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WO2018228797A1 - Procédé et dispositif pour consolider par percussion des rayons de transition d'un vilebrequin - Google Patents

Procédé et dispositif pour consolider par percussion des rayons de transition d'un vilebrequin Download PDF

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Publication number
WO2018228797A1
WO2018228797A1 PCT/EP2018/063696 EP2018063696W WO2018228797A1 WO 2018228797 A1 WO2018228797 A1 WO 2018228797A1 EP 2018063696 W EP2018063696 W EP 2018063696W WO 2018228797 A1 WO2018228797 A1 WO 2018228797A1
Authority
WO
WIPO (PCT)
Prior art keywords
impact
crankshaft
transition radii
transition
connecting rod
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/EP2018/063696
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 WO2018228797A1 publication Critical patent/WO2018228797A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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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
    • B24B39/045—Burnishing machines or devices, i.e. requiring pressure members for compacting the surface zone; Accessories therefor designed for working external surfaces of revolution the working tool being composed of a plurality of working rolls or balls
    • 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
    • C21D11/00—Process control or regulation for heat treatments
    • 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
    • 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

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 13.
  • 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.
  • At least two impact tools are used for impact hardening. It is envisaged that at least one of the percussion tools impact-bonded the transition radii adjacent to the connecting rod journal and at least one other percussive impact-hardened the transition radii adjacent to the main journal, wherein a sequence for the impact hardening of the transition radii is determined such that concentricity error of the crankshaft balanced and / or minimized become.
  • a sequence is to be understood as meaning the time sequence of impact hardening of the individual transition radii. It can be provided, for example, that all transition radii of the crankshaft are successively impact-solidified. It can, for.
  • any number of transition radii can be impact-solidified simultaneously or sequentially-in any desired combinations-with the sequence being selected such that concentricity errors of the crankshaft are compensated and / or minimized.
  • the striking tools which are used for impact hardening, bring a striking force into the respective transition radius during impact hardening.
  • an impact 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 Schlagverfes- tion of the transition radii of the crankshaft basically all the transition radii successively, starting from a first end of the crankshaft toward a second end of the crankshaft, are impact-solidified, either only a single percussion tool is used or two striking tools, which, however, are only intended to simultaneously impact-strengthen two transition radii adjoining the same pin.
  • the inventors have realized that sufficient impact flexibility is provided by the use of at least two striking tools, wherein at least one of the striking tools for impact bonding of the connecting rod journal adjacent transition radii and at least one other impact tool for impact hardening of the main journal adjacent transition radii is used can be, whereby the sequence, with the impact-hardened, individually tuned to the respective crankshaft or the respective type of crankshaft that concentricity error of the crankshaft in the optimal case completely excluded and thus the cost of a later concentricity correction is minimized.
  • crankshafts can be made with at least the same quality or robustness, as with the known methods of the prior art.
  • the method according to the invention or the device according to the invention can also be used or used in 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 sequence is determined on the basis of simulations, calculations and / or test series of the respective type of crankshaft.
  • an optimization of the sequence or of the method for impact hardening can take place by firstly producing a crankshaft of a specific type of crankshaft, after which the deformation or concentricity of the crankshaft is measured.
  • the sequence of impact hardening of the transition radii can then be varied, wherein after the production of this crankshaft, this is likewise measured with respect to deformation or concentricity.
  • the sequence for a crankshaft type can then be continuously optimized for concentricity errors on this basis.
  • the sequence for optimum impact hardening to avoid concentricity error may also be the same or similar for crankshaft types of the same or similar configuration.
  • the sequence has a connecting rod bearing subsequence after which the transition radii of the connecting rod journal are first impact-hardened, after which the transition radii of the main journal are impact-hardened in a main bearing subsequence.
  • the sequence has a main bearing subsequence, after which the transition radii of the main bearing journals are first impact-hardened, after which the transition radii of the connecting-rod journals are impact-hardened in a connecting-rod bearing subsequence.
  • a subsequence may be provided for each transition radius type.
  • more than two subsequences can also be provided if there are more than two types of transition radii in the crankshaft which are to be impact-solidified successively.
  • the order which type of transition radius is first impact-hardened can under certain circumstances sufficiently compensate for and / or minimize the problem of concentricity errors.
  • the impact hardening according to the subsequences takes place in each case according to a fixed pattern, preferably according to one of the following schemes, according to which the respective transition radii of the crankshaft
  • impact hardening according to which the impact hardening according to the connecting rod bearing subsequence takes place according to another scheme than the impact hardening according to the main bearing subsequence.
  • transition radii of a first type of transition radii starting from the first end of the crankshaft to the second end of the crankshaft, are successively impact-solidified and the transition radii of another type of transition radii are impact-solidified successively along the opposite direction of the crankshaft, then possibly Compensate for deformation of the crankshaft advantageous, which can lead to a low concentricity error of the crankshaft.
  • Such a "chaotic" scheme may be particularly advantageous in order to avoid concentricity errors of the crankshaft by targeted impact forces are introduced so that concentricity errors are compensated.
  • initially all transition radii of the connecting rod journal are chaotically impact-hardened and subsequently all the transition radii of the main bearing journal are chaotically impact-hardened - or vice versa.
  • the sequence has at least one partial sequence which provides that one or more transition radii of the main bearing journals are impact-hardened, after which one or more transition radii of the connecting-rod journals are then impact-hardened and then again one or more transition radii of the Main bearing pins are impact-hardened.
  • the sequences have at least one partial sequence which provides that one or more transition radii of the connecting rod journal are impact-hardened, after which one or more transition radii of the main journal are then impact-hardened and subsequently one or more transition radii of the connecting rod journal are impact strengthened.
  • a transition-type overlapping chaotic impact hardening is also possible. This also applies to transitions to flanges, cones and other geometric cross-sectional changes - both for tangent and deposited radii alike.
  • a sequence can be provided in which at least two transition radii are simultaneously impact-solidified.
  • two transition radii adjoining the same pin are simultaneously impact-strengthened.
  • the subsequences when using the subsequences, it can be provided that, within a subsequence, several transition radii, in particular transition radii adjoining the same cones, are simultaneously impact-solidified.
  • the subsequences can therefore also refer to groups of transitional radii. Even with a chaotic impact hardening it can be provided that at least two transition radii adjoining the same pin are simultaneously impact-hardened, after which one or more transition radii are subsequently skipped or become. In a further development, it may further be provided that three, four or more impact tools are used for impact hardening.
  • even more striking tools can be provided, for example five, six, seven, eight, nine, ten or even more striking tools.
  • 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.
  • two adjacent to the same pin transition radii can be simultaneously impact strengthened.
  • a plurality of such impact devices may be provided, in particular a striker for each type of transition radius, and most preferably a striker for impact hardening of transition radii adjacent to the connecting rod trunnions and another striker for impact hardening of transition radii adjacent to the main journal.
  • a striker for each type of transition radius and most preferably a striker for impact hardening of transition radii adjacent to the connecting rod trunnions and another striker for impact hardening of transition radii adjacent to the main journal.
  • three, four, five or more impact devices may be provided, wherein the impact devices used also different configurations, eg. B. may have a different number of striking tools.
  • a beating device can be provided with two striking tools as well as a further beating device with only one striking tool.
  • 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 e.g pneumatically, hydraulically and / or electrically generated
  • 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 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 inventors have recognized that an improvement of the concentricity does not occur exclusively because in now critical for the concentricity portions of the crankshaft or in transition radii of the crankshaft compared to other sections now also reduced impact force can be introduced, but in particular also because The residual compressive stresses can now be distributed differently over the crankshaft, but in each case the minimum required residual compressive stresses are introduced in each transition radius.
  • Very particularly advantageous concentricity errors of the crankshaft can be compensated and / or minimized if the sequence and the impact forces to be introduced into the individual transition radii are each adapted or determined jointly for the corresponding type of crankshaft.
  • the same impact force is introduced in two adjacent to the same connecting rod journal transition radii.
  • the same impact force is introduced in two transition radii adjoining the same main journal.
  • transition radii in which the same impact force is introduced.
  • two transition radii adjoining the same pin can each form a group.
  • the same impact force is introduced.
  • transition radii of all main journals a 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 be advantageous to introduce the same impact force in all transition radii of the main journal and in all transition radii of the connecting rod journal, wherein the impact force which is introduced into the transition radii of the main journal, in this case of the impact force, which is introduced into the transition radii of the connecting rod journal, differs.
  • a first connecting rod journal in the transition radii of a first connecting rod journal a first impact force and in the transition radii of a second connecting rod journal a second (deviating from the first impact) impact force is introduced.
  • an individual impact force can be introduced into the transition radii of each connecting rod journal.
  • a 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.
  • 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, wherein concentricity errors can be further suppressed or compensated.
  • the fatigue strength of the crankshaft by this measure even exceed the requirements. This is especially true because at the same time the sequence can be optimized for impact hardening.
  • a base value for the forces to be introduced into the transition radii impact forces is determined based on the desired fatigue strength of the Kur- shaft and / or based on the desired fatigue strength of portions of the crankshaft.
  • a base value for the entire crankshaft which may be a minimum impact force, may be determined at which time the desired fatigue strength is achieved in all Sections of the crankshaft is still guaranteed, 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 an equalization value in order to compensate, 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.
  • the compensation value for several, preferably for each transition radius is determined individually to compensate for runout of the crankshaft, to avoid and / or minimize.
  • 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 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 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.
  • crankshaft d. H. a synchronous drive or double-sided drive of the crankshaft.
  • crankshaft is rotatably fixed for the processing thereof via a fastening device on a drive shaft.
  • the striking tools 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 of 0 , 5 Hz to 3 Hz, perform a flapping motion or bring in the impact force.
  • the impact pressures which 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 more preferably between 50 and 130 bar, amount.
  • 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 invention also relates to a device for carrying out a method 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 manufactured according to a method described above.
  • the crankshaft according to the invention differs from conventional crankshafts in particular in that during the impact hardening a specific sequence or sequence was used when introducing the internal compressive stresses into the transition radii.
  • a characteristic hardening of the transition radii of the crankshaft and a characteristic deformation or a characteristic concentricity of the crankshaft can result overall.
  • the crankshaft may differ from conventional crankshafts in that different strengths of impact force have been introduced into at least two transition radii for their solidification according to a variant of the invention.
  • 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 crankshaft and its striking hardening with two impact devices
  • FIG. 6 shows an exemplary detail of a crankshaft and a force diagram.
  • 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 6) 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 center 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 can also be arranged to be displaceable, as indicated by the double arrows in FIG.
  • At least two impact tools 16 are used, wherein at least one of the impact tools 16 impact-bonded the transition radii 8 adjacent to the connecting rod journal 5 and at least one further impact tool 16 impact-solidifies the transition radii 8 adjacent to the main journal 6, wherein a Sequence for the impact hardening of the transition radii 8 is determined such that concentricity errors of the crankshaft 4 are compensated and / or minimized.
  • two impact devices 1 are shown, but in principle any number of impact devices 1 may be provided, according to the invention at least one impact tool 16 for impact hardening of the transition radii 8 of the main bearing pin 6 and a percussion tool 16 for impact hardening of the transition radii 8 of the connecting rod journal 5 is provided ,
  • At least one impact device 1 is designed and set up for impact hardening of the transition radii 8 of the main bearing journals 6 and a
  • Impact device 1 for impact hardening of the transition radii 8 of the connecting rod journal 5 is formed and arranged, as shown in Figure 1.
  • 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 mounting 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 that shown in FIG. 1, but basically also includes connecting rod journal 5, main bearing journal 6 and crank webs 7.
  • 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 base body 18 which can be provided with a prismatic system according to the radius of the crankshaft segment to be machined and preferably has guides 19 which guide two striking tools 16 in their support plane and give them a corresponding freedom about a deflection unit 20 for adaptation to the dimensional conditions of the crankshaft 4 is advantageous.
  • 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 deflection unit 20, which transmits the impact energy to the impact tools 16.
  • the intermediate part 22 may optionally be omitted.
  • the same impact force F s is introduced in two adjacent to the same connecting rod journal 5 transition radii 8.
  • the same impact force F s is introduced in two transition radii 8 adjoining the same main journal 6. But it can also be provided in principle that in all transition radii 8, the same impact force F s is introduced.
  • a beating device 1 shown in FIG. 3 is particularly suitable for this purpose. It can also be provided that a beating device 1 with two impact tools 16 is configured such that the impact tools 16 introduce a respective different impact force F s into the transition radii 8 adjoining the same journal 5, 6. To increase the effectiveness of the impact, 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.
  • 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.
  • any number of striking tools for example two, three, four, five, six, seven, eight, nine, ten or more may be meant or singular is for readability only and not restrictive.
  • 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 which is arranged coaxially to the longitudinal axis of the impactor 1, perpendicular to the region of the crankshaft segment to be machined, in this case the transition radius to be machined 8, incident.
  • the structural design and the power transmission of the impact device 1 are better and simpler for this purpose.
  • 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.
  • the design of the beating device 1 shown in Figure 4 with only a percussion tool 16 is also particularly suitable when the same pin 5, 6 adjacent transition radii 8 are to be impact-solidified with different degrees of impact F s .
  • the striking devices 1 shown in FIG. 1 or basically the beating devices 1 used for the invention may be a beating device 1 according to FIG. 3 or according to FIG. 4 or any other beating device 1 in any combination. According to the invention, it is important that at least one impact tool 16 is used for impact hardening of the transition radii 8 adjoining the connecting rod journal 5 and at least one further impact tool 16 for impact hardening of the transition radii 8 adjoining the main bearing journal 6.
  • sequence for impact hardening is determined on the basis of simulations, calculations and / or test series of the respective type of crankshaft.
  • transition radii 8 are simultaneously impact-solidified, for example with a beating device 1 with two striking tools 16 according to FIG. 3.
  • FIG. 5 shows an exemplary crankshaft 4 with respective transition radii 8 between connecting rod journal 5 and crank web 7 or main journal 6 and crank web 7 and further cross-sectional transitions with transition radii 8.
  • Two impact devices 1 in a configuration with two striking tools 16 according to FIG. 3 are indicated schematically by way of example.
  • the crankshaft 4 has a first end Ei and a second end E 2 .
  • the sequence for impact hardening has a connecting rod bearing subsequence A, after which first the transition radii 8 of the connecting rod journal 5 are impact-hardened, after which the transition radii 8 of the main bearing pins 6 are impact-strengthened in a main bearing subsequence B.
  • This is shown in Figure 5 by corresponding arrows.
  • the conrod bearing pin 5 associated impact device 1 along the length of the crankshaft 4 is moved from left to right to successively schlagzuverfestigen all connecting rod journal 5.
  • any number of transition radii 8 of the connecting rod journal 5 can be impact-solidified simultaneously and / or sequentially.
  • the transition radii 8 of the main bearing journals 6 can then be impact-hardened in accordance with the second main bearing subsequence B.
  • the impact device 1, which is assigned to the transition radii 8 of the main bearing journals 6 (in FIG. 5, the impact device 1 at the bottom right), can be moved from right to left of main bearing journals 6 are moved to main journal 6 to successively beat each two transition radii 8 of the main journals 6.
  • any number of transition radii 8 of the main bearing journals 6 can be impact-strengthened simultaneously and / or successively with any number of impact devices 1 and / or impact tools 16.
  • the subsequence provided first would be the main stock subsequence B, as shown in FIG. 5, and the subsequence provided below is the conrod subsequence A.
  • the impact hardening according to the subsequences A, B takes place in each case according to a defined scheme, preferably according to one of the following schemes described. For example, from the first end Ei of the crankshaft 4 toward the second end E 2 of the crankshaft 4 or from the center M of the crankshaft 4 to the ends E 1: E 2 or from the ends E 1: E 2 of the crankshaft 4 to whose center M are impact-strengthened, after which the impact hardening according to the connecting rod bearing subsequence A takes place according to a different scheme than the impact hardening according to the main bearing subsequence B.
  • a scheme is provided for the connecting rod bearing subsequence A, according to which the crankshaft 4 is impact-hardened by the first end Ei of the crankshaft 4 in the direction of the second end E 2 , whereas the main bearing subsequence B is designed is to zzizuverfestigen of the second end E 2 of the crankshaft 4 in the direction of the first end Ei of the crankshaft 4.
  • the percussion device 1 of the transitional radii 8 at the positions P ⁇ and P 2 may, for example, in a scheme of connecting rod bearing subsequence A subsequent to the transition radii 8 at positions P 5 and P 6, subsequently to the transition radii 8 at positions P 9 or P 10 and finally to the transition radii 8 of the positions P 13 and P 14 are moved.
  • the scheme of the main bearing sub-sequence B it may be provided, for example, that the impactor 1 of the transition radii 8 at the positions P and P 12 following the transition radii 8 at the positions P 7 and P 8 and finally to the transition radii 8 the positions P 3 and P 4 is moved.
  • the striking hardening according to at least one of the subsequences A, B provides a scheme in which at least in one case after impact hardening of a transition radius 8 at least one of the adjacent transition radii 8 is skipped and initially a further away transition radius 8 is impact-strengthened.
  • the transition radii 8 at the positions P and P 2 could be simultaneously simultaneously or successively impact-hardened, after which the transition radii 8 are simultaneously impact-hardened at the positions P 13 and P 14 , after which the transition radii 8 of the middle Pleuellagerzapfen 5 at the positions P 5 and P 6 or P 9 and P 10 are simultaneously or successively impact-solidified.
  • Such a "chaotic" impact hardening can also be provided analogously for main bearing subsequence B during impact hardening of the transition radii 8 of the main bearing journals 6.
  • the sequence has at least one partial sequence which provides that one or more transition radii 8 of the main bearing journals 6 are impact-hardened, after which one or more transition radii 8 of the connecting rod journals 5 are subsequently impact-hardened and then again one or more transition radii 8 Main bearing pin 6 impact-strengthened.
  • the sequence has at least one partial sequence which provides that one or more transition radii 8 of the connecting rod journals 5 are impact-hardened, after which one or more transition radii 8 of the main bearing journals 6 are subsequently impact-strengthened and then again one or more transition radii 8 of the connecting rod journal 5 are impact-strengthened.
  • the temporal sequence in the course of the subsequences A, B can thus also overlap or interleave.
  • the impactor 1, which is assigned to the connecting rod journal 5 are first used to schlagzuverf the transition radii 8 at the positions or P 2 , after which the impactor 1, which is associated with the main journal 6 is used to the transition radii eighth at the positions P 3 and P 4 impact, after which the impactor 1, which is assigned to the connecting rod journal 5, is subsequently used again to schlagzuverfestigen one or more transition radii 8 of the connecting rod journal 5, etc.
  • FIG. 6 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 second impact force F s is introduced in the transition radii 8 of a first connecting rod journal 5, a first impact force F s and in the transition radii 8 of a second connecting rod journal 5, a second impact force F s is introduced.
  • an individual impact force F s is introduced into the transition radii 8 of each connecting rod journal 5.
  • an individual impact force F s is introduced into the transition radii 8 of each main bearing 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.
  • 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. 6 schematically shows a force diagram for this purpose.
  • 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. 6 shows the situation 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.

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  • 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 consolider par percussion des rayons de transition (8) d'un vilebrequin (4), en particulier des rayons de transition (8) entre des tourillons de coussinet de bielle (5) et des bras de manivelle (7) et des rayons de transition (8) entre des tourillons de montage principaux (6) et les bras de manivelle (7) du vilebrequin (4). Selon l'invention, au moins deux outils (16) de percussion sont utilisés pour la consolidation par percussion, au moins un des outils (16) de percussion consolidant par percussion les rayons de transition (8) adjacents aux tourillons de coussinet de bielle (5) et au moins un autre outil (16) de percussion consolidant par percussion les rayons de transition (8) adjacents aux tourillons de montage principaux (6), une séquence pour la consolidation par percussion des rayons de transition (8) étant définie de telle manière que des erreurs de concentricité du vilebrequin (4) sont compensées et/ou réduites au minimum.
PCT/EP2018/063696 2017-06-14 2018-05-24 Procédé et dispositif pour consolider par percussion des rayons de transition d'un vilebrequin Ceased WO2018228797A1 (fr)

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DE102017113077.2A DE102017113077B4 (de) 2017-06-14 2017-06-14 Verfahren und Vorrichtung zum Schlagverfestigen von Übergangsradien einer Kurbelwelle

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CN112872728A (zh) * 2021-01-14 2021-06-01 中国重汽集团济南动力有限公司 淬火曲轴的加工工艺

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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

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DE3438742C2 (fr) 1984-10-23 1988-03-24 Maschinenfabrik Alfing Kessler Gmbh, 7080 Aalen, De
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

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