature Bolzens 8 offers further functions described below:
- the recess 22 of the anchor bolt 8 reduces the weight, which is advantageous because the assembly armature 10 and anchor bolt 8 is in a high-frequency movement during operation of the pump 1 and by the weight savings through the recess 22, the inertia of the assembly can be reduced and further the necessary energy use for the electromagnetic control can be reduced.
- the recess 22 in the anchor bolt 8 also offers further advantages in the assembly in relation to the fact that it provides a certain elasticity of the component anchor bolt 8 in the region of the press assembly 20. On the one hand, this ensures that the
- the elasticity after successful insertion ensures that the outer diameter 47 of the anchor bolt 8 is pressed against the inner diameter 45 of the armature 10 reinforced, resulting in an improved adhesion in the Forming area of the press association 20.
- FIG. 8 shows a section of the anchor bolt 8 according to a second exemplary embodiment, wherein the anchor bolt 8 has a decreasing outside diameter 47 in the insertion direction (V) only over a part of the length of the contact area 48, but which has a linear course 44.
- the portion having a decreasing outer diameter 47 extends over less than half the length of the contact portion 48 and is located on the magnet armature 10 facing side of the anchor bolt. 8
- the anchor bolt 8 In the remaining part of the length of the contact region 48 with the magnet armature 10, the anchor bolt 8 has a constant outer diameter 47. This small part of the length, which has a decreasing outer diameter 47 is located on the magnet armature 10 facing side of the anchor bolt 8. The changing inner diameter 45 extends at an angle ⁇ in relation to the reference line 49.
- This shape of the anchor bolt 8 in the area of the press fit 20 has the function that the anchor bolt 8 is centered in the magnet armature 10 at the beginning of the press-fitting operation and the risk of tilting or tilting is reduced.
- the second embodiment of the anchor bolt 8 shown in FIG. 8 offers the advantage over the illustrated embodiment from FIG. 7 that less effort is required in the machining process. processing of the component is necessary.
- FIG. 9 A third embodiment is shown in Fig. 9, wherein the section of the anchor bolt 8 is shown.
- the anchor bolt 8 has in the insertion direction (V) over the entire length of the contact region 48 on a magnifying outer diameter 47, which has a linear course 44.
- the changing outer diameter 47 is at an angle ⁇ in relation to the reference line 43.
- This embodiment has the function that, especially in combination with the pre-assembly process, temporarily limited
- Fig. 10 shows a section of the anchor bolt 8 according to a fourth embodiment, wherein the anchor bolt 8 in the insertion direction (V) over the entire length of the contact portion 48 has a changing outer diameter, but which has a curved non-linear curve 46.
- the function of this embodiment is the surface in
- Fig. 11 shows a section of the anchor bolt according to the prior art.
- the section shown of the anchor bolt 8 of FIG. 11 serves as a reference and is combined in the prior art with the embodiment of the armature 10 of FIG. Therefore, this explicit combination of anchor bolt 8 of FIG. 11 and the armature 10 of FIG. 4 is not part of the inventive feature of this invention.
- 12 shows the method according to the invention for joining the components armature 10 and anchor bolt 8. The method has the goal that the anchor bolt, at least partially, is inserted into a recess of the magnet armature and the anchor bolt and the magnet armature by means of a press fit in a contact area connected to each other.
- the start of the method 1201 takes place in that in each case one component magnet armature 10 and a component Anchor bolt 8 in any embodiment, as shown in FIGS. 4 to 10, are selected.
- the actual assembly of the two components in particular by means of a mounting device, optionally additionally precedes the method steps 1202 and 1203:
- step 1202 the recess of the armature before and / or during insertion of the anchor bolt 8 in the recess 24th of the armature 10, in particular by a thermal or mechanical method.
- the mechanical process is carried out by the use of a tool.
- step 1203 the anchor bolt 8, which is inserted into the recess 24 of the armature 10, thermally treated.
- the outer diameter 47 of the anchor bolt 8 is reduced by a thermal process, in particular by cooling.
- method step 1204 the actual joining process of the components armature 10 and anchor bolt 8 takes place. It should be noted that the method steps 1202 and 1203 can each be used separately or in combination. By using the method steps 1202 and 1203, the required press-fit force is reduced.
- Method step 1205 describes the formation of the interference fit in the contact region of the magnet armature 10 and the anchor bolt 8 after the successful assembly in step 1204.
- the interference fit 20 between the magnet armature 10 and the anchor bolt 8 is formed, in particular, only in method step 1205.
- the pressing occurs, the surface roughness is largely retained, resulting in a tight fit of the interference fit.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015225770.3A DE102015225770A1 (en) | 2015-12-17 | 2015-12-17 | Valve, in particular suction valve, in a high-pressure pump of a fuel injection system |
PCT/EP2016/075531 WO2017102146A1 (en) | 2015-12-17 | 2016-10-24 | Valve, in particular suction valve, in a high-pressure pump of a fuel injection system |
Publications (1)
Publication Number | Publication Date |
---|---|
EP3390804A1 true EP3390804A1 (en) | 2018-10-24 |
Family
ID=57184481
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP16784928.0A Withdrawn EP3390804A1 (en) | 2015-12-17 | 2016-10-24 | Valve, in particular suction valve, in a high-pressure pump of a fuel injection system |
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Country | Link |
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US (1) | US20200284231A1 (en) |
EP (1) | EP3390804A1 (en) |
CN (1) | CN108368811A (en) |
DE (1) | DE102015225770A1 (en) |
WO (1) | WO2017102146A1 (en) |
Family Cites Families (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10038293A1 (en) * | 2000-08-05 | 2002-02-14 | Bosch Gmbh Robert | Fuel injector |
DE10256734B4 (en) * | 2002-07-03 | 2014-09-04 | Continental Teves Ag & Co. Ohg | Method for monitoring and detecting the mounting direction of the plunger of a solenoid valve and solenoid valve for the method |
JP3962951B2 (en) * | 2002-09-18 | 2007-08-22 | 株式会社デンソー | Fuel injection device |
US7128281B2 (en) * | 2004-06-03 | 2006-10-31 | Siemens Vdo Automotive Corporation | Modular fuel injector with a damper member and method of reducing noise |
DE102008042789A1 (en) * | 2008-10-13 | 2010-04-29 | Robert Bosch Gmbh | Fuel injector e.g. in-line fuel injector, for fuel injection system of internal-combustion engine of motor vehicle, has injection valve designed as split injection valve whose parts are joined with each other at side joint |
DE102013220593A1 (en) | 2013-10-11 | 2015-04-16 | Robert Bosch Gmbh | Electromagnetically controllable suction valve |
-
2015
- 2015-12-17 DE DE102015225770.3A patent/DE102015225770A1/en not_active Withdrawn
-
2016
- 2016-10-24 CN CN201680074051.6A patent/CN108368811A/en active Pending
- 2016-10-24 EP EP16784928.0A patent/EP3390804A1/en not_active Withdrawn
- 2016-10-24 WO PCT/EP2016/075531 patent/WO2017102146A1/en unknown
- 2016-10-24 US US16/063,449 patent/US20200284231A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
WO2017102146A1 (en) | 2017-06-22 |
CN108368811A (en) | 2018-08-03 |
DE102015225770A1 (en) | 2017-06-22 |
US20200284231A1 (en) | 2020-09-10 |
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