[go: up one dir, main page]

WO2018228792A1 - Procédé et dispositif pour la consolidation par percussion de rayons de transition d'un vilebrequin - Google Patents

Procédé et dispositif pour la consolidation par percussion de rayons de transition d'un vilebrequin Download PDF

Info

Publication number
WO2018228792A1
WO2018228792A1 PCT/EP2018/063691 EP2018063691W WO2018228792A1 WO 2018228792 A1 WO2018228792 A1 WO 2018228792A1 EP 2018063691 W EP2018063691 W EP 2018063691W WO 2018228792 A1 WO2018228792 A1 WO 2018228792A1
Authority
WO
WIPO (PCT)
Prior art keywords
crankshaft
impact
transition radii
transition
impact force
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.)
Ceased
Application number
PCT/EP2018/063691
Other languages
German (de)
English (en)
Inventor
Alfons Reeb
Jochen Schmidt
Konrad Grimm
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.)
Maschinenfabrik Alfing Kessler GmbH
Alfing Kessler Sondermaschinen GmbH
Original Assignee
Maschinenfabrik Alfing Kessler GmbH
Alfing Kessler Sondermaschinen GmbH
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 Maschinenfabrik Alfing Kessler GmbH, Alfing Kessler Sondermaschinen GmbH filed Critical Maschinenfabrik Alfing Kessler GmbH
Publication of WO2018228792A1 publication Critical patent/WO2018228792A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B24—GRINDING; POLISHING
    • B24B—MACHINES, DEVICES, OR PROCESSES FOR GRINDING OR POLISHING; DRESSING OR CONDITIONING OF ABRADING SURFACES; FEEDING OF GRINDING, POLISHING, OR LAPPING AGENTS
    • B24B39/00—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor
    • B24B39/04—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor designed for working external surfaces of revolution
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P9/00—Treating or finishing surfaces mechanically, with or without calibrating, primarily to resist wear or impact, e.g. smoothing or roughening turbine blades or bearings; Features of such surfaces not otherwise provided for, their treatment being unspecified
    • B23P9/04—Treating or finishing by hammering or applying repeated pressure
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D7/00—Modifying the physical properties of iron or steel by deformation
    • C21D7/02—Modifying the physical properties of iron or steel by deformation by cold working
    • C21D7/04—Modifying the physical properties of iron or steel by deformation by cold working of the surface
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D7/00—Modifying the physical properties of iron or steel by deformation
    • C21D7/02—Modifying the physical properties of iron or steel by deformation by cold working
    • C21D7/04—Modifying the physical properties of iron or steel by deformation by cold working of the surface
    • C21D7/06—Modifying the physical properties of iron or steel by deformation by cold working of the surface by shot-peening or the like
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D9/00—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor
    • C21D9/30—Heat treatment, e.g. annealing, hardening, quenching or tempering, adapted for particular articles; Furnaces therefor for crankshafts; for camshafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B23—MACHINE TOOLS; METAL-WORKING NOT OTHERWISE PROVIDED FOR
    • B23P—METAL-WORKING NOT OTHERWISE PROVIDED FOR; COMBINED OPERATIONS; UNIVERSAL MACHINE TOOLS
    • B23P2700/00—Indexing scheme relating to the articles being treated, e.g. manufactured, repaired, assembled, connected or other operations covered in the subgroups
    • B23P2700/07—Crankshafts
    • C—CHEMISTRY; METALLURGY
    • C21—METALLURGY OF IRON
    • C21D—MODIFYING THE PHYSICAL STRUCTURE OF FERROUS METALS; GENERAL DEVICES FOR HEAT TREATMENT OF FERROUS OR NON-FERROUS METALS OR ALLOYS; MAKING METAL MALLEABLE, e.g. BY DECARBURISATION OR TEMPERING
    • C21D2221/00—Treating localised areas of an article

Definitions

  • the invention relates to a method for impact hardening of transition radii of a crankshaft, in particular of transition radii between connecting rod journal and crank webs and / or transitional radii between the main journal and the crank webs of the crankshaft according to the preamble of claim 1.
  • the invention also relates to an apparatus for carrying out the method for impact hardening of transition radii of a crankshaft.
  • the invention also relates to a crankshaft.
  • crankshafts are manufactured using a variety of machining and heat treatment processes, so that the crankshafts can be exposed to increasingly higher engine power.
  • thermal treatments such as induction hardening and case hardening, laser hardening or nitriding, as well as strain hardening processes such as deep rolling, shot peening or impact hardening.
  • strain hardening processes such as deep rolling, shot peening or impact hardening.
  • the impact hardening is an advantageous method for increasing the fatigue strength, in particular the bending fatigue strength and torsional fatigue, of crankshafts.
  • the increase in fatigue strength is achieved in that impact forces are introduced into the claimed areas in cross-sectional transitions and changes in cross section by cold forming, preferably hammering by means of special impact tools in the crankshaft.
  • strict control procedures and highly qualified personnel are required to carry out the process.
  • a follow-up with corrective measures may be required to slightly correct the concentricity of the crankshaft after impact hardening if necessary.
  • the object of the present invention is therefore to further develop the methods and devices for impact hardening in order to further improve the fatigue strength of crankshafts, in particular while avoiding concentricity errors.
  • the invention is also based on the object of providing an improved crankshaft, in particular with respect to its fatigue strength and concentricity. With respect to the crankshaft, the object is achieved by the features listed in claim 14.
  • transition radii of a crankshaft in particular transition radii between connecting rod journal and crank webs and / or transition radii, are impact-bonded between main bearing journal and the crank webs of the crankshaft.
  • the connecting rod journal and the main journals are hereinafter referred to in part as "pin" for simplicity.
  • journal may mean both the connecting rod journal and the main bearing journals, as well as only the connecting rod journal or only the main journals. Insofar as this is not explicitly stated otherwise, here all three variants are encompassed by the term pin.
  • the invention is particularly preferably suitable for increasing the fatigue strength of, for example, crankshafts having a length of 0.2 to 8 m or more and / or main and connecting rod journal diameters of 30 to 500 mm or more.
  • the invention is particularly suitable for increasing the fatigue strength of large crankshafts of 1, 5 to 8 m in length or more and / or main and connecting rod journal diameter of 100 to 500 mm or more.
  • the crankshaft may have various types of transition radii, for example, fillets, for example, in a basket arch shape, or also undercut radii or radii with transitions.
  • the transition radii can, for example, pass tangentially into the journal positions or running surfaces of the main and connecting rod journal.
  • the crankshaft usually has transition radii at all transitions or cross-sectional changes. This is especially true for cross-sectional changes between journals and crank webs.
  • the invention is particularly suitable. But transition radii can also for any other cross-sectional changes, in particular for changes in cross section at the end portions of the crankshaft, z. B. at a transition to a flange, a disc or a shaft, etc., may be provided.
  • a transition radius the fatigue strength of which is to be improved by the method according to the invention or the device according to the invention, does not necessarily have to be present between a connecting rod journal and a crank web or a main journal and a crank web, but can be arranged at any point of the crankshaft.
  • the terms "connecting rod journal”, “main journal”, “flange”, “pin” and / or “crank arm” can accordingly be reinterpreted by a person skilled in the art.
  • transition radii between connecting rod journal and crank web and / or main journal and crank web.
  • this is not restrictive and should only serve the better understanding or better readability.
  • a transition radius in the context of the invention, this can basically be an arbitrary transition radius at any point of the crankshaft.
  • differently sized impact forces are introduced into at least two transition radii.
  • the difference between the impact forces is at least greater than a tolerance range which is typically present in the introduction of the impact forces in the prior art.
  • the differently introduced impact forces preferably differ significantly. It can be provided, for example, that the impact forces which are introduced into the at least two transition radii differ by at least 2%, preferably by at least 5%, more preferably by at least 10% and most preferably by at least 30%.
  • the introduction of a striking force can be understood to mean that a striking head of a striking tool or a so-called "striker" of a striking device strikes against the region of the crankshaft to be consolidated, in the present case a transition radius. The impact takes place purposefully to the desired impact position along the annular radius around the pin circumferential transition radius.
  • the methods and devices according to the prior art provide that in the Schlagverfest only the transition radii of the crankshaft in all transition radii, in particular in the transition radii between connecting rod journal and crank webs and the transition radii between main journals and crank webs, the same impact force is introduced.
  • the impact force is chosen such that it is sufficient to bring sufficient compressive residual stresses in all to be solidified transition radii of the crankshaft.
  • the inventors have recognized on the basis of simulations and test series that the robustness or fatigue strength of the crankshaft can be achieved in a consistent - and sometimes even better - quality advantageous even when the impact forces are varied individually for different transition radii. As a result, critical concentricity errors can be completely excluded in the optimum case and thus the effort for a later concentricity correction can be minimized.
  • the invention also makes possible a more cost-effective machining process by reducing the machining steps. In particular, a less machining for a compensation of the concentricity errors in the subsequent processing can be realized.
  • crankshafts can be made with at least the same quality or robustness, as with the known methods of the prior art.
  • crankshafts which have been previously processed to increase their fatigue properties by other methods.
  • a crankshaft which has been hardened by induction hardening can be subsequently improved with respect to its bending and torsional fatigue strength by introducing compressive residual stresses according to the method according to the invention or with the device according to the invention.
  • the same impact force is introduced in two transition radii adjoining the same main journal.
  • transition radii can be defined, in which the same impact force is introduced.
  • two transition radii adjoining the same pin can each form a group.
  • transition radii of at least two connecting rod journal pins preferably into the transition radii of all connecting rod journal pins.
  • This also applies to transitions to flanges, cones and other geometric cross-sectional changes - both tangent and deposited radii.
  • One possibility for forming groups of transition radii, in which the same impact force is introduced, can thus also result from the fact that the transition radii of all main journals form a group.
  • the transition radii of all connecting rod trunnions may optionally form a group.
  • the inventors have recognized that in order to avoid concentricity errors it may already be sufficient to introduce the same impact force in all transition radii of the main journal and in all transition radii of the conrod journal, the impact force being introduced into the transition radii of the main journal in this case the impact force that is introduced into the transition radii of the connecting rod journal, differs.
  • a first impact force to be introduced into the transition radii of a first conrod journal
  • a second impact force (deviating from the first impact force) to be introduced into the transition radii of a second conrod journal.
  • an individual impact force can be introduced into the transition radii of each connecting-rod journal.
  • a second impact force (deviating from the first impact force) is introduced into the transition radii of a first main journal, and a second impact force (deviating from the first impact force) is introduced into the transition radii of a second main journal.
  • an individual impact force can be introduced into the transition radii of each main journal.
  • the impact forces can thus be determined individually for each transition radius.
  • optimally suitable impact forces and impact patterns can result for each transition radius or at least for different groups of transition radii.
  • run-out errors occur as a result of impact hardening in the first place.
  • the fatigue strength of the crankshaft by this measure even exceed the requirements.
  • a base value for the impact forces to be introduced into the transition radii to be determined on the basis of the desired fatigue strength of the treatment device. at shaft and / or determined by the desired fatigue strength of sections of the crankshaft.
  • a base value for the entire crankshaft can be determined, which may be a minimum impact force, the introduction of which ensures the desired fatigue strength in all sections of the crankshaft, or preferably with the addition of a safety margin.
  • the basic value is determined individually for different sections of the crankshaft, such that the desired fatigue strength of the crankshaft is ensured in the respective sections, preferably with the addition of a safety margin.
  • a base value for end portions or end portions of the crankshaft, a base value for a central portion of the crankshaft, a base value for all main journals, a base value for all connecting rod journals and / or a base value for other portions of the crankshaft can be determined.
  • a plurality of base values may also be provided.
  • the base value can also be chosen such that it is a defined percentage, for example 10% to 50%, preferably 20% to 40%, greater than the minimum impact force necessary for the crankshaft or the crankshaft range, so that the base value decreases can be adjusted up and down to impact hardening the transition radii.
  • the base value is varied by a compensation value in order to compensate for, avoid and / or minimize concentricity errors of the crankshaft. If a baseline value higher than a minimum value is determined for the impact forces to be introduced into the transition radii (for example by adding at least one margin of safety), the base value can be individually varied by particular compensation values for individual transition radii, in particular increased the minimum value of the impact force to reach the desired fatigue strength at a transition radius is not exceeded. The compensation value can therefore be used specifically to avoid or compensate for concentricity errors.
  • the fatigue strength of the crankshaft and the concentricity of the crankshaft can be adjusted almost independently. It can be provided, for example, that all transition radii of the connecting rod journals are impact-bonded to the base value, and all transition radii of the main journals are impact-hardened with the base value varied by the compensation value, for example a 1 10% value or 90% value based on the base value , Alternatively, it can also be provided that all main bearing journals are impact-hardened with the base value and all connecting rod journals are impact-hardened with the base value varied by the compensation value. In a further development of the invention, it can further be provided that the compensation value for a plurality, preferably for each transition radius, is determined individually in order to compensate, avoid and / or minimize concentricity errors of the crankshaft.
  • the compensation value is at most 30%, preferably at most 15%, particularly preferably at most 5%, of the base value. It may also be provided that the equalization value is a maximum of 30%, but not less than 20%, not more than 20%, but not less than 15%, not more than 15%, but not less than 10%, or not more than 10%, but not less than 5% of the underlying.
  • a highly stressed area for introducing a percussion force in at least one of the transition radii along the ring around the crankshaft (in particular about the connecting rod journal and / or main journal) circumferential respective transition radius a highly stressed area, a little stressed area and intervening intermediate regions are defined, after which such impact-hardening is achieved that the impact force introduced into the intermediate regions is increased in the direction of the highly stressed region.
  • a region of the respective transition radius of the crankshaft, which is subjected to particularly high loads, in particular in engine operation, for example tensile forces, etc., is meant by a region which is subject to high loads.
  • the attention of the highly stressed areas of the transition radii is of central importance. The highest residual compressive stresses should preferably be introduced into these areas.
  • a region subject to high stress may mean an area along the circumference of the transition radius and / or a region along the respective transition radius which revolves annularly around the crankshaft or around the connecting rod journal and / or the main bearing journal.
  • an area around the so-called bottom dead center of a connecting rod journal can be a highly stressed area in the sense of the invention.
  • the bottom dead center is the area that can be referred to as opposite in engine operation as a tension side of the connecting rod journal or as the pressure side.
  • the methods and devices according to the prior art provide that during impact hardening of a transition radius a constant impact force along the annular transition around the connecting rod journal and / or the main bearing journal respective transition radius is introduced.
  • the impact force is chosen such that it is sufficient to bring sufficient compressive residual stresses in the highly stressed areas of the crankshaft.
  • the complete circumferential impact strengthening of a transition radius along the circumference of the crankshaft causes a lot of effort.
  • the inventors have meanwhile found that the robustness or fatigue strength of the crankshaft in a constant or better quality can be advantageously achieved even if the maximum impact force introduced into a certain transition radius is only in the high-stress area is introduced, and when the impact force is increased from the intermediate areas towards the high-stress area. As a result, an abrupt or sudden change in the impact force from one beat to the next blow can be avoided.
  • transition radii are no longer completely solidified (with the same impact force).
  • the impact force introduced into the intermediate regions is steadily increased in the direction of the highly stressed region.
  • a highly stressed area may be provided, which is surrounded on both sides by intermediate areas, whereby the highly stressed area is separated from the area with little stress.
  • the impact force within the intermediate areas and / or the less stressed area follows any course, but preferably sudden changes in the impact force are avoided and the impact force in the highly stressed region of the transition radius preferably on highest is (in particular maximum, average and / or sum of all individual percussion forces of the transition radius considered).
  • the impact force introduced into the intermediate regions is increased monotonously, very preferably in a strictly monotonic manner, in the direction of the highly stressed region.
  • the impact force introduced into the intermediate regions is increased uniformly or linearly in the direction of the highly stressed region. It is also possible to increase the impact force introduced into the intermediate regions according to any mathematical function in the direction of the highly stressed region.
  • the impact force in the direction of areas for which a different impact force is advantageous preferably uniformly increased or reduced.
  • the impact force which is introduced in the impact-hardening in the highly stressed area based on the desired endurance of the crankshaft crankshaft and / or the desired fatigue strength of sections of the crankshaft is determined.
  • crankshaft It may therefore be sufficient to take into account only the necessary impact force in the highly stressed areas to achieve the desired fatigue strength of the crankshaft and / or the desired fatigue strength of portions of the crankshaft.
  • the impact force which is introduced in the impact-hardening in the highly stressed area is constant or is kept constant over the highly stressed area.
  • a high fatigue strength or robustness of the crankshaft can be achieved, in particular, by introducing a (high) impact force with a constant thickness into the highly stressed area. This applies in particular (but not exclusively) if, in the intermediate regions, impact forces which drop off with respect to their strength, in particular impact forces that drop linearly from one impact to the next impact, are introduced in the low-stressed region except for zero can be reduced.
  • the highly stressed area along the annular about the connecting rod journal peripheral transition radius starting from a highly loaded point of the connecting rod journal, at least ⁇ 20 °, preferably at least ⁇ 30 °, more preferably at least ⁇ 40 °, especially preferably at least ⁇ 50 °, very particularly preferably at least ⁇ 60 °, for example at least ⁇ 70 °, at least ⁇ 80 ° or at least ⁇ 90 °.
  • the highly loaded point of the connecting rod journal is, in particular, the bottom dead center of the connecting rod journal. It can therefore be provided in particular that, starting from a highly loaded point of a pin, the highly stressed area along the circumference of the pin is defined.
  • the highly stressed area along the annular around the main journal pivoting transition radius starting from a highly loaded point of the main journal, at least ⁇ 20 °, preferably at least ⁇ 30 °, more preferably at least ⁇ 40 °, more preferably at least ⁇ 50 °, most preferably at least ⁇ 60 °, for example at least ⁇ 70 °, at least ⁇ 80 ° or at least ⁇ 90 °.
  • an upper limit for the extension of the highly stressed region along the transition radius which surrounds the ring journal around the main journal, after which the highly stressed region, starting from a highest loaded point of the main journal, is at most ⁇ 90 °, preferably at most ⁇ 80 °, more preferably at most ⁇ 70 °, very particularly preferably at most ⁇ 60 °, for example at most ⁇ 50 °, for example at most ⁇ 40 °, at most ⁇ 30 ° or at most ⁇ 20 °.
  • This also applies analogously to transitions to flanges, cones and other geometric cross-sectional changes - both for tangent and deposited radii.
  • crankshaft For the determination of the highly stressed area or the highest loaded point simulations and / or calculations and / or test series of the respective type of crankshaft can be used.
  • the respective highly stressed areas or the respective highest loaded points of the transition radii may differ at the individual transition radii of the crankshaft. However, the highly stressed area or the most heavily loaded point can also coincide with all transition radii, in particular with one type of transition radii. Optionally, the highly stressed area or the highest loaded point at all transition radii between connecting rod journal and crank webs on the one hand and between main journal and crank cheeks on the other hand.
  • the highly stressed area may, starting from the bottom dead center of the connecting rod journal or the highest loaded point of the main journal, in principle have any desired size, for example less than ⁇ 20 ° or greater than ⁇ 90 °.
  • the highest loaded point (in particular with respect to torsion) of a transition radius of a main journal in the cross section of the crankshaft at the intersection of the transition radius of the main journal with the line connecting the centers of the main journal and the adjacent to the transition radius of the main journal pin connecting rod lies.
  • the highest loaded point of a transition radius of a main journal can be arranged on a side facing away from the bottom dead center of an adjacent connecting rod journal side of the crankshaft.
  • the impact forces which are introduced into the highly stressed region, the low-stressed region and the intermediate intermediate regions of a transition radius can differ from the impact forces which are introduced into the corresponding regions of another transition radius.
  • the patterns of impact forces that are introduced into the respective transition radii may differ, ie, the distribution of the regions along the respective annular circumferential radius of transition and / or the distribution of impact forces and / or the strength of the impact forces within the respective regions. It can be provided, for example, that the maximum impact force, which is introduced into the respective highly stressed region of the transition radii, differs between the transition radii.
  • the impact hardening takes place in such a way that the impressions of a percussion head of at least one percussion tool overlap in a defined manner along the respective transition radius circulating annularly around the crankshaft (in particular around the connecting rod journal and / or main journal).
  • the impact head of the at least one impact tool introduces the impact force at an adjustable impact angle in the transition radius.
  • the highly loaded area, the intermediate areas and / or the low-stress area can also relate to the circumference of the transition radius itself and not only to the circumference of the respective pin around which the transition radius rotates in an annular manner.
  • the stress on a transition radius may also be different along the circumference of the transition radius.
  • the impact angle is chosen such that the impact force is introduced at an angle which is exactly adapted to the highest load during operation of the crankshaft or the maximum load, taking into account the bending load and torsional load, based on the circumference of the transition radius.
  • a striking device is used for impact hardening, comprising a percussion piston, a deflection unit and at least one impact tool, wherein the at least one impact tool is attached to the deflection and wherein the percussion piston transmits a force impulse to the at least one impact tool via the deflection according to which the impact head of the at least one impact tool introduces the impact force into the transition radius.
  • a beating device may be used which has two striking tools which are fastened to a common deflection unit.
  • a percussion piston can be used which transmits a strong impulse or a force impulse (eg pneumatically, hydraulically and / or electrically generated) to the impact head.
  • a strong impulse or a force impulse eg pneumatically, hydraulically and / or electrically generated
  • visible impact impressions of the impact head occur at the respective impact positions.
  • the depth of the impact impressions and the quality or the depth effect of the inherent compressive residual stress depend on the selected impact force.
  • the tool and the process parameters are preferably exactly matched to the respective crankshaft and possibly to partial geometric changes (cross-sectional changes).
  • a position control can be used to rotate the crankshaft step by step from one stroke position to the next stroke position.
  • a PTP control or point control can be provided for this purpose.
  • a drive device may be provided which comprises a motor, in particular an electric motor.
  • the electric motor can be any desired electric motor, for example a three-phase motor (in particular a three-phase asynchronous machine), an AC motor, a DC motor or a universal motor.
  • a stepper motor can be used. It may also be provided a two-part drive means, in which, for example, an engine is provided at each end of the crankshaft, d. H. a synchronous drive or double-sided drive of the crankshaft.
  • crankshaft is rotatably mounted for its processing via a fastening device on a drive shaft.
  • the at least one impact tool with a periodicity preferably with a beat frequency of 0.5 Hz to 30 Hz, more preferably with a clock of 0.5 Hz to 5 Hz and most preferably with a clock from 0.5 Hz to 3 Hz, perform a striking motion or bring in the impact force.
  • a beat frequency preferably with a beat frequency of 0.5 Hz to 30 Hz, more preferably with a clock of 0.5 Hz to 5 Hz and most preferably with a clock from 0.5 Hz to 3 Hz
  • beat frequencies between 0.1 Hz and 50 Hz may be provided, but the above values are particularly suitable.
  • the impact pressures that are converted by the percussion piston to the impact force depending on the operation - between 10 and 300 bar, preferably between 30 and 180 bar, and particularly preferably between 50- 130 bar, be.
  • the impact force can therefore be specified by setting a corresponding impact pressure (the percussion piston).
  • a different impact pressure is used for impact hardening of at least two transition radii.
  • at least one base value and at least one compensation value related to the impact pressure may also be provided.
  • the temperature in the region of the crankshaft segment or transition radius to be machined should preferably not be higher than 65 ° C; values between 12 ° C and 25 ° C are preferred.
  • microcracks have no effect on the fatigue properties, but they can disturb the visual appearance.
  • the removal of the surface can be done in various ways, such as by grinding, turning, milling, turn milling, peeling or polishing.
  • the striking hardening of a transition radius can also be carried out several times around the crankshaft or the pin circumferentially. It can therefore also be provided to impact-strengthen areas or sections which have already been previously impact-hardened.
  • the regions (that is to say the region which is subject to high stress, the region which is less stressed and / or the intermediate regions) may partially overlap or be defined over an angle section which is greater than 360 °.
  • the ranges may be defined, for example, over an angle section of 540 °, 720 °, 900 °, 1080 ° or more.
  • first impact-strengthen by 360 ° with a first striking force along the annular circumferential transition radius and then with a second impact force.
  • force which may also be identical to the first impact force, the intermediate areas and the high-stress area to be impact-strengthened and in a third cycle with a third impact force, which may also be identical to the first and / or second impact force, the high-stressed area schlagzuverfestigen.
  • the impact can also be such z. B. be increased starting from the intermediate areas in the direction of the highly stressed area that impact forces are introduced into the annular peripheral transition radius in several rounds. The impact force can therefore be introduced as the sum of several individual impact forces.
  • the invention also relates to a device for carrying out a method as described above for impact hardening of transition radii of a crankshaft, in particular of transition radii between connecting rod journal and crank webs and / or transition radii between the main journal and the crank webs of the crankshaft.
  • the device is also suitable for impact hardening of transitions to flanges, cones and other geometrical cross-sectional changes - both tangent and deposited radii.
  • some of the components of the device according to the invention may correspond in their construction to the device according to EP 1 716 260 B1, for which reason the disclosure content of EP 1 716 260 B1 is completely integrated into the present disclosure by referencing.
  • the invention also relates to a computer program with program code means in order to carry out the method according to the invention when the program is executed on a control and / or regulating device, in particular on a microprocessor.
  • the invention also relates to a crankshaft made by a method as described above.
  • crankshaft according to the invention differs from conventional crankshafts in particular in that for their solidification in at least two transition radii different sized impact forces were introduced. Furthermore, the crankshaft may differ from conventional crankshafts in that impact forces in at least one of the transition radii along the annular circumferential transition radius in different intensities have been introduced in some areas in order to solidify them. Furthermore, the crankshaft according to the invention may differ from conventional crankshafts in that, if necessary, more than one impact angle may be used for their hardening was used, resulting in a total of a characteristic hardening of the transition radii of the crankshaft.
  • FIG. 1 shows an overall view of a device according to the invention for carrying out the method of a first embodiment
  • FIG. 2 shows a perspective view of a part of the device according to the invention for carrying out the method in a second embodiment
  • FIG. 3 shows a striking device with two impact tools in an enlarged view according to detail "A" of Fig. 1.
  • FIG. 5 shows an exemplary detail of a crankshaft and a force diagram
  • FIG. 7 shows an exemplary division of an annular circumferential transition radius into a highly stressed area, a little stressed area and intervening intermediate areas of an exemplary journal
  • 9 shows an exemplary distribution of impact forces along an annular radius around a pin in a second embodiment
  • 10 shows an exemplary distribution of impact forces along an annular radius around a pin circumferential transition radius in a third embodiment.
  • Fig. 1 1 shows an exemplary distribution of impact forces along an annular radius around a pin circumferential transition radius in a fourth embodiment.
  • the device shown in Figure 1 in an overall view basically corresponds in its structure to the devices according to DE 34 38 742 C2 and EP 1 716 260 B1 with one or more impact devices 1, which is why hereinafter only on the essential parts and on the differences to the prior Technology is discussed in more detail.
  • the device has a machine bed 2 and a drive device 3.
  • the drive device 3 is used to bring or rotate a crankshaft 4 along a direction of rotation in an impact position.
  • crankshaft 4 has connecting rod journal 5 and main journal 6, between which each crank webs 7 are arranged on.
  • Transverse radii 8 (cf., FIGS. 3 to 5) are formed between connecting rod journal 5 and crank webs 7 and between main bearing journal 6 and crank webs 7 or generally between cross-sectional transitions of crankshaft 4.
  • a fastening device 9 On the side facing the drive device 3 side of the crankshaft 4, a fastening device 9 is provided, which has a clamping disk or a mounting flange 10.
  • a support 1 1 On the side facing away from the drive device 3 side of the crankshaft 4, a support 1 1 is preferably provided in the manner of a tailstock, which has a further fastening means 9 to receive the crankshaft 4 rotatable bar or rotatable set.
  • a Lü- nice which is positioned at a rotationally symmetrical location, may be provided.
  • the drive device 3 is able to set the crankshaft 4 along a rotation axis C in a rotational movement. It can be provided that the main axis of rotation C K w of the crankshaft 4 is positioned off-center of the axis of rotation C of the drive device 3, as shown in Figure 1 and Figure 2.
  • alignment means 17 may preferably be provided in the region of the fastening device 9. It can be provided that the alignment means 17 a central axis of each to be solidified pin 5, 6 shift so that the central axis of the pin 5, 6 is located on the axis of rotation C.
  • a direct drive preferably without a clutch
  • An engine, preferably an electric motor, of the drive device 3 can thus be mechanically coupled without transmission or transmission to the fastening device 9 or to the crankshaft 4.
  • the impact devices 1 described in more detail below by way of example are each held adjustably in a displacement and adjusting device 15 in order to adapt them to the position of the connecting rod journal 5 and the main bearing journal 6 and to the length of the crankshaft 4.
  • the support 1 1 may be arranged to be displaceable, as indicated by the double arrows in Figure 1.
  • FIG. 1 shows two impact devices 1, but in principle any number of impact devices 1 may be provided, for example only a single impact device 1.
  • At least one impact device 1 is designed and arranged for impact hardening of the transition radii 8 of the main bearing journals 6 and that a striking device 1 is designed and set up for impact hardening of the transition radii 8 of the connecting rod journals. According to the invention it is provided that in at least two transition radii 8 different impact forces F s are introduced. The inventors have recognized that this concentricity error can be avoided or compensated.
  • FIG. 2 is a fragmentary perspective view of a further device for carrying out the method according to the invention, but without a beating device.
  • the device of FIG. 2 is essentially identical to the device of FIG. 1, for which reason reference will be made below only to the essential differences in detail.
  • a drive device 3 is provided.
  • a fastening device 9 is provided, which has a fastening flange 10 and an attached face plate with clamping jaws for fixing the crankshaft 4.
  • the face plate with the clamping jaws of the fastening device 9 is adjustably arranged on the mounting flange 10 on an alignment means 17, whereby the longitudinal axis C K w of the crankshaft 4 can be displaced relative to the axis of rotation C of a drive shaft or an input shaft 13.
  • crankshaft 4 of FIG. 2 has a configuration differing from the embodiment shown in FIG. 1, but basically also comprises connecting rod journal 5, main bearing journal 6 and crank webs 7.
  • FIG. 2 (as in FIG. 1), it is possible to turn away from the drive device 3
  • End of the crankshaft 4 may be provided a further fastening device 9, but this may also be omitted.
  • FIG. 3 shows, by way of example, a beating device 1 of FIG. 1 in greater detail.
  • the invention can in principle be implemented with any impactor 1.
  • the impact device 1 described below is particularly suitable. It has a main body 18, which accordingly the radius of the crankshaft segment to be machined can be provided with a prismatic system and preferably guides 19 which guide two impact tools 16 in the support plane and give them a corresponding freedom about a deflection unit 20, which is advantageous for adaptation to the dimensional conditions of the crankshaft 4 ,
  • At the front ends of the two impact tools 16 each have a ball is arranged as a striking head 21.
  • An intermediate part 22 establishes the connection between a percussion piston 23 and the deflecting unit 20, which transmits the impact energy to the striking tools 16.
  • the intermediate part 22 may optionally be omitted.
  • the same impact force F s is introduced in two transition radii 8 adjoining the same connecting rod journal 5.
  • the same impact force F s is introduced in two transition radii 8 adjoining the same main journal 6.
  • a beating device 1 shown in FIG. 3 is particularly suitable for this purpose.
  • a striking device 1 with two impact tools 16 is configured such that the striking tools 16 introduce a respective different impact force F s into the transition radii 8 adjoining the same pin 5, 6.
  • a clamping prism 24 can be fastened by means of springs 25 with adjustable clamping bolts 26 with clamping nuts 27 on the side of the journal 5, 6 facing away from the main body 18.
  • the percussion piston 23 transmits a force impulse to the percussion tools 16 via the deflecting unit 20, whereafter the striking heads 21 of the percussion tools 16 introduce the striking force F s into the transition radii 8.
  • FIG. 4 shows a striking device 1, which is provided with only one striking tool 16.
  • the impactor 1 is preferably inclined to the crankshaft 4, in such a way that the impact tool 16, coaxial with the longitudinal axis of
  • Impact device 1 is arranged, perpendicular to the area of the crankshaft segment to be machined, in this case of the transition radius 8 to be machined, impinges. Although only one crankshaft segment can be machined in this case, on the other hand the structural design and the power transmission of the impact device 1 are better and simpler for this purpose. In addition, bore ends can be solidified with this tool standing.
  • This embodiment proves to be particularly advantageous for use on non-symmetrical crankshaft segments, such as the end regions and the oil bore ends of the crankshaft 4.
  • FIG. 5 shows an exemplary detail of a crankshaft 4 with respective transition radii 8 between connecting rod journal 5 and crank webs 7 and main journal 6 and crank webs 7.
  • the same impact force F s is introduced into the transition radii 8 of at least two main bearing journals 6, preferably into the transition radii 8 of all main bearing journals 6.
  • the same impact force F s is introduced into the transition radii 8 of at least two connecting rod journal 5, preferably into the transition radii 8 of all connecting rod journal 5.
  • a first striking force F s is introduced into the transition radii 8 of a first main bearing journal 6, and a second striking force F s is introduced into the transition radii 8 of a second main bearing journal 6.
  • an individual impact force F s is introduced into the transition radii 8 of each main journal 6.
  • an underlying value F 0 for the impact forces F s to be introduced into the transition radii 8 is determined on the basis of the desired fatigue strength of the crankshaft 4 and / or on the basis of the desired fatigue strength of sections of the crankshaft 4. It may further be provided that the base value F 0 is varied by a compensation value F A in order to compensate, avoid and / or minimize concentricity errors of the crankshaft 4.
  • FIG. 5 schematically shows a force diagram for this purpose. It can be seen that the impact force F s is based on a base value F 0, on the basis of which the compensation value F A effects an additive or subtractive modification.
  • the base value F 0 and the compensation value F A are selected such that a minimum impact force F min , which is required at the respective transition radius 8, is not exceeded.
  • a safety margin is additionally provided.
  • the compensation value F A is determined individually for a plurality (preferably for each) transition radius 8 in order to compensate, avoid and / or minimize concentricity errors of the crankshaft 4.
  • FIG. 5 shows the state of affairs or the force diagram only as an example for a transition radius 8. However, this is not meant to be limiting.
  • the compensation value F A is at most 30%, preferably at most 15%, particularly preferably at most 5%, of the base value F 0 .
  • the compensation value F A is at most 30%, but at least 20%, at most 20%, but at least 15%, at most 15%, but at least 10%, or at most 10%, but at least 5%, of the underlying F 0 is.
  • a low-stressed region B M IN and intervening intermediate regions B Z w are defined, after which the impact strength is such that the impact force F s introduced into the intermediate regions B Z w is increased in the direction of the highly stressed region ⁇ ⁇ ⁇ .
  • the impact force F s which is introduced in the impact hardening in the highly stressed area B MAX , is determined based on the desired fatigue strength of the crankshaft 4 and / or the desired fatigue strength of portions of the crankshaft 4.
  • the transition radii 8 respectively adjacent to the pins 5, 6 can have highly stressed areas ⁇ ⁇ ⁇ , which are each located at different positions.
  • An exemplary load on the crankshaft 4 is shown in FIG. 5 by a large arrow shown at the top left.
  • the connecting rod journal 5 is along of the arrow via a piston, not shown, connected to the engine.
  • this is the so-called pressure side.
  • On the opposite side of the pressure side, namely the tension side there is the so-called bottom dead center UT of the connecting rod journal 5.
  • the load on bending of the respective transition radii 8 is the highest according to experience.
  • the highly stressed area B M AX can be defined adjacent to the bottom dead center UT, preferably surrounded symmetrically.
  • a point of maximum load of the main journal 6 adjacent to the connecting rod journal 5 can be a region which corresponds to the pressure side of the adjacent connecting rod journal 5.
  • this area of a main journal 6 will hereinafter be referred to as "top dead center" OT.
  • FIG. 5 For a better clarification of the positions of the dead centers UT, OT, a schematic section through the crankshaft 4 along the illustrated section line "VI" of FIG. 5 is shown in FIG.
  • the highest loaded point or the top dead center OT a transition radius 8 of a main journal 6 in the cross section of the crankshaft 4 at the intersection of the transition radius 8 of the main journal 6 with the connecting line x of the centers M H , M P of the main journal 6 and is located on the transition radius 8 of the main journal 6 adjacent connecting rod journal 5.
  • Figure 7 shows a section through an exemplary pin 5, 6, to illustrate the possible distribution of the areas BMAX, B M IN, B Z w along the circumference of the pin 5, 6.
  • the highest loaded point of the pin 5, 6, ie the bottom dead center UT of a connecting rod journal 5 or the top dead center OT of a main journal 6 is designated by 180 °.
  • the high-stress area B MAX is defined along the transition radius 8 which is annular around the crankshaft 4.
  • the highly stressed region B M AX may, starting from this point preferably symmetrically, be at least ⁇ 20 °, preferably at least ⁇ 30 °, more preferably at least ⁇ 40 °, more preferably at least ⁇ 50 °, most preferably at least ⁇ 60 ° , For example, at least ⁇ 70 °, at least ⁇ 80 ° or at least ⁇ 90 °.
  • Adjacent to the highly stressed area B MAX are defined two intermediate areas B zw , which define the high-stress area B MAX of the low-stressed area B M
  • the intermediate regions B zw can comprise an arbitrary angle section along the annular peripheral transition radius 8. The same applies to the less stressed area B M IN-
  • the respective angular ranges can be determined by calculations, simulation and / or test series, possibly also from measurements in real-time operation (of the engine).
  • the impact force F s introduced into the intermediate regions B Z w is preferably increased (preferably continuously) in the direction of the highly stressed region B MAX . In that the impact force F s is increased, it is meant that the impact force F s between successive strikes is preferably increased further and further.
  • FIGS. 8 to 11 show four exemplary courses of the striking force F s along the circumference of a pin 5, 6, for example of the pin 5, 6 from FIG. 7.
  • the impact force F s introduced in the high-stress areas B MAX is greater than or at least equal to the respective maximum impact force F s which is introduced into the intermediate areas B Z w (and of course each greater than the impact force F s , which is introduced into the low-stress area B M IN).
  • the maximum impact force F MAX is thus introduced in the highly stressed region B MAX of the transition radius 8. Furthermore, an exemplary distribution of forces is shown in FIGS. 8 and 11, in which no impact force F s is introduced during impact hardening in each case in the low-stressed region B M IN.
  • an impact force F on the other hand is introduced s in which each little stressed region B M IN during impact solidifying, which is less than the lowest impact force F s, which is introduced in the intermediate areas B zw.
  • a minimum impact force F min is provided, whereas in the less stressed region B M
  • the impact force F s is prepared starting from the intermediate regions B zw to the most heavily loaded point or the lower dead center BDC and the upper dead center OT opposite lying position linearly decreased steadily to a minimum value, in this case becomes 0.
  • the course of the striking force F s follows a continuous ramp which, starting from a point located along the circumference of the crankshaft 4, the highest loaded point or the bottom dead center UT or top dead center TDC respectively in the direction of the highest loaded point or of bottom dead center UT and top dead center TDC, respectively.
  • the course of the striking force F s follows in each case in the respective areas B M IN, B Z W and B MAX each of its own ramp function, which together result in the illustrated ramp.
  • FIG. 10 shows a profile of the striking force F s , which fundamentally resembles the profile of the striking force F s of FIG. In the intermediate regions B zw , however, in contrast to the linear or ramp-shaped change in the impact force F s shown in FIG. 8, a smoothed curve is shown.
  • 1 1 shows a diagram in which the impact forces F s can be changed in the intermediate areas in gradations Respectively.

Landscapes

  • Chemical & Material Sciences (AREA)
  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Crystallography & Structural Chemistry (AREA)
  • Materials Engineering (AREA)
  • Metallurgy (AREA)
  • Organic Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)
  • Heat Treatment Of Articles (AREA)

Abstract

L'invention concerne un procédé pour la consolidation par percussion de rayons de transition (8) d'un vilebrequin (4), en particulier de rayons de transition (8) entre des tourillons de coussinet de bielle (5) et des bras de manivelle (7) et/ou de rayons de transition (8) entre des tourillons de montage principaux (6) et les bras de manivelle (7) du vilebrequin (4). Selon l'invention, des forces de percussion (FS) plus ou moins importantes sont appliquées dans au moins deux rayons de transition (8).
PCT/EP2018/063691 2017-06-14 2018-05-24 Procédé et dispositif pour la consolidation par percussion de rayons de transition d'un vilebrequin Ceased WO2018228792A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017113070.5 2017-06-14
DE102017113070.5A DE102017113070B3 (de) 2017-06-14 2017-06-14 Verfahren zum Schlagverfestigen von Übergangsradien einer Kurbelwelle

Publications (1)

Publication Number Publication Date
WO2018228792A1 true WO2018228792A1 (fr) 2018-12-20

Family

ID=62245313

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/063691 Ceased WO2018228792A1 (fr) 2017-06-14 2018-05-24 Procédé et dispositif pour la consolidation par percussion de rayons de transition d'un vilebrequin

Country Status (2)

Country Link
DE (1) DE102017113070B3 (fr)
WO (1) WO2018228792A1 (fr)

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3438742A1 (de) 1984-10-23 1986-04-30 Maschinenfabrik Alfing Keßler GmbH, 7080 Aalen Verfahren zur steigerung der dauerfestigkeit von bauteilen unterschiedlicher formgebung
EP1034314B1 (fr) 1997-11-26 2003-01-08 Maschinenfabrik Alfing Kessler GmbH Dispositif de durcissement electro-inductif de surfaces de portee et de rayons de transition de vilebrequins
EP0788419B1 (fr) 1994-10-24 2003-01-08 Ingersoll Cm Systems, Inc. Procede et appareil de fabrication de vilebrequins
EP1479480A1 (fr) 2003-05-20 2004-11-24 Lonero engineering Co., Inc Tête de rouleau d'écrouissage
EP1612290A1 (fr) 2004-07-02 2006-01-04 METAPLAS IONON Oberflächenveredelungstechnik GmbH Procédé et installation pour la nitruration à l'aide de gaz d'un substrat et substrat obtenu.
EP1716260A1 (fr) * 2004-02-23 2006-11-02 Maschinenfabrik Alfing Kessler GmbH Procede et dispositif d'augmentation de la limite de fatigue, notamment de la resistance a la flexion alternee et de la resistance a la torsion alternee d'arbres de vilebrequins
DE102005032185A1 (de) * 2005-07-09 2007-01-18 Volkswagen Ag Verfahren zur Erhöhung der Dauerfestigkeit von Kurbelwellen
DE102007028888A1 (de) 2007-06-20 2009-01-02 Maschinenfabrik Alfing Kessler Gmbh Verfahren zur Erhöhung der Festigkeit eines Bauteils
WO2015141611A1 (fr) * 2014-03-20 2015-09-24 本田技研工業株式会社 Vilebrequin et procédé de renforcement de composant d'arbre

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006058710A1 (de) * 2006-12-13 2008-06-19 Daimler Ag Werkzeugmaschine und Bearbeitungsvorrichtung zum Verfestigen von Radienübergängen an Kurbelwellen für Brennkraftmaschinen oder ähnlichen Werkstücken
US20140260787A1 (en) * 2013-03-18 2014-09-18 Electro-Motive Diesel, Inc. Selectively strengthened crankshaft

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3438742A1 (de) 1984-10-23 1986-04-30 Maschinenfabrik Alfing Keßler GmbH, 7080 Aalen Verfahren zur steigerung der dauerfestigkeit von bauteilen unterschiedlicher formgebung
EP0788419B1 (fr) 1994-10-24 2003-01-08 Ingersoll Cm Systems, Inc. Procede et appareil de fabrication de vilebrequins
EP1034314B1 (fr) 1997-11-26 2003-01-08 Maschinenfabrik Alfing Kessler GmbH Dispositif de durcissement electro-inductif de surfaces de portee et de rayons de transition de vilebrequins
EP1479480A1 (fr) 2003-05-20 2004-11-24 Lonero engineering Co., Inc Tête de rouleau d'écrouissage
EP1716260A1 (fr) * 2004-02-23 2006-11-02 Maschinenfabrik Alfing Kessler GmbH Procede et dispositif d'augmentation de la limite de fatigue, notamment de la resistance a la flexion alternee et de la resistance a la torsion alternee d'arbres de vilebrequins
EP1716260B1 (fr) 2004-02-23 2008-01-09 Maschinenfabrik Alfing Kessler GmbH Procede d'augmentation de la limite de fatigue, notamment de la resistance a la flexion alternee et de la resistance a la torsion alternee d'arbres de vilebrequins
EP1612290A1 (fr) 2004-07-02 2006-01-04 METAPLAS IONON Oberflächenveredelungstechnik GmbH Procédé et installation pour la nitruration à l'aide de gaz d'un substrat et substrat obtenu.
DE102005032185A1 (de) * 2005-07-09 2007-01-18 Volkswagen Ag Verfahren zur Erhöhung der Dauerfestigkeit von Kurbelwellen
DE102007028888A1 (de) 2007-06-20 2009-01-02 Maschinenfabrik Alfing Kessler Gmbh Verfahren zur Erhöhung der Festigkeit eines Bauteils
WO2015141611A1 (fr) * 2014-03-20 2015-09-24 本田技研工業株式会社 Vilebrequin et procédé de renforcement de composant d'arbre
US20170165742A1 (en) * 2014-03-20 2017-06-15 Honda Motor Co., Ltd. Crankshaft and method of strengthening shaft component

Also Published As

Publication number Publication date
DE102017113070B3 (de) 2018-11-15

Similar Documents

Publication Publication Date Title
DE19606732C2 (de) Gefügte Mehrlagenwellen
DE69704690T2 (de) Verfahren zur Herstellung einer hohlen Turbinschaufel und Anlage zum laufenden Warmverwinden
EP0144981B1 (fr) Procédé et dispositif pour le forgeage de vilebrequins sur des presses
EP3609649B1 (fr) Procédé de post-traitement d'un vilebrequin
EP1452272A1 (fr) Procédé de galetage de la zone de transition entre tourillon et flanc de vilebrequins
WO2010054648A1 (fr) Procédé pour augmenter la rigidité en flexion de vilebrequins
DE112005002861T5 (de) Kurbelwelle und Verfahren zum Fertigen einer solchen Kurbelwelle
WO2018228795A1 (fr) Procédé et dispositif de consolidation par percussion de rayons de transition d'un vilebrequin
DE102017113065B3 (de) Verfahren und Vorrichtung zum Schlagverfestigen von Übergangsradien einer Kurbelwelle
DE10258143B4 (de) Verfahren und Honvorrichtung zur Honbearbeitung
DE19500078A1 (de) Verfahren zur Verringerung des relativen Bruchmomentes im Bereich von Sollbruchstellen von Bauteilen
DE102017113070B3 (de) Verfahren zum Schlagverfestigen von Übergangsradien einer Kurbelwelle
DE102017113088A1 (de) Verfahren und Vorrichtung zum Kaltverfestigen einer Kurbelwelle
DE102017113066B3 (de) Verfahren zum Schlagverfestigen von Übergangsradien einer Kurbelwelle
WO2018228797A1 (fr) Procédé et dispositif pour consolider par percussion des rayons de transition d'un vilebrequin
DE19916492A1 (de) Kurbelwelle für eine Brennkraftmaschine
DE19922303A1 (de) Verfahren zur Herstellung einer gebauten Kurbelwelle für eine Hubkolbenmaschine
DE102004042707B4 (de) Kurbelwelle und Verfahren zu ihrer Herstellung
DE102017113074B3 (de) Verfahren und Vorrichtung zum Schlagverfestigen eines Übergangsradius einer Kurbelwelle
EP3615264B1 (fr) Procédé et dispositif de traitement par impact de rayons de transition d'un vilebrequin
DE4222748C2 (de) Verfahren und Vorrichtung zum Gesenkschmieden von einstückigen großen Kurbelwellen mit mehreren Kurbelkröpfungen aus einem Stab
DE10202547C1 (de) Verfahren zum Bearbeiten von Hubzapfen einer Kurbelwelle sowie danach hergestellte Kurbelwelle
DE10061042C2 (de) Gebaute Kurbelwelle und ein Verfahren zur Herstellung derselben
DE1752597A1 (de) Verfahren zum Schmieden von Rohlingen,bestehend aus mehreren nicht-koaxialen Teilen mittels einer Vorrichtung mit einem einzigen Freiheitsgrad
DE2310913C3 (de) Verfahren und Vorrichtung zum Verfestigen von Zahnradzahnen

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18727277

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18727277

Country of ref document: EP

Kind code of ref document: A1