EP1723316B1 - Arbre a cames et procede pour produire un arbre a cames - Google Patents

Arbre a cames et procede pour produire un arbre a cames Download PDF

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Publication number
EP1723316B1
EP1723316B1 EP05715761A EP05715761A EP1723316B1 EP 1723316 B1 EP1723316 B1 EP 1723316B1 EP 05715761 A EP05715761 A EP 05715761A EP 05715761 A EP05715761 A EP 05715761A EP 1723316 B1 EP1723316 B1 EP 1723316B1
Authority
EP
European Patent Office
Prior art keywords
cam
support shaft
disk support
cam disk
camshaft
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.)
Expired - Fee Related
Application number
EP05715761A
Other languages
German (de)
English (en)
Other versions
EP1723316A1 (fr
Inventor
Alois Schmid
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mercedes Benz Group AG
Original Assignee
DaimlerChrysler AG
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
Application filed by DaimlerChrysler AG filed Critical DaimlerChrysler AG
Publication of EP1723316A1 publication Critical patent/EP1723316A1/fr
Application granted granted Critical
Publication of EP1723316B1 publication Critical patent/EP1723316B1/fr
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01L1/02—Valve drive
    • F01L1/04—Valve drive by means of cams, camshafts, cam discs, eccentrics or the like
    • F01L1/047—Camshafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D53/00—Making other particular articles
    • B21D53/84—Making other particular articles other parts for engines, e.g. connecting-rods
    • B21D53/845—Making camshafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H1/00—Making articles shaped as bodies of revolution
    • B21H1/18—Making articles shaped as bodies of revolution cylinders, e.g. rolled transversely cross-rolling
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21H—MAKING PARTICULAR METAL OBJECTS BY ROLLING, e.g. SCREWS, WHEELS, RINGS, BARRELS, BALLS
    • B21H7/00—Making articles not provided for in the preceding groups, e.g. agricultural tools, dinner forks, knives, spoons
    • B21H7/18—Making articles not provided for in the preceding groups, e.g. agricultural tools, dinner forks, knives, spoons grooved pins; Rolling grooves, e.g. oil grooves, in articles
    • B21H7/187—Rolling helical or rectilinear grooves
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J5/00—Methods for forging, hammering, or pressing; Special equipment or accessories therefor
    • B21J5/06—Methods for forging, hammering, or pressing; Special equipment or accessories therefor for performing particular operations
    • B21J5/12—Forming profiles on internal or external surfaces
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21K—MAKING FORGED OR PRESSED METAL PRODUCTS, e.g. HORSE-SHOES, RIVETS, BOLTS OR WHEELS
    • B21K1/00—Making machine elements
    • B21K1/06—Making machine elements axles or shafts
    • B21K1/12—Making machine elements axles or shafts of specially-shaped cross-section
    • 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
    • F01L2301/00—Using particular materials
    • 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
    • F01L2303/00—Manufacturing of components used in valve arrangements
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T29/00—Metal working
    • Y10T29/49—Method of mechanical manufacture
    • Y10T29/49229—Prime mover or fluid pump making
    • Y10T29/49293—Camshaft making
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/19—Gearing
    • Y10T74/1987—Rotary bodies

Definitions

  • the invention relates to a camshaft for an internal combustion engine with a cam disk support shaft on which a plurality of cams and a drive wheel are mounted, according to the closer defined in the preamble of claim 1.
  • the invention further relates to a method for producing a camshaft, in which on a cam carrier shaft a plurality of cams and at least one drive wheel are mounted.
  • camshafts which consist of several composite parts and are used in internal combustion engines for controlling the valve opening times, are referred to as built camshafts.
  • the cams are made by forging and may have a deviating from the circular opening.
  • the wave profile is formed by rolling and has elevations and depressions, which lead to circumferential and thus circular cross-sectional changes on the shaft.
  • rolling or rolling circumferential grooves are incorporated into the shaft, which raise due to material displacement circumferential beads.
  • the radial elevations extend annularly in the axial direction of the cam disk support shaft and have a radial excess with respect to the openings in the cam disks.
  • the cams on the edge have a chamfer so that they do not tilt when pressed onto the shaft.
  • the disadvantage here is that when pressing a cam on the carrier shaft, the Wellenwulste be smoothed in part and lose their excess due to the wear during the joining. For this reason, the cams are cleared in the described method for the purpose of introducing a rotationally symmetric micro-toothing in a complex manner.
  • cam carrier tube A relatively inexpensive, untreated steel material is used for the actual shaft, also referred to as a cam carrier tube, and a high quality, alloyed, hardenable ball bearing steel for the cams.
  • the support tube is upset at the end to which the camshaft drive gear is mounted for the purpose of wall thickness increase. At the ends and at the periphery there is a machining.
  • the cams are forged, machined and heat treated. After joining by hydroforming, the camshafts and the camshaft bearing seats are ground at different workpiece clamping stresses on the assembled camshaft.
  • camshafts for commercial vehicles must be able to transmit much larger torques. Reasons for this are the higher gas exchange forces due to the larger displacement.
  • camshafts for commercial vehicles there are requirements for special applications to propel auxiliary equipment via the camshaft, as required. the drive of hydraulic power units in agricultural machinery via the camshaft.
  • the hydroforming process has a significant limitation: It requires a hollow camshaft or a tube for receiving the cams, whose wall thickness must also not be too large, so that the required expander pressures remain manageable.
  • disadvantages in the starting material for the camshaft tube are predetermined.
  • the seamless drawn or longitudinally welded pipe is more expensive than the rolled all round material.
  • the tube must be formed at one end for reasons of strength and on one side a cap against oil leakage is required.
  • the tube compared to the solid shaft has a lower resistance torque against torsional and bending load, which may require larger sizes of shaft tube under comparable circumstances.
  • hydroforming technology binds a relatively high capital investment. This depends on the one hand with the hydraulic unit required to generate pressure, on the other hand, due to the very high operating pressures of 2500 to 3000 bar safety conditions that affect the investment costs. Another negative cost aspect of the hydroforming process is the ongoing operating costs.
  • the seals that seal the hydroforming lance against the camshaft tube are subject to considerable wear and must be replaced regularly, which in turn limits the plant utilization. Due to the non-positive transmission of the operating forces, hydroforming technology can also only to a limited extent be a reliable frictional shaft-hub connection for commercial vehicle camshafts.
  • the respective cam disk bore In order to be able to join the cam disks to the carrier pipe at known built-up camshafts, the respective cam disk bore must be preprocessed. This in turn can only be done in the unmolded state. In order to give the cams their final hardness, a mostly inductive heating with subsequent quenching in the water or oil bath is required.
  • a method for producing a built-up camshaft and a built-up camshaft of a shaft tube and deferred elements using the hydroforming are known from EP 0 265 663 B2 known.
  • the expansion of the shaft is hydraulically, whereby the shaft-hub connection comes about by adhesion.
  • the EP 0 374 389 B1 describes a method for the pretreatment of components of a built camshaft. There are described heat treatment measures for a pipe, which should make it possible that the pipe can be better expanded by hydroforming, or that the bearings get a higher hardness.
  • the cam disk carrier tube is preformed with different cross sections, so that during the subsequent expansion by hydroforming, only the tube sections which receive the cam disks are plastically deformed.
  • the pipe sections between the individual cams are only widened elastically.
  • a method of manufacturing a built-up camshaft using hydroforming and a built-up camshaft of a shaft tube and slidable members are disclosed in US Pat EP 0 265 663 A1 described.
  • the cams may have internal profiles in their openings, so that in addition to the adhesion and positive engagement, wherein the shaft forming tube is plastically deformed, while the cams are elastically expanded.
  • a composite camshaft in which a hollow shaft is machined by hydroforming.
  • the mounted on the shaft cams have a circular cross-section and a groove extending in the axial direction, which is at least partially filled in the hydroforming 'with the material of the shaft by plastic deformation, so that adjusts a positive rotational connection.
  • EP 0 730 705 B1 is a method of manufacturing a one-piece hollow camshaft is described in which by internal high pressure forming a tube in the die is widened so as to give a hollow camshaft. It is advantageous that no separate cams must be made. In contrast, it is disadvantageous that a heat treatment of the camshaft is required. In addition, in the areas of the cam tip, the wall thickness of the camshaft is particularly greatly reduced, which means that the strength requirements of a commercial vehicle with this technology can hardly be met.
  • a camshaft and a method for producing the same are in EP 0 970 293 B1 described.
  • thin cams are punched out of a metal sheet or a sheet metal strip.
  • a majority of these flat materials is assembled into sheet stacks above or next to one another.
  • a cam consists of several parts, which are finally joined by hydroforming on a pipe.
  • the cams may have a toothing or a notch-like profile on the circumference, which serves for rotational position orientation.
  • the from the EP 0 856 642 A1 known built camshaft is based on a longitudinal compression bandage, the joining partners are coated at the joints.
  • the coating can be a Phosphate layer, but also be adhesive. Also addressed is an unspecified profiling option.
  • the EP 0 839 990 B1 starts from a cam disk carrier shaft made by casting.
  • This shaft can be profiled at the locations where the cams are mounted.
  • the non-rotationally symmetrical profile is cast for the purpose of balancing and thus serves for better mass distribution of the shaft.
  • Cold forming of cast iron components is generally considered problematic due to material brittleness.
  • the profiling takes place with rolling rods which have longitudinal grooves.
  • the course of a groove in the rolling tool substantially follows the direction of movement of the rolling rod, which has the same profile in each cross-section transverse to the direction of movement.
  • the recess does not extend exactly in the direction of movement of the rolling rod, but is inclined by the thread pitch.
  • the cross sections of a rolling rod are then not completely equal over the length.
  • each rolling rod appears as a rectangle.
  • the longitudinal boundary lines of the side view of a rolling rod are parallel to the direction of movement.
  • the polygon addressed here as an example of the profile of the carrier wave deviating from the circular shape merely has the goal of approaching a circular shape.
  • composite camshaft is an indirect positive connection. It is used a corrugated clamping sleeve, which engages in a rotationally symmetrical shaft toothing and in a likewise rotationally symmetrical internal toothing on the cam disc opening.
  • the disadvantage here the handling of the clamping sleeve as a separate component.
  • the EP 0 580 200 B1 refers to the design of the cam for the purpose of lightweight construction, for which it is made of a thin sheet. However, this design is unlikely to be able to meet the strength requirements imposed on a camshaft.
  • a cam plate carrier tube is mechanically expanded by a pierced or solid mandrel. This requires that the cam disk carrier tube has different wall thicknesses before joining.
  • the joining surface may have recesses, pockets or a toothing. If a toothing is provided for the profile of the joint surface, this is to be attached to both joining partners, ie to the camshaft and to the cam disks.
  • crankshaft Another built crankshaft and a method for producing the same are in the DE 100 61 042 C2 described.
  • a tapered bow wedge is used.
  • a maximum of two crank webs can be added to each other by turning them on a crank pin.
  • the joining surfaces must be machined because of the high tolerance requirements. When joining the shaft is deformed substantially elastically, the connection is releasable again.
  • a single wedge-shaped arc profile formed of alternating peaks and valleys.
  • the cams are connected by the continuous increase in the radius of the cam carrier shaft with the same by means of a transverse press dressing, in which no special coating of the contact surfaces is required.
  • the attachment of the cams and the at least one drive wheel on the cam carrier shaft can be effected in a particularly simple manner by the drive wheel is rotated, while the cams are held in a rigid position.
  • the device required for this purpose can be particularly simple and the method described is very easy to master.
  • cam disk carrier shaft is designed as a solid shaft.
  • cam disk support shaft is formed as a hollow shaft. In this case, however, it should be provided that a mandrel is inserted into the hollow shaft for machining the cam disk carrier shaft.
  • a particularly simple deformation of the cam carrier shaft is possible if the depth of the recesses increases continuously with the increase of the elevations.
  • the method according to the invention allows for such great manufacturing tolerances that the soft machining of the bore of the cam disks can be dispensed with and thus a cost saving can be achieved. Moreover, in the present invention, it is only necessary to reshape the outer profile of the cam carrier shaft and not simultaneously the cams. This has the advantage that the contacting joining surface is larger and that no other aids, such as preliminary shrinking of the cams on the cam disk support shaft or subsequent expansion of the cam disk support shaft or even soldering of the joining surfaces is required.
  • the cams are slid according to the invention with play on the cam disk support shaft and fixed by a rotational movement.
  • the cam disk support shaft when mounting the cams and the at least one drive wheel on the cam disk support shaft, the cam disk support shaft is plastically deformed, the cams and the at least one drive wheel are elastically expanded.
  • this plastic deformation of the cam carrier shaft After the introduction of the depressions and elevations in the wave profile in order to form a Bogenkeilprofil by the resulting around the widening envelopes, this plastic deformation of the cam carrier shaft, the profile of the same during the joining can be partially smoothed again.
  • the connection between the cam carrier shaft and the cams thus substantially maintains the plastic by the plastic deformation of the shaft during the joining and by the elastic expansion of the hub. This is also advantageous if the individual cams have certain dimensional deviations, since these are compensated by the plastic deformation.
  • the elevations and depressions are introduced into the cam disk carrier shaft by means of two rod-shaped rolling tools moving relative to each other.
  • considerable cost savings over conventional methods such as hobbing or Wälzbineen are possible.
  • Compared to one Machined toothing produced advantageously has the shape of a toothing formed at room temperature advantageously higher strength.
  • the profile of the cam disk bore can be produced in an advantageous development of the method by forging in the required final quality, resulting in a further simplification of the production of the camshaft according to the invention.
  • camshaft 1 shows a built-up camshaft 1, which has a cam disk support shaft 2, on which a plurality of cam disks 3 as well as a camshaft drive wheel or drive wheel 4 are non-rotatably mounted on respective sections 2a thereof in the assembled state.
  • the camshaft 1 is used in a known manner to control the valve opening times in an internal combustion engine, not shown.
  • the cams 3, whose number depends on the internal combustion engine, each each have a bore 5 for mounting the same on the portions 2 a of the cam disk support shaft 2 and are generally offset by a certain angle to each other.
  • the camshaft 1 further has a plurality of bearings 6, in which it is supported under operating conditions in a crankcase of the internal combustion engine.
  • Fig. 1 the camshaft 1 is shown in its unassembled state, wherein the cam discs 3 and the drive wheel 4 each game s1, s2 and s3 with respect to the cam disk support shaft 2 have. It can be seen that the axial distance a of two adjacent cam disks 3 is greater than the width b of a cam disk 3.
  • a round steel material is preferably used, which may for example be hot rolled.
  • the requirements for the material of the cam carrier shaft 2 are a certain cold workability and toughness. A special heat treatment by tempering or a particularly high wear resistance is not required.
  • drawn round materials with a circular starting cross section as semifinished products for the cam disk carrier shaft 2. Hollow bodies such as pipes can also be used, whereby the entire camshaft 1 would receive a lower mass and could be dispensed with a deep hole to supply lubrication points.
  • a mandrel should be inserted into the hollow shaft in this case.
  • a tooth-like profile having a plurality of local elevations 7 and a corresponding number of local depressions 8, which are arranged alternately to one another, is introduced into the cam disk carrier shaft 2.
  • the camshaft carrier shaft 2 is generated by displacement of material as an envelope of all elevations 7, a wedge-shaped arc profile 9, wherein the outer contour of the sections 2a is performed similar to a toothing with interrupted wings.
  • the introduced into the shaft recesses 8 do not represent micro-toothing to increase the frictional engagement. They can best be understood as a macro-toothing.
  • the cam carrier shaft 2 For machining the cam carrier shaft 2, there are provided two rod-shaped rolling tools, hereinafter referred to simply as rolling rods 10 and 11, provided on their respective mutually facing sides with profiles provided with alternating gaps and projections and with relative movement the two rolling rods 10 and 11 by cold forming the elevations 7 and the recesses 8 in the cam disk support shaft 2 introduce.
  • the cam disk support shaft 2 is preferably clamped between not shown tips, whereupon the rolling rods 10 and 11 set in the direction of the arrows designated V 10 and V 11 synchronously and at the same speed in motion.
  • the cam carrier shaft 2 is rotated in accordance with the arrow V 2 and moves around its own axis several times during machining.
  • the length of the two rolling rods 10 and 11 thus corresponds to a multiple of the diameter or the circumference of the cam disk support shaft 2.
  • Movement of the rolling rods 10 and 11 exert a radial pressure on the cam disk support shaft 2 and reshape it. From Figures 2 to 5 it can be seen that the profile depth of the rolling rods 10 and 11 increases over the length thereof, whereby the required forming forces change.
  • the entire rolling process shown in the sequence in FIGS. 2 to 5 can be completed after a few seconds, after which the rolling rods 10 and 11 return to their original position. Then, the cam carrier shaft 2 can be moved along its longitudinal axis to the next reshaped portion 2a, whereupon the introduction of the ridges 7 and the recesses 8 to form the wedge-shaped arch profile 9 is repeated.
  • the wedge-shaped arc profile 9 resulting from the deformation ie the envelope around the elevations 7, is embodied as an Archimedean or logarithmic spiral.
  • mathematical functions of higher order such as the Fermat, Galilean or hyperbolic spiral, sinusoidal spiral, Lemniscate, quadratrix or others, would be considered for the wedge-shaped arch profile 9, the function itself being of secondary importance. All that matters is that the wedge-shaped arch profile 9 is an opening function widening in polar coordinates with the rotation angle and deviating from the circular shape. The center of this function does not necessarily coincide with the axis of rotation of the Cam disk carrier shaft 2 coincide, so that eccentric spirals are possible.
  • two rolling rods 10 and 11 are respectively provided to support the cam disk support shaft 2 during the rolling process and to dissipate the rolling forces.
  • the rolling rods 10 and 11 are geometrically identical and are arranged with such an offset to each other, which corresponds to half the central circumference of the cam disk support shaft 2.
  • the rolling rods 10 and 11 can be optimized so that the required forming work for introducing the wedge-shaped arc profile 9 in the cam disk support shaft 2 evenly distributed on both rolling rods 10 and 11.
  • the cam carrier shaft 2 can be indirectly driven by the rolling motion of the rolling rods 10 and 11 thereof.
  • the rolling rods 10 and 11 are made of hardened steel and have the width b of the cams 3.
  • the recesses can be introduced into the rolling rods 10 and 11 by known machining techniques, including, for example, surface grinding and deep grinding with a correspondingly profiled grinding wheel.
  • the grinding wheel profile in turn can be incorporated into the grinding wheel, for example via the CNC-controlled dressing by means of diamond tile.
  • cam disk carrier shaft 2 For each section 2a to which a cam disc 3 is attached to the cam disk support shaft 2, as indicated above, a separate, to be performed after each forming operation is provided, to which the cam disk support shaft 2 remains taut. However, between the forming operations, the cam disk carrier shaft 2 must be repositioned in its rotational position corresponding to the required rotational angle offset of the cams 3 and optionally axially displaced, including the rotary drive, by the distance a + b of the mutually adjacent cam disks 3.
  • FIGS. 7, 8 and 9 show an alternative forming method for forming the wedge-shaped arch profile 9 into the sections 2 a of the cam disk carrier shaft 2.
  • a die 13 is provided which, in the present case, has three mutually movable die parts 13a, 13b and 13c with a respective profile which forms the elevations 7 and the depressions 8.
  • the die 13 is formed by the illustrated closing and opening movement of the die parts 13 a, 13 b and 13 c, the cam disk support shaft 2 under swelling or pulsating pressurization, for example by hammering.
  • the die parts 13a, 13b and 13c each have the width b of the cams 3.
  • the die parts 13a, 13b and 13c perform a radial movement relative to the cam disk support shaft 2, wherein the force introduction for the deformation of the material by means of a known linearly guided actuators can be done hydraulically, pneumatically or electromechanically.
  • the individual profile cross sections of the cam disk support shaft 2, ie the sections 2a to be reshaped, are formed successively, for which purpose the cam disk support shaft 2 is brought into a new angular position each time prior to forming.
  • Nockenin.3 is not in the figures shown. These can be forged, for example, wherein the forged contour is expediently close to the final contour of the cam discs 3. It is then only necessary to machine the outer functional surface of the cams 3 for valve control. Incidentally, this also applies to the bearing points 6 of the cam disk support shaft 2 according to the assembly of the camshaft 1 described below. A production of the cam disks 3 by casting or sintering is also possible. As can be seen in FIGS. 10 to 17, the inner profile of the bores 5 of the cam disks 3 is adapted to the elevations 7 and thus to the enlargement of the outer radius of the cam disk support shaft 2 and thus to the wedge-shaped arch profile 9.
  • the bore 14 of the drive wheel 4 also substantially corresponds to the bore 5 of the cam discs 3.
  • the inner profile of the bore 5 of the cam discs 3 is mirror-inverted to the inner profile of the bore 14 of the drive wheel 4.
  • FIGS. 10 and 11, 12 and 13, 14 show and FIGS. 15 and 16 and 17 show the sequence in a possible embodiment of the attachment of the cams 3 and the drive wheel 4 on the cam carrier shaft 2.
  • FIG. 10 shows that the drive wheel 4 is clamped by means of three tensioning elements 15.
  • the clamping elements 15 are part of a rotary device, not shown in its entirety, which has a rotary drive, which is preferably regulated and has a monitoring of the angular position of the clamping elements 15 and thus the drive wheel 4.
  • the cam disk support shaft 2 is likewise set in rotation by the angle ⁇ 2 by positive entrainment.
  • the initial joining play s2 likewise reduces to 0, which can be seen in FIG. Due to the dimensional tolerances of the degradation of the initial mating clearance s2 is achieved at each cam 3 at a different time or at a different angular position of the drive wheel 4.
  • the torque introduced during the joining by the drive wheel 4 into the cam disk carrier shaft 2 causes a plastic deformation of that shaft profile, which is wrapped around by the drive wheel 4.
  • the initial width of the elevations d1 in FIG. 14 also increases here to the width d2 in accordance with FIG. 16.
  • the bore 14 of the drive wheel 4 is also increased by the assembly torque elastically expanded.
  • the bore 14 of the drive wheel 4 has a greater radial extent than the bores 5 of the cam discs 3.
  • the corresponding design of the geometry parameters ensures that all non-circular wave profiles deform simultaneously during the assembly rotation by the angle ⁇ 3. With suitable measures should be prevented that the drive wheel 4 during joining under the action of the joining forces on the cam disk support shaft 2 slipped.
  • the rotation control of the rotary device shuts off the rotational movement of the drive wheel 4, whereby the mounting torque drops to zero.
  • the cams 3 and the drive wheel 4 spring back in the radial direction and partially remove their elastic expansion again. They exert on the plastically deformed cam disk support shaft 2 a lasting radial pressure which prevents the release of the individual joint connections of the cam disks 3 against the cam disk support shaft 2 and the drive wheel 4 against the cam disk support shaft 2.
  • the force-locking axial displacement fuses.
  • the finished built camshaft 1 is produced, whereby the bearings 6 and the outer functional surfaces can be machined by known finishing processes, for example by centerless circular grinding for the bearing points 6 and by cam shape grinding for the outer contour of the joined cam disks 3.
  • the camshaft 1 Under operating conditions preferably on the same direction of rotation as the drive wheel 4 during assembly on the cam disk support shaft 2. Accordingly, the transmission of the camshaft drive torque from the drive wheel 4 via the cam disk carrier shaft 2 takes place on the cam disks 3 in a form-fitting manner.
  • the pitch of the elevations 7 and the recesses 8 and the formation of the tooth shapes are extremely selected in the figures.
  • the deviation of the wedge-shaped arc profile 9 from the circular shape will be less, with a smaller difference of the largest radius of the sections 2a from the smallest radius, ie a smaller slope of the wedge-shaped arc profile 9 leads to a better self-locking.
  • the twist angle ⁇ 3 can reach the size of 180 ° and more.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (14)

  1. Arbre à cames pour un moteur à combustion interne, comprenant un arbre porteur de disques à cames sur lequel sont agencés plusieurs disques à cames et une roue d'entraînement, le rayon extérieur de l'arbre porteur de disques à cames se modifiant en continu dans celles des portions dans lesquelles sont agencés les disques à cames, les disques à cames présentant un perçage dont le rayon intérieur se modifie en continu,
    caractérisé en ce que
    dans celles des portions (2a) dans lesquelles sont agencés les disques à cames (3), l'arbre porteur de disques à cames (2) est pourvu en alternance de bossages (7) et de renfoncements (8) qui forment un profil arqué (9) en forme de coin sur la périphérie de la portion (2a) de l'arbre porteur de disques à cames (2), les bossages (7) agrandissant en continu le rayon extérieur de l'arbre porteur de disques à cames (2), en ce que le perçage (5) des disques à cames (3) est adapté à l'agrandissement du rayon extérieur de l'arbre porteur de disques à cames (2), et en ce que précisément un profil arqué (9) en forme de coin est prévu autour de la périphérie de l'arbre porteur de disques à cames (2) et du perçage (5) des disques à cames (3).
  2. Arbre à cames selon la revendication 1.
    caractérisé en ce que
    la distance axiale (a) de deux disques à cames voisins (3) est supérieure à la largeur (b) d'un disque à cames (3).
  3. Arbre à cames selon la revendication 1 ou 2,
    caractérisé en ce que
    le profil intérieur du perçage (5) des disques à cames (3) est réalisé à symétrie inversée par rapport au profil intérieur d'un perçage (14) de la roue d'entraînement (4).
  4. Arbre à cames selon la revendication 1, 2 ou 3,
    caractérisé en ce que
    l'arbre porteur de disques à cames (2) est réalisé sous forme d'arbre plein.
  5. Arbre à cames selon la revendication 1, 2 ou 3,
    caractérisé en ce que
    l'arbre porteur de disques à cames (2) est réalisé sous forme d'arbre creux, un mandrin étant inséré dans l'arbre creux pour usiner l'arbre porteur de disques à cames (2).
  6. Arbre à cames selon l'une des revendications 1 à 5,
    caractérisé en ce que
    la profondeur des renfoncements (8) augmente en continu au fur et à mesure de l'agrandissement des bossages (7).
  7. Arbre à cames selon l'une des revendications 1 à 6,
    caractérisé en ce que
    le profil arqué (9) en forme de coin est réalisé à la manière d'une spirale d'Archimède ou d'une spirale logarithmique.
  8. Procédé pour fabriquer un arbre à cames, dans lequel on agence plusieurs disques à cames et au moins une roue d'entraînement sur un arbre porteur de disques à cames,
    caractérisé en ce que
    dans celles des portions (2a) de l'arbre porteur de disques à cames (2), sur lesquelles on agence les disques à cames (3), on réalise en alternance des bossages (7) et des renfoncements (8) de telle sorte que la périphérie de la portion (2a) de l'arbre porteur de disques à cames (2) forme à titre d'enveloppante un profil arqué (9) en forme de coin qui agrandit en continu le rayon extérieur de l'arbre porteur de disques à cames (2), en ce que l'on ménage dans les disques à cames (3) un perçage (5) qui est adapté à l'agrandissement du rayon extérieur de l'arbre porteur de disques à cames (2), et en ce que l'on agence les disques à cames (3) et ladite au moins une roue d'entraînement (4) par rotation en sens opposés sur l'arbre porteur de disques à cames (2), les disques à cames (3) et ladite au moins une roue d'entraînement (4) et/ou l'arbre porteur de disques à cames (2) étant déformés élastiquement.
  9. Procédé selon la revendication 8,
    caractérisé en ce que
    lors de l'agencement des disques à cames (3) et de ladite au moins une roue d'entraînement (4) sur l'arbre porteur de disques à cames (2), l'arbre porteur de disques à cames (2) est déformé plastiquement, les disques à cames (3) et ladite au moins une roue d'entraînement (4) étant évasés élastiquement.
  10. Procédé selon la revendication 8 ou 9,
    caractérisé en ce que
    pour agencer les disques à cames (3) et ladite au moins une roue d'entraînement (4) sur l'arbre porteur de disques à cames (2), on fait tourner la roue d'entraînement (4) tandis que l'on retient les disques à cames (3) dans une position fixe.
  11. Procédé selon la revendication 8, 9 ou 10,
    caractérisé en ce que
    l'on réalise les bossages (7) et les renfoncements (8) par façonnage à froid dans l'arbre porteur de disques à cames (2).
  12. Procédé selon la revendication 11,
    caractérisé en ce que
    l'on réalise les bossages (7) et les renfoncements (8) dans l'arbre porteur de disques à cames (2) au moyen de deux outils de galetage (10, 11) en forme de barreau se déplaçant l'un par rapport à l'autre.
  13. Procédé selon la revendication 11,
    caractérisé en ce que
    l'on réalise les bossages (7) et les renfoncements (8) dans l'arbre porteur de disques à cames (2) par martelage dans une matrice (13).
  14. Procédé selon l'une des revendications 8 à 13,
    caractérisé en ce que
    l'on réalise les disques à cames (3) par forgeage.
EP05715761A 2004-03-11 2005-03-05 Arbre a cames et procede pour produire un arbre a cames Expired - Fee Related EP1723316B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004011815A DE102004011815A1 (de) 2004-03-11 2004-03-11 Nockenwelle und Verfahren zur Herstellung einer Nockenwelle
PCT/EP2005/002339 WO2005088082A1 (fr) 2004-03-11 2005-03-05 Arbre a cames et procede pour produire un arbre a cames

Publications (2)

Publication Number Publication Date
EP1723316A1 EP1723316A1 (fr) 2006-11-22
EP1723316B1 true EP1723316B1 (fr) 2007-07-18

Family

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EP05715761A Expired - Fee Related EP1723316B1 (fr) 2004-03-11 2005-03-05 Arbre a cames et procede pour produire un arbre a cames

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Country Link
US (1) US7290515B2 (fr)
EP (1) EP1723316B1 (fr)
DE (2) DE102004011815A1 (fr)
WO (1) WO2005088082A1 (fr)

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DE102007012756A1 (de) * 2007-03-16 2008-09-18 Muhr Und Bender Kg Verfahren zum Herstellen von gebauten Nockenwellen
DE102009025023A1 (de) 2009-06-10 2010-12-16 Neumayer Tekfor Holding Gmbh Verfahren zur Herstellung einer Nockenwelle und entsprechende Nockenwelle
DE102011087049A1 (de) * 2011-11-24 2013-05-29 Mahle International Gmbh Verfahren zum Fügen von Bauelementen auf einer Welle
DE102011079584A1 (de) * 2011-07-21 2013-01-24 Mahle International Gmbh Nockenwelle und zugehöriger Nocken
DE102011117849A1 (de) * 2011-11-08 2013-05-08 Neumayer Tekfor Holding Gmbh Verfahren zur Fertigung einer Nockenwelle und entsprechende Nockenwelle
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CN112526925B (zh) * 2020-11-16 2022-12-16 中国航发西安动力控制科技有限公司 基于三维凸轮型面实体化模型偏差补偿的型面精加工方法

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Also Published As

Publication number Publication date
DE102004011815A1 (de) 2005-09-29
US7290515B2 (en) 2007-11-06
US20070006834A1 (en) 2007-01-11
DE502005001066D1 (de) 2007-08-30
WO2005088082A1 (fr) 2005-09-22
EP1723316A1 (fr) 2006-11-22

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