WO2008068116A1 - Poussoir mécanique, en particulier pour pompe à carburant de moteur à combustion interne - Google Patents

Poussoir mécanique, en particulier pour pompe à carburant de moteur à combustion interne Download PDF

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Publication number
WO2008068116A1
WO2008068116A1 PCT/EP2007/061648 EP2007061648W WO2008068116A1 WO 2008068116 A1 WO2008068116 A1 WO 2008068116A1 EP 2007061648 W EP2007061648 W EP 2007061648W WO 2008068116 A1 WO2008068116 A1 WO 2008068116A1
Authority
WO
WIPO (PCT)
Prior art keywords
plunger
housing
bolt
plunger housing
insert plate
Prior art date
Application number
PCT/EP2007/061648
Other languages
German (de)
English (en)
Inventor
Stefan Dorn
Manfred Jansen
Norbert Radinger
Norbert Geyer
Karsten Kucht
Original Assignee
Schaeffler Kg
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Priority claimed from DE102006057246.7A external-priority patent/DE102006057246B4/de
Application filed by Schaeffler Kg filed Critical Schaeffler Kg
Priority to JP2009539687A priority Critical patent/JP5303468B2/ja
Publication of WO2008068116A1 publication Critical patent/WO2008068116A1/fr

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Classifications

    • 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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
    • F04B1/0404—Details or component parts
    • F04B1/0408—Pistons
    • 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
    • F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
    • F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
    • F02M59/102—Mechanical drive, e.g. tappets or cams
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L2305/00—Valve arrangements comprising rollers
    • F01L2305/02—Mounting of rollers

Definitions

  • the invention relates to a mechanical plunger, in particular for the lifting operation of a pump piston of a fuel pump of an internal combustion engine.
  • the plunger has a sleeve-shaped plunger housing, which is designed as Blechumformteil and is mounted longitudinally movably with a substantially cylindrical outer surface in a ram guide, and a rotatably mounted drive roller and a Hubübertragungsbauteil, which is made separately to the plunger housing and inserted into the plunger housing and a driven having lateral contact surface for the pump piston.
  • Such a plunger is apparent from the generic DE 103 45 089 A1.
  • the proposed there plunger serves as an actuating element of a known high-pressure fuel pump for lateral force-free transmission of a cam lift on the pump piston and has a formed as a sheet metal forming sleeve-shaped plunger housing. This has both a high lightweight and a considerable cost savings compared to the usually extruded ram housings such roller tappet.
  • the skilled person can afford these advantageous properties by comparing the plunger proposed in the cited document with a plunger, such as It is apparent from a directly extruded and thus relatively thick-walled plunger housing from DE 197 29 793 A1.
  • the plunger proposed in the first-mentioned publication nevertheless has some serious disadvantages in connection with the drive roller.
  • This essentially means that the drive roller is centerless mounted in the Hubübertragungsbauteil used in the ram housing and accordingly slides with its peripheral surface in a corresponding recess of the Hubübertragungsbauteils.
  • Such storage of the drive roller is known to be extremely difficult to tune, as a proper rotation of the drive roller can only be guaranteed if the contact friction between the cam and the drive roller under all operating conditions of the internal combustion engine or the fuel pump always greater than the contact friction between the drive roller and the stroke transmission member.
  • the present invention is therefore the object of a plunger of the type mentioned in such a way that the disadvantages mentioned are eliminated by simple means. Accordingly, the tappet should not only have a high lightweight and cost-saving potential, but also require as little drive power as possible with respect to the drive roller and at the same time the best possible operational reliability. Summary of the invention
  • a drive roller is to be provided centrally and optionally by means of rolling elements bearing bolt, wherein protruding from the drive roller end portions of the bolt are supported in pin bosses of the plunger housing.
  • the plunger is both particularly lightweight and inexpensive to produce and also has a required drive power significantly reducing and reliable rolling contact against the driving cam.
  • the role superimposed and in turn supported in the pin boss bolt serves as an expense-neutral captive for the drive roller on the plunger.
  • the Hubübertragungsbauteil should be made as a stamped part or as a stamped bent part of sheet metal material.
  • the Hubübertragungsbauteil made of sheet metal material is not only the basis for a further reduction in the manufacturing cost of the plunger, but may also differ in terms of the choice of material from the plunger housing, that the sheet metal materials used for these two components optimally on the different functional requirements, optionally with suitable surface coatings are tuned.
  • a stroke transmission component produced by other known production methods, such as extruding, casting, sintering or plastic injection molding with a material selection, heat and / or surface treatment adapted to the functional requirements, is also possible.
  • the plunger housing is double-walled in the region of the pin bosses, wherein the pin bosses are arranged in tabs of the plunger housing, which are bent parallel to the outer circumferential surface of the plunger housing extending into this.
  • a tappet housing designed in this way is particularly advantageous if it has a completely cylindrical outer circumferential surface and the pin is fixed in a form-fitting manner in the pin bosses by clamping its front ends. For in this case, a deformation of the tabs caused by the caulking process has no or only a slight influence on the cylinder shape of the tappet housing required for guiding in the tappet guide.
  • the plunger housing should have a recess into which a the outer shell surface of the plunger housing radially superior Vertexfeld- is used to align the drive roller in the plunger guide and consequently for parallel alignment of the drive roller to the cam.
  • the plunger housing has radially recessed, flat sections in the region of the pin bosses relative to the cylindrical shape. It may be appropriate for Umformischen reasons to locally cut off the flat portions relative to the cylindrical outer surface, so that the flat portions each jump back forming a substantially crescent-shaped gap in the plunger housing.
  • the Hubübertragungsbauteil should be formed as supported on axial shoulders of the plunger housing in the direction of the drive roller insert plate, wherein the axial shoulders are formed on an inner circumferential surface of the plunger housing by the flat portions.
  • a lifting transmission component designed in this way can be produced in a cost-effective manner in particular as a stamped part made of sheet metal material with corresponding edge layer hardening by stamping.
  • an insert plate produced as a fine stamping part is particularly suitable for cost-saving functional extension to the effect that the anti-rotation body aligning the plunger in the ram guide is formed by an integrally formed on the insert plate and guided by the recess of the plunger housing projection.
  • the insert plate is planar and supported with two opposite circular segment-shaped support sections on the axial shoulders. While the circular segment-shaped support sections serve for safe support of the insert plate on the axial shoulders, are formed by intervening, deviating from the circular segment shape exemptions from the inner surface of the plunger housing for venting and oil return during operation of the plunger.
  • the insert plate may be box-shaped in such a way that the insert plate is supported on the axial shoulders with ribs extending on two opposite support sections and has two opposing stiffening angles running between the support sections.
  • a gain in stiffness achieved as a result of the just formed insert plate can alternatively also be produced in that the insert plate has a trough-shaped construction and has an inner section with a U-shaped cross section surrounded by a planar frame section.
  • the frame section with two opposite support sections on the axial shoulders, which are each formed as a straight edge and the gap adjacent extending end face supported.
  • a likewise trough-shaped insert plate of high stiffness, which is supported at the same time with low contact pressures on the axial shoulders, can also be given by the insert plate with two opposite support sections with U-shaped cross section at the axial shoulders, each as a substantially U-shaped cross-section complementary arc-shaped and the gap adjacent extending end face are trained det, is supported.
  • a hinge corresponding support caused by component tolerances and leading to squeezing edge beams misalignment or misalignment of extending on the insert plate contact surface and the pump piston to each other in a simple manner at least in the direction of rotation of the insert plate can be compensated.
  • the insert plate should be used by means of a running on the inner circumferential surface of the plunger housing Lose securing device form fit in the plunger housing.
  • this comprises a support plate supporting circlip and on the inner surface of the plunger housing extending and preferably produced by stamping, knob-like projections on which the circlip is supported. Due to the production and assembly sequence of the ram, the extremely cost-saving retaining ring not only makes this variant a further cost-saving potential for the ram, but only in a late manufacturing step does the finished insert plate be mounted in the likewise finished ram housing, considerable latitude in the largely independent choice of material in the insert plate and the plunger housing.
  • the positively locking captive securing device also allows a slight Verkippspiel the insert plate in the plunger housing, so that thereby also caused by component tolerances slight misalignment or misalignment of the contact surface and the pump piston can be balanced each other.
  • An alternative captive securing device is intended to comprise projections which run on the inner circumferential surface of the tappet housing and are preferably made by caulking, and recesses formed in the insert plate, in which the projections engage.
  • the caulking of the projections expediently takes place in the soft state of the plunger housing with the insert plate mounted therein.
  • a caulking of the projections in the hard state of the plunger housing is conceivable, which again largely due to the then late mounting of the insert plate in the plunger housing in the choice of material for the insert plate and the plunger housing.
  • the Hubübertragungsbauteil is designed as supported on the bolt roller carrier, which with a contact surface having the bottom part and with this angled in the direction of the bolt side parts a side in the direction of the bolt U-. forms a shaped cross-section.
  • the end portions of the bolt are supported both in the pin bosses of the plunger housing and in pin bosses of the side panels.
  • the pin bosses of the plunger housing and / or the pin bosses of the side pieces are dimensioned in relation to the bolt such that the roller carrier is pivotally inserted around or with the pin in the plunger housing.
  • the force acting on the drive roller force in a Lekskraftkompo- nente which is transmitted via the bolt on the roller carrier and its contact surface on the pump piston, and in a transverse force component, the over the bolt on the plunger housing and from the ram guide is transmitted, split. Accordingly, it is possible, the plunger housing only taking into account the transverse force to be transmitted make the component particularly thin-walled and thus particularly lightweight.
  • the pivotable suspension of the roller carrier on the bolt also enables at least partial compensation of misalignment or misalignment of the contact surface and the pump piston with respect to one another.
  • the bottom part may be substantially flat, the roller carrier having stiffening angles extending from the bottom part transversely to the side parts.
  • a likewise high dimensional stiffness of the roller carrier can alternatively also be produced by virtue of the fact that the bottom part is formed like a vane with a cross-section U-shaped transversely to the direction of the bolt.
  • the side parts should be passed through windows in the plunger housing and embrace outer sides of the planar sections in favor of a large width of the drive roller with a correspondingly high load rating or life, wherein the windows are each formed in a transition section between the cylindrical shape and the flat portions.
  • the applicability of the plunger should not be limited to an actuator of a fuel pump, but also extend to elements with this related function, as is the case, for example, in mechanical tappets for actuating gas exchange valves of the internal combustion engine.
  • the contact surface is formed as a dome-shaped recess in the bottom part and, for example, serves to receive a co-moving with the gas exchange valve push rod with a spherical end portion.
  • the bolt is fixed axially end-to-end in the pin bosses with end portions radially expanded, wherein the bolt is solidified over its entire longitudinal extent with a core hardness of at least 58 HRC and the end sections are widened by means of radial point rivets.
  • the through-hardened bolt Despite the high brittleness of the through-hardened bolt in the region of its end sections, it is sufficiently deformable by means of radial point rivets-a method known per se, which is explained in more detail in the description of exemplary embodiments of the invention-in view of the axially form-fitting fixing of the bolt in the pin bosses ,
  • the fully through-hardened bolt requires only little effort for the heat treatment and can, for example, be taken from the extremely cost-effective mass production of rolling elements.
  • such a bolt only or predominantly positively acting, ie be set without or without significant support by a press fit in the pin bosses without its radially expanded end portions are exposed to abrasion due to rotation of the bolt, as in caulked pin with end face uncured end portions the case may be.
  • the radially yakge- rietete bolt should be fixed only positively with axial play and / or radial play in the pin bosses. Due to lack of, acting on the pin bosses clamping forces between the end portions of the bolt on the one hand and / or lack of radial force of a press fit on the pin bosses on the other hand, not only a high dimensional stability of compared to a F doublpressteil relatively thin-walled plunger housing can be ensured, but it can in favor of low production costs and a special passport or surface quality of the pin eyes are waived.
  • the radial clearance allows a self-rotation of the bolt in the pin bosses in favor of its more uniform surface stress in the drive roller, so that in this way the safety against surface wear in the contact area between the pin and drive roller including optionally provided rolling elements is further increased.
  • the plunger housing has at least one of a bead-like indentation on the outer circumferential surface of the plunger housing outgoing, extending transversely to the bolt and directed to the drive roller Anspritzbohrung for lubrication and cooling of the drive roller up.
  • Figure 1A shows a first embodiment of a plunger according to the invention with insert plate in exploded perspective view
  • FIG. 1B shows the assembled ram according to FIG. 1A in a perspective sectional view
  • Figure 1 C the plunger according to Figure 1 B in perspective oblique bottom view of the contact surface
  • FIG. 2A shows a second embodiment of a plunger according to the invention with insert plate in exploded perspective view
  • FIG. 2B shows the assembled ram according to FIG. 2A in a perspective sectional view
  • FIG. 2C shows the plunger according to FIG. 2B in a perspective oblique bottom view
  • Figure 2D shows the plunger according to Figure 2B in longitudinal section
  • Figure 3A shows a third embodiment of a plunger according to the invention with insert plate in exploded perspective view
  • FIG. 3B shows the assembled ram according to FIG. 3A in a perspective sectional view
  • FIG. 3C shows the plunger according to FIG. 3B in a perspective oblique bottom view
  • Figure 4A shows a fourth embodiment of a plunger according to the invention with insert plate in exploded perspective view
  • FIG. 4B shows the assembled ram according to FIG. 4A in a perspective sectional view
  • FIG. 5A shows a fifth exemplary embodiment of a tappet with roller carrier according to the invention in an exploded perspective view
  • FIG. 5B shows the assembled ram according to FIG. 5A in a perspective sectional view
  • Figure 6A shows a sixth embodiment of a ram according to the invention with roller carrier in exploded perspective view
  • FIG. 6B shows the assembled ram according to FIG. 6A in a perspective oblique bottom view
  • FIG. 6C shows a longitudinal section of the plunger according to FIG. 6B in a mounting representation
  • Figure 7 shows a seventh embodiment of an inventive
  • Figure 8 shows an eighth embodiment of a plunger according to the invention with dome-shaped contact surface in longitudinal section
  • FIG. 9B shows the assembled ram according to FIG. 9A in a perspective sectional view
  • FIG. 10A shows a tenth embodiment of a tappet with roller carrier according to the invention in an exploded perspective view
  • Figure 11 shows the characteristic movement of a Radialhuiniettechnikmaschines in a schematic representation.
  • a mechanical plunger 101 for the lifting operation of a pump piston, not shown here, of a fuel pump of an internal combustion engine.
  • the plunger 101 has a deep-drawn Chumformteil sleeve-shaped and thin-walled trained plunger housing 102 which is mounted longitudinally movably with a substantially cylindrical outer surface 3 in a ram guide of the fuel pump.
  • a low-friction mating surface for a likewise not shown cam of a camshaft of the internal combustion engine is a mounted on a bolt 4 by means here as needles rolling elements 5 mounted drive roller 6, supported from the drive roller 6 outstanding end portions 7 of the bolt 4 in pin bosses 8 of the plunger housing 102 are.
  • the plunger 101 further comprises a formed as an insert plate 109 and an output side contact surface 10 for the pump piston exhibiting Hubübertragungsbauteil 11 and designed as a snap ring retaining ring 112 as part of a running on the inner circumferential surface 13 of the plunger housing 102 Verliertechnischsvorraum 114, by means of which the insert plate 109 acting positively is fixed in the plunger housing 102.
  • the captive securing device 114 comprises not only the securing ring 112 on the inner circumferential surface 13 of the tappet housing 102 extending knob-like projections 115, the number here is four and which are made by stamping on the outer circumferential surface 3 of the plunger housing 102 and on which the insert plate 109th over which this interlocking circlip 112 is supported.
  • the insert plate 109 produced here as a flat, fine stamped part is supported in the direction of the drive roller 6 with two opposite circular segment-shaped support sections 116 on axial shoulders 117, which are formed on the inner lateral surface 13 of the plunger housing 102 by flat sections 118 projecting radially in the region of the pin bosses 8 relative to the cylindrical shape are.
  • On the circumference of the insert plate 109 four recesses 19 are further recognizable, which is free for the opposite to the projections 115 insertion the insert plate 109 are required in the plunger housing 102.
  • a projection 20 integrally formed on the insert plate 109 which is guided through a recess 121 of the plunger housing 102 and whose outer circumferential surface 3 projects radially beyond, serves as an anti-rotation body 122 accommodated by a complementary longitudinal groove of the plunger guide for the radial alignment of the plunger 101 in the plunger guide for the purpose of parallel alignment of the drive roller 6 to the cam.
  • the insert plate 109 is secured within the plunger housing 102 against rotation by the projection 20.
  • the insert plate 109 is formed with straight edges 23 so that during operation of the plunger 101 for venting and oil return or circulation always sufficient transfer between the insert plate 109 and the inner circumferential surface 13 of the plunger housing 102 is formed - as it is also in the rest other embodiments of the invention is always the case.
  • FIGS. 2A to 2D disclose a plunger with insertion plate 209 designated as 201 as a second exemplary embodiment of the invention. This differs from the previously described plunger 101 substantially by the design of the insert plate 209, which is box-shaped here and is supported with raised on their support portions 216 extending ribs 24 on axial shoulders 217 of a plunger housing 202. The contact forming between the ribs 24 and the axial shoulders 217 acts on the one hand to prevent rotation of the insert plate 209 in the plunger housing 202.
  • the insert plate 209 has some radial play relative to the inner lateral surface 13 of the plunger housing 202, so that a radial displacement of the insert plate 209 in FIG Direction of the bolt 4 due to the angled contact between the ribs 24 and the axial shoulders 217 to a slight pivoting of the contact surface 10 leads. Consequently, this can be aligned on the pump piston so that component tolerance-related misalignment or misalignment between the pump piston and the contact surface 10 are compensated in the pivot plane.
  • the contact surface 10 is at least partially convex cylindrical in the direction of a connecting line between the ribs 24 in order to ensure edge support and low-pressure contact with the pump piston transversely to the pivoting of the insert plate 209.
  • a high dimensional stability of the insert plate 209 is provided by two opposing stiffening angles 225 extending between the support sections 216, wherein additionally a contact surface 10 formed in the direction of the pump piston contributes to the form stiffness of the insert plate 209 produced here as a stamped bent part.
  • the plunger 201 further differs from the plunger 101 in that here an anti-rotation body 222 designed as a separate component is fastened in a recess 221 of the plunger housing 202.
  • Another distinguishing feature consists in a Anspritzbohrung 26 for lubrication and cooling of the drive roller 6.
  • the Anspritzbohrung 26 is based on a bead-like indentation 27, which communicates with a Schmierstoffzu 1500kanal in the ram guide and on the outer circumferential surface 3 of the tappet housing 202 is stamped centrally between planar sections 218, so that the injection bore 26 extends transversely to the pin 4 and is directed onto the drive roller 6.
  • the stroke transmission component 11 of a plunger 301 shown in FIGS. 3A to 3C is likewise designed as an insert plate 309. This is formed trough-shaped with respect to the insert plate 209 and has an inner section 29 with a U-shaped cross-section enclosed by a flat frame section 28 and with a contact surface 10 which is also raised in the direction of the pump piston.
  • flat sections 318 of a plunger housing 302 in this case jump back radially relative to the cylindrical shape, so that in each case a substantially crescent-shaped gap 30 is formed in the plunger housing 302.
  • This shaping is expediently carried out by local cutting of the plunger housing 302 during the sheet metal forming process, whereby axial shoulders 317 in the form of here each straight-edged and at the gap 30 adjacent the extending end faces 331 arise.
  • the insert plate 309 is supported with opposite support portions 316 of the frame portion 28 in the direction of the drive roller 6. In order to ensure, taking into account a load-related deflection of the insert plate 309 whose support is still free from edge supports on the end faces 331, they are slightly convex in the radially inward direction.
  • a further distinguishing feature of the plunger 301 relates to its loss-securing device 314 for the insert plate 309, which here comprises protrusions 315 produced by local caulking on the diameter-stepped inner surface 13 of the plunger housing 302 and recesses 32 of corresponding number formed on the circumference of the insert plate 309, in which the projections 315 engage both axially and radially positively.
  • the caulking for producing the projections 315 is advantageously carried out in the soft state of the plunger housing 302, so that for this type of Verliertechnischsvoriques 314 a relation to the plungers 101 and 201 modified manufacturing and assembly sequence of the plunger 301 is required.
  • the insert plate 309 is to be mounted before the heat treatment of the plunger housing 302 in this and both together with the plunger housing 302 to harden and then to grind.
  • a plunger 401 shown in FIGS. 4A and 4B differs from the previously described plunger 301 in that an insert plate 409 is continuous-trough-shaped here, so that its opposite support sections 416 have a U-shaped cross-section and are designed to be substantially arcuately complementary thereto
  • Axial shoulders 417 of a plunger housing 402 in the form of circular arc-shaped end faces 431 are supported.
  • a good nestling of the support portions 416 to the front surfaces 431 is achieved in that the end faces 431 are slightly more curved than the support portions 416.
  • the U-shaped cross section of the support portions 416 has a so-called Gothic profile with two circular arcs offset at the center.
  • FIGS. 5A and 5B disclose another plunger 501 according to the invention.
  • this is designed here as a roller carrier 533 which forms a U-shaped cross-section in the direction of the bolt 4 with a contact surface 10 having the contact surface 10, here flat bottom part 534 and with this angled in the direction of the bolt 4 side parts 535
  • the roller carrier 533 is articulated to the bolt 4 by means of bolt eyes 36 extending in the side parts 535, so that the end sections 7 of the bolt 4 are supported both in the bolt eyes 8 of a tappet housing 502 and in the pin bosses 36 of the side parts 535.
  • the pin bosses 8 of the tappet housing 502 and / or the pin bosses 36 of the side members 535 are dimensioned relative to the pin 4 so that the roller carrier 533 is pivotally inserted around or with the pin 4 in the tappet housing 502.
  • the stiffness required for the transmission of the longitudinal force component of the formed as stamped and bent part of sheet metal material and consequently also low-mass roller carrier 533 can be generated in this embodiment, that this from the flat bottom portion 534 transversely to the side members 535 outgoing stiffening angle 525 has.
  • FIGS. 6A and 6B A further embodiment of a tappet 601 according to the invention with roller carrier 633 is shown in FIGS. 6A and 6B.
  • the roller carrier 633 has a trough-shaped bottom part 634 with a transverse to the direction of the bolt 4 U-shaped cross-section.
  • the resulting stiffness of the roller carrier 633 is further increased by stiffening angle 625 and by ribs 37 which extend parallel to the U-shape and on both sides of the raised at the bottom portion 634 in the direction of the pump piston contact surface 10 formed.
  • the plungers 501 and 601 differ in the design of their plunger housings 502 and 602 in the manner already explained, according to which flat portions 618 of the plunger housing 602 each radially back to the cylindrical shape to form the crescent-shaped gap 30, while the flat portions 518 of Tappet housing 502 are formed with a closed transition to the cylindrical shape.
  • the plunger guide and the pump piston already mentioned at the beginning can be seen from the longitudinal sectional view of the plunger 601 according to FIG. 6C and designated by 38 and 39, respectively.
  • FIGS. 7 and 8 with tappets 701 and 801 it is clear that the tappets with roller carriers have a high degree of flexibility with regard to a modular system, as illustrated below.
  • the plunger guides 38 allow the use of identical plunger housings 602 and 702, it is sufficient to use a different mounting dimension 40, ie the distance between the drive roller 6 and the contact surface 10, to use a roller support 633 and 733 different from a differential installation dimension 41.
  • the modular system allows the use of identical roller carriers 633 and 733 in then different ram housings 602 and 702.
  • a ram 801 shown in FIG. This has a roller carrier 833, the contact surface 10 is formed here as a dome-shaped recess 42 in a bottom part 834.
  • a recess 42 is suitable, for example, for receiving a pump piston which is of spherical design at the end or else also a push rod of a gas exchange valve drive which has a spherical end.
  • FIG. 9A and 9B Another embodiment of the invention is disclosed in Figures 9A and 9B with a plunger 901.
  • the plunger 901 has a plunger housing 902 with windows 43 which are each formed in a transition section 44 between the cylindrical shape and flat sections 918 and through which side parts 935 of a roller carrier 933 are passed, so that the side parts 935 engage around the flat sections 918 on the outside.
  • a significant advantage of this arrangement in an increased space for the width of the drive roller 6 whose Tragiere- or life increases with the width.
  • a further advantage can also be seen in the comparatively large-area, planar sections 918, which must be sufficiently wear-resistant as an axial contact surface for the drive roller 6.
  • FIGS. 10A and 10B Another tappet 1001 with roller carrier 1033 according to the invention is disclosed in FIGS. 10A and 10B.
  • the plunger 1001 has a plunger housing 1002, which is double-walled in the region of the pin bosses 8.
  • the pin bosses 8 are arranged in tabs 45 integrally formed on the plunger housing 1002 and extending parallel to the outer circumferential surface 3 of the plunger housing 1002 after the inward bending.
  • Side parts 1035 of the roller carrier 1033 surround the lugs 45 on the outside and therefore run between the inner circumferential surface 13 of the tappet housing 1002 and the tabs 45.
  • the inner shell surface 13 of the tappet housing 1002 can be provided with closely spaced tabs, so that then the side parts of a modified Roll carrier would run inside the tabs.
  • Openings 46 which pass through the outer circumferential surface 3 of the plunger housing 1002 in alignment with the pin bosses 8, serve only as mounting holes for inserting the pin 4 and for pushing out a plug, not shown, for holding the rolling elements 5 in the not yet mounted drive roller 6 and as access for a Forming tool, with which the end portions 7 of the assembled bolt 4 are radially expanded frontally to fix the bolt 4 in the pin bosses 8 axially positive fit.
  • this can be done both by means of known caulking processes and by means of the method known per se as radial point riveting and briefly described below.
  • the bolt 4 made of a bearing steel such as 100Cr6 is through-hardened over its entire longitudinal extent and has a Rockwell hardness HRC of at least 58 corresponding to a Vickers hardness HV of at least 650.
  • HRC Rockwell hardness
  • HV Vickers hardness
  • the lens shape results from the spatial movement of a riveting punch 47 made of hard metal here of a radial point riveting machine (not shown).
  • the longitudinal axis 48 of the riveting punch 47 follows a cyclical loop path 49, the envelope of which extends towards the workpiece, i. to the bolt 4 towards tapering circular cone forms.
  • the longitudinal axis 48 of the riveting punch 47 repeatedly passes through the central axis 50 of the circular cone. Due to the highly loaded contact between the face-side flat riveting punch 47 and the end portions 7 of the bolt 4, these are successively deformed radially at the end side.
  • the bolt 4 having a diameter of about 7.6 mm, was made of 100Cr6 grade bearing steel and set to a core hardness hardened by about 60 HRC.
  • the frontal deformation of the assembled bolt 4 was carried out on a hydraulic radial point machine with a flat riveting punch 12 (FIG. 11) at a riveting force of about 25 kN and a riveting time of about 2 sec., In each case at both end sections 7.
  • a subsequent measurement of the thus deformed bolt 4 showed a diameter-related expansion of the end portions 7 of only about 0.1 mm.
  • the fit clearance of the pin 4 in the pin bosses 8 was chosen so large that the pin 4 was fixed after the radial point rivets both with noticeable axial play and with a slight radial play in the pin bosses 8.
  • a deformation of the thin-walled tappet housing 602 that impairs the required cylindrical shape as a result of axially or radially acting on the pin bosses 8 joining stresses could hereby be completely excluded.
  • the axial force required for pressing out the pin 4 from the pin bosses 8 - despite the comparatively small widening of the end sections 7 of the pin 4 - with an average of 2700 N was at the level of reference components with pinched off ends.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention propose un poussoir mécanique (101, 201, 301, 401, 501, 601, 701, 801, 901, 1001), en particulier pour actionner la course du piston (39) de la pompe à carburant d'un moteur à combustion interne, qui présente un boîtier de poussoir (102, 202, 302, 402, 502, 602, 702, 902, 1002) en forme de douille configuré comme pièce façonnée en tôle et un galet d'entraînement (6) monté à rotation. Un goujon (4) qui centre le galet d'entraînement est prévu et les parties d'extrémité (7) du goujon qui débordent du galet d'entraînement sont soutenues dans des oeillets de goujon (8) du boîtier du poussoir.
PCT/EP2007/061648 2006-12-05 2007-10-30 Poussoir mécanique, en particulier pour pompe à carburant de moteur à combustion interne WO2008068116A1 (fr)

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JP2009539687A JP5303468B2 (ja) 2006-12-05 2007-10-30 特に内燃機関の燃料ポンプのためのメカニカルタペット

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DE102006057246.7A DE102006057246B4 (de) 2006-12-05 2006-12-05 Mechanischer Stößel insbesondere für eine Kraftstoffpumpe einer Brennkraftmaschine, mit umgebogenen Laschen zur Abstützung des Bolzens der Antriebsrolle
DE102006057246.7 2006-12-05
US86877406P 2006-12-06 2006-12-06
US60/868,774 2006-12-06
US88725807P 2007-01-30 2007-01-30
US60/887,258 2007-01-30

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WO2010026463A1 (fr) * 2008-09-04 2010-03-11 Toyota Jidosha Kabushiki Kaisha Appareil de levage à roulette, son procédé de fabrication et pompe à liquide
WO2010130496A1 (fr) * 2009-05-13 2010-11-18 Robert Bosch Gmbh Pompe enfichable
WO2011003865A1 (fr) * 2009-07-08 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Procédé de fabrication d'un composant de transmission de course
DE102010026360A1 (de) 2010-07-07 2012-01-12 Schaeffler Technologies Gmbh & Co. Kg Stössel
EP2711546A1 (fr) * 2012-09-24 2014-03-26 Continental Automotive GmbH Agencement de poussoir et pompe
WO2014117762A1 (fr) * 2013-01-29 2014-08-07 Schaeffler Technologies AG & Co. KG Poussoir
WO2016023665A1 (fr) * 2014-08-14 2016-02-18 Continental Automotive Gmbh Pompe à carburant haute pression et dispositif agissant sur la pression
EP3026255A1 (fr) * 2014-11-27 2016-06-01 Aktiebolaget SKF Système mécanique formant un suiveur de came ou un culbuteur, actionneur de soupape ou pompe d'injection comprenant un tel système mécanique et procédé de fabrication dudit système
EP3056696A1 (fr) * 2015-02-10 2016-08-17 Aktiebolaget SKF Système mécanique formant un poussoir suiveur de came ou un culbuteur, actionneur de soupape ou pompe d'injection comprenant un tel système mécanique et procédé de fabrication dudit système
EP3073066A1 (fr) * 2015-03-27 2016-09-28 Aktiebolaget SKF Suiveur de came, pompe à injection et actionneur de soupape comprenant un tel suiveur de came et procédé de fabrication
EP3165722A1 (fr) * 2015-11-05 2017-05-10 Aktiebolaget SKF Dispositif de poussoir à galet avec insert
CN106988827A (zh) * 2015-11-24 2017-07-28 斯凯孚公司 具有润滑剂供给孔的凸轮从动辊装置以及润滑方法
CN108590909A (zh) * 2018-05-09 2018-09-28 杭州新坐标科技股份有限公司 轻量化高压泵滚子挺柱

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BR112013014653B1 (pt) * 2010-12-13 2021-01-05 Eaton Coporation tucho e método para fabricar um tucho
WO2013119214A1 (fr) * 2012-02-08 2013-08-15 Koyo Bearings Usa Llc Mécanisme suiveur
DE102012202566B4 (de) * 2012-02-20 2021-12-23 Schaeffler Technologies AG & Co. KG Rollenstößel mit fingerartigem Bolzenhalterungsmittel
DE102012217801A1 (de) * 2012-09-28 2014-04-03 Schaeffler Technologies Gmbh & Co. Kg Verfahren zur Montage eines Stößel
US10047641B2 (en) 2014-06-20 2018-08-14 Otics Corporation Roller lifter
JP6411275B2 (ja) 2015-04-10 2018-10-24 株式会社オティックス リフタの回り止め構造
US10119607B2 (en) 2016-04-15 2018-11-06 Koyo Bearings North America Llc Follower mechanism
WO2017181002A2 (fr) 2016-04-15 2017-10-19 Koyo Bearings North America Llc Poussoir porvu d'une coupelle interne reçue sur une palette
US9863382B2 (en) * 2016-05-25 2018-01-09 Hangzhou Xzb Tech Co., Ltd High pressure oil pump roller tappet
US11149593B2 (en) 2019-10-03 2021-10-19 Koyo Bearings North America Llc Tappet assembly with formed anti-rotation alignment device
US11143059B2 (en) 2019-10-03 2021-10-12 Koyo Bearings North America Llc Tappet assembly with unground outer cup

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WO2002020953A1 (fr) * 2000-09-09 2002-03-14 Mahle Ventiltrieb Gmbh Poussoir a galet pour moteur a combustion interne
DE10345089A1 (de) * 2003-09-26 2005-04-21 Bosch Gmbh Robert Stößel für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einem Stößel
DE102004061680A1 (de) * 2004-12-22 2006-08-03 Schaeffler Kg Ventiltrieb für eine Brennkraftmaschine

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WO2010026463A1 (fr) * 2008-09-04 2010-03-11 Toyota Jidosha Kabushiki Kaisha Appareil de levage à roulette, son procédé de fabrication et pompe à liquide
KR101161698B1 (ko) 2008-09-04 2012-07-09 도요타 지도샤（주） 롤러리프터, 롤러리프터제조방법 및 액체펌프
US8863615B2 (en) 2008-09-04 2014-10-21 Toyota Jidosha Kabushiki Kaisha Roller lifter, roller lifter production method and liquid pump
WO2010130496A1 (fr) * 2009-05-13 2010-11-18 Robert Bosch Gmbh Pompe enfichable
WO2011003865A1 (fr) * 2009-07-08 2011-01-13 Schaeffler Technologies Gmbh & Co. Kg Procédé de fabrication d'un composant de transmission de course
CN102421994A (zh) * 2009-07-08 2012-04-18 谢夫勒科技有限两合公司 升程传递部件的制造方法
US8590149B2 (en) 2009-07-08 2013-11-26 Schaeffler Technologies AG & Co. KG Method of manufacturing a lift transmitting component
DE102010026360A1 (de) 2010-07-07 2012-01-12 Schaeffler Technologies Gmbh & Co. Kg Stössel
WO2012004037A1 (fr) 2010-07-07 2012-01-12 Schaeffler Technologies Gmbh & Co. Kg Poussoir
DE102010026360B4 (de) * 2010-07-07 2020-12-03 Schaeffler Technologies AG & Co. KG Stößel mit einer Verdrehsicherung
US8863716B2 (en) 2010-07-07 2014-10-21 Schaeffler Technologies Gmbh & Co. Kg Tappet
EP2711546A1 (fr) * 2012-09-24 2014-03-26 Continental Automotive GmbH Agencement de poussoir et pompe
US9410518B2 (en) 2013-01-29 2016-08-09 Schaeffler Technologies AG & Co. KG Tappet
WO2014117762A1 (fr) * 2013-01-29 2014-08-07 Schaeffler Technologies AG & Co. KG Poussoir
WO2016023665A1 (fr) * 2014-08-14 2016-02-18 Continental Automotive Gmbh Pompe à carburant haute pression et dispositif agissant sur la pression
US10294905B2 (en) 2014-08-14 2019-05-21 Continental Automotive Gmbh High-pressure fuel pump and pressure control device
EP3026255A1 (fr) * 2014-11-27 2016-06-01 Aktiebolaget SKF Système mécanique formant un suiveur de came ou un culbuteur, actionneur de soupape ou pompe d'injection comprenant un tel système mécanique et procédé de fabrication dudit système
US9644729B2 (en) 2014-11-27 2017-05-09 Aktiebolaget Skf Mechanical system forming a cam follower or a rocker arm, injection pump or valve actuator comprising such a mechanical system and method for manufacturing such a mechanical system
EP3056696A1 (fr) * 2015-02-10 2016-08-17 Aktiebolaget SKF Système mécanique formant un poussoir suiveur de came ou un culbuteur, actionneur de soupape ou pompe d'injection comprenant un tel système mécanique et procédé de fabrication dudit système
US10006425B2 (en) 2015-03-27 2018-06-26 Aktiebolaget Skf Cam follower, injection pump and valve actuator having such a cam follower, and manufacturing method
EP3073066A1 (fr) * 2015-03-27 2016-09-28 Aktiebolaget SKF Suiveur de came, pompe à injection et actionneur de soupape comprenant un tel suiveur de came et procédé de fabrication
CN107035590A (zh) * 2015-11-05 2017-08-11 斯凯孚公司 具有插入件的凸轮从动辊装置
US10113449B2 (en) 2015-11-05 2018-10-30 Aktiebolaget Skf Cam follower roller device with insert
EP3165722A1 (fr) * 2015-11-05 2017-05-10 Aktiebolaget SKF Dispositif de poussoir à galet avec insert
CN107035590B (zh) * 2015-11-05 2021-02-05 斯凯孚公司 具有插入件的凸轮从动辊装置
CN106988827A (zh) * 2015-11-24 2017-07-28 斯凯孚公司 具有润滑剂供给孔的凸轮从动辊装置以及润滑方法
US10718240B2 (en) 2015-11-24 2020-07-21 Aktiebolaget Skf Cam follower roller device with lubricant supply holes and lubricating method
CN108590909A (zh) * 2018-05-09 2018-09-28 杭州新坐标科技股份有限公司 轻量化高压泵滚子挺柱
CN108590909B (zh) * 2018-05-09 2023-08-18 杭州新坐标科技股份有限公司 轻量化高压泵滚子挺柱

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