EP1723316A1 - Arbre a cames et procede pour produire un arbre a cames - Google Patents

Arbre a cames et procede pour produire un arbre a cames

Info

Publication number
EP1723316A1
EP1723316A1 EP05715761A EP05715761A EP1723316A1 EP 1723316 A1 EP1723316 A1 EP 1723316A1 EP 05715761 A EP05715761 A EP 05715761A EP 05715761 A EP05715761 A EP 05715761A EP 1723316 A1 EP1723316 A1 EP 1723316A1
Authority
EP
European Patent Office
Prior art keywords
cam
cam disk
shaft
support shaft
disks
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.)
Granted
Application number
EP05715761A
Other languages
German (de)
English (en)
Other versions
EP1723316B1 (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

Links

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 carrier shaft, on which a plurality of cam disks and a drive wheel are attached, according to the type defined in the preamble of claim 1.
  • the invention further relates to a method for producing a camshaft, in which on a cam disk carrier shaft several cam disks and at least one drive wheel are attached.
  • camshafts which consist of several assembled parts and are used in internal combustion engines to control the valve opening times, are referred to as built-up camshafts.
  • the wave profile is deformed by means of rollers and has elevations and depressions that lead to circumferential and thus circular cross-sectional changes on the shaft.
  • circumferential grooves are machined into the shaft, which due to material displacement raise circumferential beads.
  • the radial elevations extend in a ring shape in the axial direction of the cam disk carrier shaft and have a radial oversize compared to the openings in the cam disks.
  • the so-called hydroforming process is often used in the production of other camshafts, which can result in considerable cost savings.
  • the main advantage of the built camshaft using the hydroforming process compared to conventional solutions is the reduction in material costs.
  • a relatively inexpensive, untreated steel material is used for the actual shaft, which is also referred to as the cam disk support tube, and a high-quality, alloyed, hardenable ball bearing steel for the cam disks.
  • the carrier tube is compressed at the end to which the camshaft drive wheel is attached for the purpose of increasing the wall thickness. At the ends and on the circumference there is a machining.
  • the cam disks are forged, machined and heat treated. After joining by means of internal high pressure forming, the cam forms and the camshaft bearing seats are ground in different workpiece clamps on the assembled camshaft.
  • camshafts for commercial vehicles must be able to transmit significantly higher torques. The reasons for this are the higher gas exchange forces due to the larger displacement. There are also 'for commercial vehicle engines requirements of special applications to power on the camshaft, if necessary auxiliary equipment, such as the drive of hydraulic units in agricultural machinery on the camshaft.
  • the internal high-pressure forming process has a considerable limitation: it requires a hollow camshaft or a tube for accommodating the cam disks, the wall thickness of which, moreover, must not be " too large so that the required expansion pressures remain manageable
  • the seamless drawn or the longitudinally welded pipe is more expensive than the rolled round material .. - It must be taken into account that the pipe must be formed at one end for strength reasons and a sealing cover on one side
  • the tube has a lower moment of resistance to torsion and bending stress compared to the solid shaft, which under certain circumstances may require larger dimensions for the shaft tube with a comparable load.
  • Another problem is that the internal high pressure forming technology ties up a relatively high investment in the plant. On the one hand, this is related to the hydraulic unit required to generate pressure, on the other hand, due to the very high operating pressures of 2500 to 3000 bar safety requirements that influence the system costs. Another negative cost aspect of the hydroforming process is the running operating costs.
  • the seals that seal the internal high-pressure forming lance against the camshaft tube are subject to considerable wear and must be replaced regularly, which in turn limits the system efficiency. Due to the non-positive transmission of the operating forces, the hydroforming technology can only be a reliable, non-positive shaft-hub connection for commercial vehicle camshafts to a limited extent.
  • a method for producing a built-up camshaft and a built-up camshaft from a shaft tube and pushed-on elements using the internal high pressure forming are known from EP 0 265 663 B2.
  • the shaft is expanded hydraulically, which means that the shaft-hub connection is created by frictional connection.
  • EP 0 328 009 Bl or EP 0 328 010 Bl a tube is expanded by means of internal high-pressure forming, the cam disks being fastened on two tubes which are placed one above the other in order to increase the rigidity. Torques are transmitted non-positively. Due to the large number of components required, this is a relatively expensive solution.
  • EP 0 374 389 B1 describes a method for pretreating components of a built-up camshaft. There, heat treatment measures for a tube are described, which should make it possible that the tube can either be expanded better by internal high-pressure forming, or that the bearing points become more hard.
  • the cam disk support tube is preformed with different cross sections so that only the tube sections which receive the cam disks are plastically deformed during subsequent expansion by means of internal high pressure forming.
  • the pipe sections between the individual cam disks are only expanded elastically.
  • tubes are used as supports for the cam disks.
  • the cam disks are converted together with the carrier tube on the basis' of the circular cross-section in a die, so that a built-up camshaft results.
  • no hardened cam disks can be formed at room temperature, otherwise they break apart or at least form cracks. Therefore, a separate heat treatment process is required in the method described there.
  • a method for producing a built-up camshaft using internal high pressure forming and a built-up camshaft made of a shaft tube and pushed-on elements are described in EP 0 265 663 AI.
  • the cam disks can have inner profiles in their openings so that, in addition to the frictional connection, there is also a positive connection, the tube forming the shaft being plastically deformed while the cam disks are being elastically expanded.
  • a composite camshaft is known from EP 0 516 946 B1, in which a hollow shaft is machined by means of internal high pressure forming.
  • the cam disks attached to the shaft have a circular cross-section and a groove running in the axial direction, which is at least partially filled with the material of the shaft by plastic deformation during hydroforming, so that a positive rotary connection is established.
  • EP 0 730 705 B1 describes a method for producing a one-piece hollow camshaft, in which a tube is expanded in the die by internal high-pressure forming in such a way that a hollow camshaft results. It is advantageous that no separate cam disks have to be produced. On the other hand, it is disadvantageous that heat treatment of the camshaft is required. In addition, the wall thickness of the camshaft is particularly strongly reduced in the areas of the cam tip, which means that the strength requirements for a commercial vehicle camshaft can hardly be met with this technology.
  • a camshaft and a method for producing the same are described in EP 0 970 293 B1.
  • Thin cam disks are punched out of a metal sheet or sheet metal strip. A majority of these flat materials are assembled into sheet metal stacks above or next to one another.
  • a cam disc consists of several parts that are ultimately joined to a tube by internal high-pressure forming.
  • the cam discs can have a toothing or a notch-like profile on the circumference, which serves for orientation in the rotational position.
  • the built-up camshaft known from EP 0 856 642 AI is based on a longitudinal press dressing, the joining partners being coated at the joining points.
  • the coating can be a Phosphate layer, but also be adhesive.
  • a profiling option that is not specified in more detail is also addressed.
  • EP 0 839 990 B1 is based on a cam disk carrier shaft produced by casting.
  • This shaft can be profiled at the points where the cam discs are attached.
  • the non-rotationally symmetrical profile is cast on 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 because of the brittleness of the material.
  • the profiling is carried out using rolling rods which have longitudinal grooves.
  • the course of a groove in the rolling tool essentially follows the direction of movement of the rolling rod, which has the same profile in every cross section transverse to the direction of movement.
  • the recess does not extend exactly in the direction of movement of the roller bar, • but is inclined to the thread pitch angle.
  • the cross sections of a rolling rod are then not completely the same over the length.
  • each roll bar 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 mentioned here as an example for the profile of the carrier wave deviating from the circular shape has only the aim of approximating a circular shape.
  • the composite camshaft described in DE 195 20 306 CI is an indirect positive connection.
  • a corrugated adapter sleeve is used, which engages in a rotationally symmetrical shaft toothing and in a likewise rotationally symmetrical inner toothing on the cam disk opening.
  • the disadvantage here is however, the handling of the adapter sleeve as a separate component.
  • EP 0 580 200 B1 relates to the configuration of the cam disk for the purpose of lightweight construction, for which purpose it is made from a thin sheet. However, this construction is unlikely to meet the strength requirements for a camshaft.
  • a cam disk support tube is mechanically widened by a punch that is pierced or drawn through. This requires that the cam disk support tube has different wall thicknesses before joining.
  • the joining surface can have recesses, pockets or a toothing. If a toothing is provided for the profile of the joining surface, this is on both joining partners, that is. to be attached to the camshaft and the cam discs.
  • crankshaft Another built crankshaft and a method for producing the same are described in DE 100 61 042 C2.
  • a conical bogie wedge is used here.
  • a maximum of two crank webs can be attached to a crank pin by rotating them against each other.
  • the joining surfaces have to be machined due to the high tolerance requirements.
  • the shaft is essentially elastically deformed, the connection being releasable. All of the methods described are therefore not able to meet the requirements placed on a highly stressed camshaft in the sense of a simple and inexpensive solution.
  • a single wedge-shaped arch profile formed from alternating elevations and depressions is provided on the circumference of those sections of the cam disk carrier shaft in which the cam disks are attached.
  • the cam disks are connected to the cam disk carrier shaft by means of a cross-compression bandage, in which no special coating of the contact surfaces is required, by continuously increasing the radius of the cam disk carrier shaft.
  • the mounting of the cam disks and the at least one drive wheel to the cam disk support shaft in a particularly simple manner can be effected in that the drive wheel is rotated while the cam discs are held in a rigid position.
  • the device required for this can be constructed in a particularly simple manner and the described method is very easy to master.
  • camshaft carrier shaft is designed as a solid shaft.
  • cam disk carrier shaft it is also possible for the cam disk carrier shaft to be designed 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 reshaping of the cam disk carrier shaft is possible if the depth of the depressions increases continuously with the increase in the elevations.
  • the method according to the invention allows such large manufacturing tolerances that the . There is no need for soft machining of the bore of the cam disks, and cost savings can thus be achieved.
  • the cam disks are pushed onto the cam disk support shaft with play and fixed by a rotary movement.
  • the question of centering advantageously plays the joining partner hardly plays a role, as a result of which the outlay for the method according to the invention is relatively low.
  • the cam disk support shaft is plastically deformed, the cam disks and the at least one drive wheel being elastically expanded.
  • the profile of the cam disk support shaft can be partially smoothed out again during the joining by this plastic deformation.
  • the connection between the cam disk carrier shaft and the cam disks is essentially maintained in this way by the plastic deformation of the shaft during joining and by the elastic expansion of the hub. This is also advantageous if the individual cam disks have certain dimensional deviations, since these are compensated for by the plastic deformation.
  • the elevations and depressions are introduced into the cam disk carrier shaft by means of two rod-shaped rolling tools that move relative to one another.
  • considerable cost savings are possible compared to • conventional processes such as hobbing or gear shaping.
  • gearing formed at room temperature has a higher strength.
  • the profile of the cam disk bore can be produced by forging in the required final quality, which leads to a further simplification of the production of the camshaft according to the invention.
  • Figure 1 is a side view of the camshaft according to the invention.
  • FIG. 3 shows the method from FIG. 2 in a second state
  • FIG. 4 shows the method from FIG. 2 in a third state
  • FIG. 5 shows the method from FIG. 2 in a fourth state
  • FIG. 6 shows a modification of the method from FIG. 2
  • FIG. 7 shows a second embodiment of the introduction of elevations and depressions into the cam disk carrier shaft according to the method according to the invention in a first state; 8 shows the method from FIG. 7 in a second state;
  • FIG. 9 shows the method from FIG. 7 in a third state
  • FIG. 11 shows the attachment of a cam disk to the cam disk support shaft according to the method according to the invention in a first state
  • FIG. 12 shows the method from FIG. 10 in a second state
  • FIG. 13 shows the method from FIG. 11 in a second state
  • FIG. 14 shows the method from FIG. 10 in a third state
  • FIG. 17 shows the method from FIG. 11 in a fourth state.
  • camshaft 1 shows a built-up camshaft 1, which has a camshaft carrier shaft 2, on which, in the assembled state, a plurality of camshafts 3 and a camshaft drive wheel or drive wheel 4 are attached in a rotationally fixed manner to respective sections 2a thereof.
  • the camshaft 1 is used in a known manner to control the valve opening times in an internal combustion engine, not shown.
  • the cam disks 3, the number of which depends on the internal combustion engine, each have a bore 5 for mounting the same on the sections 2a of the cam disk support shaft 2 and are generally offset from each other by a certain angle.
  • the camshaft 1 also has a plurality of bearing points 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, the cam disks 3 and the drive wheel 4 each having play sl, s2 and s3 with respect to the cam disk support shaft 2. It can be seen that the axial distance a between two adjacent cam discs 3 is greater than the width b of a cam disc 3.
  • a round material made of steel, which can be hot-rolled, for example, is preferably used as the starting material for the cam disk carrier shaft 2.
  • the requirements for the material of the cam disk support shaft 2 are a certain cold formability and toughness.
  • a special heat treatment by tempering or a particularly high wear resistance is not necessary.
  • drawn round materials with a circular starting cross section can also be used as semi-finished products for the cam disk support shaft 2.
  • Hollow bodies such as pipes can also be used, as a result of which the entire camshaft 1 'would have a lower mass and a deep hole for supplying lubrication points could be dispensed with. In this case, however, a mandrel should be inserted into the hollow shaft for machining the cam disk carrier shaft 2 described later.
  • a tooth-like profile with several local elevations 7 and a corresponding number of local depressions 8, which are arranged alternately to one another, is introduced into the cam disk support shaft 2.
  • a wedge-shaped arc profile 9 is generated by material displacement as an envelope of all ridges 7, the outer contour of the sections 2a is similar to a toothing with interrupted wings.
  • the depressions 8 made in the shaft do not represent micro-toothing to increase the frictional engagement. At best, they can be understood as macro-toothing.
  • two rod-shaped rolling tools are provided, which are referred to below for the sake of simplicity as rolling rods 10 and 11 and are provided on their respective mutually facing sides with profiles which are provided with alternating gaps and projections and with a relative movement the two rolling racks l 'O and the elevations 7 and depressions 8 contribute 11 by cold forming in the cam disk support shaft.
  • the cam disk carrier shaft 2 is preferably clamped between tips, not shown, whereupon the rolling rods 10 and 11 move in the direction of V 10 and Vo. set the arrows in motion synchronously and at the same speed. As a result, the cam disk carrier shaft 2 is rotated according to the arrow V 2 and moves several times around its own axis during processing.
  • the length of the two roller bars 10 and 11 therefore corresponds to a multiple of the diameter or the circumference of the cam disk carrier shaft 2.
  • these exert a radial pressure on the cam disk carrier shaft 2 and shape it. It can be seen from FIGS. 2 to 5 that the profile depth of the rolling rods 10 and 11 increases over the length thereof, as a result of which the required forming forces change.
  • the entire rolling process shown in FIGS. 2 to 5 can be completed after a few seconds, after which move the rolling rods 10 and 11 back to their starting position.
  • the cam disk carrier shaft 2 can then be displaced along its longitudinal axis to the next section 2a to be shaped, whereupon the introduction of the elevations 7 and the depressions 8 to form the wedge-shaped curved profile 9 is repeated.
  • each gap of the profile of the rolling rods 10 and 11 which runs transversely to the direction of movement of the rolling rods 10 and 11 forms an elevation 7 and each projection which also extends transversely to the direction of movement of the rolling rods 10 and 11 forms a recess 8 on the cam disk carrier shaft 2.
  • the profile of the roll bars 10 and 11 it is clear that the elevations 7 • continuously increase the radius of the cam disk support shaft 2, since each subsequent gap of the profile is lower than the respective preceding. In the present case, this also means that the higher the protrusions of the profile of the rolling rods 10 and 11, the deeper the gap behind it, which facilitates material penetration during the forming process.
  • the wedge-shaped arch profile 9 resulting from the reshaping is designed as an Archimedean or logarithmic spiral.
  • higher-order mathematical functions such as the Fermat, Galilean or hyperbolic spiral " , sinus spiral, lemniscate, quadratrix or others would also be considered for the wedge-shaped arch profile 9, the function itself being of subordinate importance
  • the wedge-shaped arc profile 9 is an opening function which expands in polar coordinates with the angle of rotation, .sich. And deviates from the circular shape. The center of this function does not necessarily have to be with the axis of rotation of the Cam disk carrier shaft 2 collapse, so that eccentric spirals are also possible.
  • two rolling rods 10 and 11 are provided in order to support the cam disk support shaft 2 during the rolling process and to derive the rolling forces.
  • the rolling rods 10 and 11 are preferably geometrically identical and are arranged with an offset to one another which corresponds to half the central circumference of the cam disk carrier shaft 2.
  • the rolling rods 10 and 11 can be optimized in such a way that the forming work required for introducing the wedge-shaped curved profile 9 into the cam disk carrier shaft 2 is distributed uniformly over both rolling rods 10 and 11.
  • the cam disk support shaft 2 can be driven indirectly by the rolling rods 10 and 11 by the same.
  • the rolling rods 10 and 11 are preferably made of hardened steel and have the width b of the cam disks 3.
  • the depressions can be introduced into the rolling rods 10 and 11 by known machining techniques, which include, for example, surface grinding and deep grinding with a correspondingly profiled grinding wheel.
  • the grinding wheel profile in turn, can be worked into the grinding wheel, for example, using CNC-controlled dressing using a diamond tile.
  • cam disk support shaft 2 For each section 2a to which ⁇ a cam disk 3 is attached to the cam disk support shaft 2, as indicated above, a separate, successive shaping process is provided, for which purpose the cam disk support shaft 2 remains tensioned. Between the forming processes, however, the cam disk carrier shaft 2 must be repositioned in its rotational position in accordance with the required angular displacement of the cam disks 3 and, if necessary, including the rotary drive, axially shifted accordingly, the distance a + b of the adjacent cam disks 3.
  • FIGS. 7, 8 and 9 show an 'alternative forming method for forming the wedge-shaped arch profile 9 in the sections 2a of the cam disk support shaft 2.
  • a die 13 is provided which, in the present case, has three die parts 13a, 13b and 13c which can be moved relative to one another, each with a profile which forms the elevations 7 and the depressions 8.
  • the illustrated closing and opening movement of the die parts 13a, 13b and 13c reshapes the cam disk support shaft 2 with swelling or pulsating pressurization, for example by hammering.
  • the die parts 13a, 13b and 13c each have the width b of the cam disks 3.
  • the die parts 13a, 13b and 13c execute a radial movement relative to the cam disk carrier shaft 2, the force being introduced for the shaping of the material with the aid of a known, linearly guided actuator hydraulically, pneumatically, or electromechanically.
  • the individual profile cross sections of the cam disk support shaft 2, that is to say the sections 2a to be formed, are formed one after the other, for which purpose the cam disk support shaft 2 is brought into a new angle of rotation before the forming.
  • cam disks. 3 are not shown in the figures shown. These can be forged, for example, the forged contour advantageously being close to the end contour of the cam disks 3. It is then only necessary to machine the outer functional surface of the cam disks 3 for valve control. This is also true for the Lagerstel ⁇ 'en 6- .the cam disk support shaft 2 by the process described in the following the assembly of the cam shaft 1. Also, a production of the cams 3 by casting or sintering is 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 increase in the outer radius of the cam disk support shaft 2 and thus to the wedge-shaped curved profile 9.
  • the bore 14 of the drive wheel 4 also essentially corresponds to the bore 5 of the cam disks 3. However, the inner profile of the bore 5 of the cam disks 3 is mirror-inverted to the inner profile of the bore 14 of the drive wheel 4.
  • Figures 10 and 11, 12 and 13, 14 each show in pairs and 15, as well as 16 and 17, the 7 ⁇ blauf in a possible embodiment of the attachment of the cam disks 3 and the drive wheel 4 on the cam disk support shaft 2.
  • the clamping elements 15 are part of a rotating device, not shown in its entirety, which has a rotary drive, which is preferably regulated and has monitoring of the angular position of the clamping elements 15 and thus of the drive wheel 4.
  • the cam disks 3, as can be seen in FIG. 11 are clamped in a rotationally fixed manner by means of two clamping elements 16 and fixed in their position. If, as shown in FIGS.
  • the cam disk support shaft 2 is also set in rotation by the angle ⁇ 2 by positive entrainment.
  • the initial joint play s2 also decreases to 0, which can be seen in FIG. 15. Due to the dimensional tolerances, the reduction of the initial joint play s2 on each cam disk 3 is achieved at a different point in time or at a different angle of rotation of the drive wheel 4.
  • the torque introduced into the cam disk carrier shaft 2 during the joining by the drive wheel 4 causes a plastic deformation of that wave profile which is wrapped around by the drive wheel 4.
  • the initial width of the elevations dl according to FIG. 14, like for the cam disks 3 also increases to the width d2 according to FIG. 16.
  • the bore 14 of the drive wheel 4 is also enlarged by the assembly torque elastically expanded.
  • the bore 14 of the drive wheel 4 generally has a greater radial expansion than the bores 5 of the cam disks 3.
  • the rotary control of the rotary device switches off the rotary movement of the drive wheel 4, as a result of which the assembly torque drops to zero.
  • the cam disks 3 and the drive wheel 4 spring back in the radial direction and partially reduce their elastic expansion. They exert a permanent radial pressure on the plastically deformed camshaft carrier shaft 2, which releases 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 prevented.
  • the non-positive axial displacement locks are set for the cam disks 3 and the drive wheel 4.
  • the finished camshaft 1 is produced by the above-described joining machining, the bearing points 6 and the outer functional surfaces being able to be machined by known fine machining methods, for example by centerless cylindrical grinding for the bearing points 6 and by cam shape grinding for the outer contour of the joined cam disks 3.
  • the camshaft 1 In the state installed in the internal combustion engine, the camshaft 1 preferably has the same direction of rotation as the drive wheel 4 when it is mounted on the camshaft carrier shaft 2 under operating conditions. Accordingly, the transmission of the camshaft drive torque from the drive wheel 4 via the cam disk support shaft 2 to the cam disks 3 takes place in a form-fitting manner.
  • any 'cam to rotate.
  • the drive wheel could 4 and the cam disks 3 are connected individually to the cam disk support shaft 2, with monitoring of the applied torque being sensible in this context.
  • the parameters in the figures in particular the slope of the wedge-shaped arch profile 9, the division of the elevations 7 and the depressions 8, and the design of the tooth shapes have been chosen extremely.
  • the deviation of the wedge-shaped arch 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, that is to say a smaller slope of the wedge-shaped arch profile 9, leading to better self-locking.
  • the angle of rotation 03 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)

Abstract

L'invention concerne un arbre à cames (1) destiné à un moteur à combustion interne et comprenant un arbre support de disques à cames (2) sur lequel sont montés plusieurs disques à cames (3) ainsi qu'une roue d'entraînement (4), le rayon extérieur de l'arbre support de disques à cames (2) variant de manière continue dans les segments dans lesquels les disques à cames (3) sont montés. Les disques à cames (3) présentent un alésage (5) dont le diamètre intérieur varie de manière continue. Dans les segments (2a) dans lesquels sont montés les disques à cames (3), l'arbre support de disques à cames (2) présente en alternance des bosses (7) et des creux (8) qui forment un profil d'arc cunéiforme (9) sur la périphérie du segment (2a) de l'arbre support de disques à cames (2). Les bosses (7) augmentent de manière continue le rayon extérieur de l'arbre support de disques à cames (2). L'alésage (5) des disques à cames (3) est adapté à l'accroissement du rayon extérieur de l'arbre support de disques à cames (2) et un profil d'arc cunéiforme (9) unique est réalisé autour de la périphérie de l'arbre support de disques à cames (2) et de l'alésage (5) des disques à cames (3).
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 true EP1723316A1 (fr) 2006-11-22
EP1723316B1 EP1723316B1 (fr) 2007-07-18

Family

ID=34895186

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05715761A Expired - Fee Related EP1723316B1 (fr) 2004-03-11 2005-03-05 Arbre a cames et procede pour produire un arbre a cames

Country Status (4)

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

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DE102006035082A1 (de) * 2006-07-28 2008-01-31 Daimler Ag Verfahren und Vorrichtung zur Herstellung einer Welle-Nabe-Verbindung
JP4812570B2 (ja) * 2006-09-13 2011-11-09 株式会社久保田鉄工所 中空異形段付軸の成形方法及びその成形装置
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
DE102011079584A1 (de) 2011-07-21 2013-01-24 Mahle International Gmbh Nockenwelle und zugehöriger Nocken
DE102011087049A1 (de) * 2011-11-24 2013-05-29 Mahle International Gmbh Verfahren zum Fügen von Bauelementen auf einer Welle
DE102011117849A1 (de) * 2011-11-08 2013-05-08 Neumayer Tekfor Holding Gmbh Verfahren zur Fertigung einer Nockenwelle und entsprechende Nockenwelle
US10654111B2 (en) 2017-03-27 2020-05-19 Walter Forrest Frantz Curvature for pathway of a locating device or chuck
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
EP1723316B1 (fr) 2007-07-18
US7290515B2 (en) 2007-11-06
US20070006834A1 (en) 2007-01-11
DE502005001066D1 (de) 2007-08-30
DE102004011815A1 (de) 2005-09-29
WO2005088082A1 (fr) 2005-09-22

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