EP0275876B1 - Procédé et appareil de dressage d'une pièce - Google Patents

Procédé et appareil de dressage d'une pièce Download PDF

Info

Publication number
EP0275876B1
EP0275876B1 EP88100107A EP88100107A EP0275876B1 EP 0275876 B1 EP0275876 B1 EP 0275876B1 EP 88100107 A EP88100107 A EP 88100107A EP 88100107 A EP88100107 A EP 88100107A EP 0275876 B1 EP0275876 B1 EP 0275876B1
Authority
EP
European Patent Office
Prior art keywords
main bearing
crankshaft
journals
crank
main
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88100107A
Other languages
German (de)
English (en)
Other versions
EP0275876A3 (en
EP0275876A2 (fr
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0275876A2 publication Critical patent/EP0275876A2/fr
Publication of EP0275876A3 publication Critical patent/EP0275876A3/de
Application granted granted Critical
Publication of EP0275876B1 publication Critical patent/EP0275876B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D3/00—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D3/00—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts
    • B21D3/02—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts by rollers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D3/00—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts
    • B21D3/16—Straightening or restoring form of metal rods, metal tubes, metal profiles, or specific articles made therefrom, whether or not in combination with sheet metal parts of specific articles made from metal rods, tubes, or profiles, e.g. crankshafts, by specially adapted methods or means

Definitions

  • the invention relates to a method and a device according to the preambles of claims 1 and 11.
  • the fatigue strength of workpieces with circular grooves is primarily impaired by the reduced strength due to the shape of the materials in the area of these grooves. It is therefore known to treat such workpieces with a method which is referred to as "deep-rolling" and which consists in that deep-rolling rollers with hydraulic cylinders / piston arrangements are pressed against the throat walls which delimit the grooves, in particular the grooves, (DE-C-30 37 688 ). On the one hand, this increases the strength of the materials in the outer layers, and on the other hand, useful compressive residual stresses are generated in the zones adjacent to the throats, which are noticeable in later use of the workpieces by a considerably increased fatigue strength.
  • the invention has for its object to design the method and the device of the aforementioned types so that the desired target fatigue strength is obtained in the deep rolling step in the area of all main bearing and crank pins and the straightening process can nevertheless be carried out with low forces and without additional tools .
  • the invention has the advantage that the cold rolling for straightening can be carried out in several successive steps and the forces exerted in each of these steps of up to approximately 50 kN can be considerably smaller than when using the known device.
  • This makes it possible to use the same devices and tools for straightening, which are also used for deep rolling, without the risk that the deep rolling rollers are overloaded during the straightening process.
  • this enables the workpieces to be deep-rolled and straightened in the same processing station, the workpieces being able to remain clamped during the measurement of the radial run-out deviations, for example by these deviations can be determined with measuring devices integrated in the deep rolling device.
  • Fig. 1 shows a workpiece 1 in the form of a crankshaft.
  • This has five main bearing journals 2a to 2e, the axes of which lie on a theoretical axis 3, here the axis of rotation of the crankshaft, four crank journals 4a to 4d arranged between the main bearing journals 2 and a crank web 5 each between these and the main bearing journals 2.
  • grooves 6a to 6d with circular cross-sections are provided which rotate around the axis 3.
  • the workpieces 1 can consist of steering knuckles, stepped shafts or the like.
  • fillets corresponding to fillets 6 which are generally arranged at the transitions from one cross-section to another and serve to provide the insufficient fatigue strength in the area to enlarge the cross-sectional transitions.
  • FIG. 1 indicates an arbitrarily assumed curvature of the crankshaft in the drawing plane on a greatly enlarged scale.
  • the distances 1 of the respective center points of the main bearing journal 2 from the left end of the crankshaft in FIG. 1 are plotted along the abscissa, while the respective deviation S of these center points from the theoretical axis 3 is plotted along the ordinate in large magnification.
  • the deviations S that actually occur are generally very small, amount to only a few tenths or hundredths of a millimeter and can each be both positive and negative. 1 also relates to a selected rotational angle position of the crankshaft. Corresponding beat diagrams can be drawn for other rotational angle positions.
  • any deviation from the concentricity is broken down into two mutually perpendicular components, one of which lies in a plane called the main plane and the other in a plane called the secondary plane. If all the crank pins 4b to 4c according to FIG. 1 lie in a single plane, which also contains the theoretical axis 3, then this is declared the main plane, while the plane perpendicular thereto is defined as the secondary plane. If, on the other hand, the crank pins 4a to 4d differ from FIG.
  • the axis of the crank pin 4b and the axis 3 define a first plane
  • the axis of the crank pin 4c and the axis 3 define a second plane
  • the bisector between these two planes and the axis 3 define a third plane that in FIG this example would be the main plane for the main journal 2c.
  • the plane perpendicular to this is the secondary plane for this main journal 2c.
  • the main plane for the main bearing journals 2a and 2e located at the ends of the crankshaft, each of which only one crankpin 4a or 4d is adjacent results from the axis 3 and the axes of these crankpins 4a and 4d, while the planes perpendicular thereto the minor levels are.
  • the invention is based on the knowledge that directional operations in the secondary planes also generally result in deformations of the crankshaft in the main planes, while conversely, straightening operations in the main planes cause practically no repercussions or deformations in the secondary planes.
  • the directional strategy according to the invention results from this, first of all eliminating all components of a field located in the secondary planes and only then eliminating all components of the field located in the main planes.
  • Corrected straightening parameters are understood in particular to mean that the magnitude of the force required to bring about the remaining straightening dimension ⁇ Sn is changed depending on the history of the crankshaft and, above all, depending on the forces on the main bearing journal in previous steps were exercised. In particular, if a certain straightening force was not sufficient in a first step to bring about the desired straightening dimension, a higher straightening force is selected in a subsequent step. If the straightening parameters used in previous straightening operations are not taken into account, reasonable straightening is hardly possible due to the changing dependence between the straightening dimension and the straightening force. The dependencies of the achievable standard dimensions on the applied directives must be determined empirically.
  • the values obtained in each case can be collected and stored in a database, which can be used as a table of values for the directional forces to be used in the case of statistical handling.
  • a data processing system is therefore preferably used to calculate the straightening forces, in the memory of which all the data relating to a specific workpiece type are collected.
  • the workpiece is aligned in the main levels by correspondingly calculating and empirically determining the guide dimensions ⁇ Sh lying in the main level or values retrieved from the database can be determined for the respective straightening forces.
  • These straightening operations in the main plane are also preferably carried out successively in a plurality of successive steps until finally the remaining deviations for all main bearing journals lie within the defined tolerance ranges.
  • the invention is based on the knowledge that straightening can be carried out by cold rolling and therefore, for example, with the aid of pressure rollers inserted into the throats of the main bearing journal 2, by exerting sufficient pressure on selected circumferential sections of the walls delimiting the throats.
  • the crankshaft is rotated continuously or with a pendulum movement, or the respective pressure roller is guided around the crankshaft or its theoretical axis in a continuous or reciprocating movement. It is only necessary to vary the forces exerted by the pressure rollers on the crankshaft as a function of the respective angular position of the crankshaft with respect to the pressure roller in such a way that a directional effect is only in the required direction, i.e. is achieved when the pressure rollers run onto the preselected sections, while in all other directions no sufficient forces are exerted by the pressure rollers to achieve a directional effect.
  • crankshafts DE-C-30 37 688
  • a device of this type suitable for the purposes of the invention is explained in more detail below with reference to FIGS. 2 to 6 and with reference to a workpiece 1, which consists of a crankshaft with only two crank pins 4a, b and three main bearing pins 2a, b, c.
  • the device contains two master shafts 8a and 8b which are rotatably mounted and arranged one above the other in a frame 7 and which correspond in size and shape to the workpiece 1 to be machined and in the example shown correspondingly many main bearing journals 10a and 10b, crank journals 11a and 11b and crank arms 12a and 12b.
  • Both master shafts 8a, b can be driven synchronously by a motor 13 mounted on the frame 7, on the drive shaft of which a gearwheel 14 is fastened.
  • the gearwheel 14 is connected to a gearwheel 15 fastened on the master shaft 8a, which is connected via a further gearwheel 16 to a gearwheel 17 fastened to the master shaft 8b, so that both master shafts are driven in the same direction when the motor 13 is switched on.
  • Each main bearing and crank pin 10 or 11 is rotatably supported in a lower jaw 18 or 19 of a pincer-type holder for the workpiece 1.
  • Each jaw 18 or 19 is pivotally connected to an upper jaw 21 or 22 of the holder by means of a pivot pin 20 (FIG. 2).
  • the two jaws 18, 21 and 19, 22 each carry a rolling tool.
  • This has in each case two cylindrical support rollers 23 which are rotatably mounted and arranged in parallel in the lower jaw 18 and 19 and a known combination of a profile roller 24 and two pressure or deep-rolling rollers 25 mounted in the upper jaw 21 or 22 (cf. 3 and 4).
  • the axes of rotation of the pressure rollers 25 and the axis 3 of the workpiece 1 or the axes of rotation of the profile rollers 24 parallel thereto generally form an angle of approximately 35 °.
  • the pressure rollers 25 are supported in circumferential grooves 26, which have a circular cross section and at the front ends of the profile roller 24 are formed.
  • the profile roller 24 is rotatably mounted on a shaft 27 fastened in the frame 7, while the deep-rolling rollers 25 are cantilevered on the profile roller 24.
  • Each tong-like holder is assigned a control device, only the control device for the holder and the main bearing journal 2c being shown in FIG. 3.
  • the rolling tool consisting of parts 23 to 25 for holding the main bearing journal 2c to simplify the drawing is only visible in FIG. 4, but not also in FIG. 3.
  • the control device contains a hydraulic or pneumatic cylinder 28, which is fastened to the rear end of the associated lower jaw 18 and in which a piston 29 is slidably mounted and carries a piston rod 30 articulated on the upper jaw 21, so that the upper jaw 21 can be moved in or out Extending the piston rod 30 can be pivoted about the pivot pin 20.
  • the chambers of the cylinder 28 lying on both sides of the piston 29 can optionally be connected via lines 31, 32 and a directional control valve 33 to a line 35 leading to a tank 34 or a further line 36.
  • Line 36 leads to an output of an actuator 37, e.g. of a further directional valve, which is simultaneously designed as a pressure control valve and has a second, blocked outlet.
  • a line 38 connected to the one input of the actuator 37 is either connected via a limiting valve 39 to the one output or via a further limiting valve 40 to the other output of a further directional valve 41, one input of which is blocked off and the other input of which is connected to the output of one Pump 43 driven by a motor 42 for the hydraulic or pneumatic medium, for example Oil, is connected.
  • the outlet of this pump 43 is also connected to a limiting valve 44 which is connected to the tank 34 via a line 45.
  • the output of the pump 43 is still connected to the other input of the actuator 37 via a limit valve 46.
  • the directional control valves 33 and 41 are, for example, with conventional switching magnets 33a and 41a, while the actuator 37 is assigned a control member 37a, which may also consist of a switching magnet.
  • the switching magnets 33a, 41a and the control member 37a are connected to a sequencer 47, and the control member 37a also leads to the output of a power amplifier 48c.
  • each directional control valve 33 and 41 can assume two positions a and b , the position a being the basic position produced by a compression spring 33b, 41b, while the other position b is produced by the corresponding switching magnet 33a, 41a being correspondingly connected via the sequence control 47 is excited.
  • the actuator 37 can also assume two positions a and b , the position b being produced by supplying a control signal to the control member 37a from the sequence control 47 or from the associated power amplifier 48c, while the other position a is the basic position produced by a compression spring 37b.
  • actuator 37 can be controlled by an analog signal from associated power amplifier 48c to assume any intermediate position between the two positions a and b , in which the pressure at its only open output assumes a value which depends on the pressure its two inputs and also depends on the proportions with which the passages indicated by arrows are involved in the passage of the printing medium.
  • all other components can also be used for the actuator 47, by means of which - controlled by electrical signals or the like.
  • the pressure in the line 36 can be continuously adjusted between a minimum and a maximum value.
  • the control device has a measuring element 49 attached to the frame 7 (FIG. 3).
  • the measuring element 49 consists, for example, of a commercially available displacement sensor with a plunger 50, which is pressed against the main bearing journal 2c by a compression spring 51. Depending on the respective position of this plunger 50, an electrical signal appears at the output of the measuring element 49, which is fed to a measuring amplifier 52c assigned to the main journal 2c.
  • a measuring amplifier 52c assigned to the main journal 2c.
  • purely inductive, non-contact displacement sensors can be used to measure the deviations of the main bearing journals from the concentricity.
  • a force meter 53 can be provided for monitoring the forces which are exerted on the associated pressure roller 25 or the workpiece 1 with the upper jaw 21 and which consists, for example, of a strain gauge connected to the jaw 21 and an electrical signal at its output emits, which is also supplied to the measuring amplifier 52c.
  • control devices for the other main bearing journals 2a and 2b are designed accordingly and provided with corresponding measuring amplifiers 52a, b or power amplifiers 48a, b (FIG. 3). Further, similarly constructed control devices can be assigned to the holders for the crank pins 4a, b, although only the parts required for deep-rolling, but not also the parts required for straightening, need be provided.
  • a display element 54 (FIG. 1), e.g. a rotary encoder, which can consist of a conventional angle encoder and whose output signals are fed to an amplifier 55.
  • the output signals of the measuring amplifier 52 and the amplifier 55 are fed via a line bundle 56 to a data processing system 57 and from there via a further line bundle 58 to the power amplifiers 48a, b, c.
  • a data memory 59 (not shown, can be assigned to the computer 57.
  • the workpiece 1 that is to say the crankshaft shown in FIGS. 1 to 4
  • the workpiece 1 is to be subjected, for example, to a conventional deep-rolling process.
  • the directional control valves 33 are first moved into position b by means of the sequence control 47, which is provided with corresponding switches or can be controlled automatically associated switching magnets are excited accordingly.
  • the lines 31 are connected to the tank 34 and the lines 32 to the lines 36, which lead to the pump 43 via the actuators 37 and the limit valves 46.
  • crankshaft to be machined is now inserted into the holder by placing its main bearing or crank pin 2 or 4 on the support rollers 23 of the associated lower jaws 18 or 19, which is easy due to the corresponding shape of the master shafts 8a, b is possible (see in particular Fig. 2).
  • the directional control valves 33 are returned to the basic position a by de-energizing the associated switching magnets and at the same time the actuators 37 are brought into position b by means of the sequence control 47.
  • the lines 32 are connected to the tank 43 and the lines 31 are connected to the pump 43 via the limit valves 39.
  • the motor 13 is switched off and the tong-like holders are opened again by appropriate control.
  • the machined crankshaft can now be removed and measured in any manner and in a manner known per se, in order to determine the deviations existing after the deep rolling process, the guide dimensions ⁇ Sn and ⁇ Sh and the required guide forces.
  • the workpiece 1 is preferably measured when the device described is used by virtue of the fact that it remains clamped in the clamp-like holders and is scanned with the measuring elements 49. So that no large forces are exerted by the pressure rollers 25, the directional control valves 33 and 41 are left in the basic position a , while the actuator 37 is controlled into the position b by means of the sequence control 47. As a result, the line 31 is now connected to the pump 43 via the limiting valve 46, which is set to a lower pressure than the limiting valve 39. After the engine 13 is switched on again, the crankshaft to be machined again performs its characteristic rotary movement.
  • the measuring elements 49 are activated, as a result of which the signals they measure are fed via the measuring amplifiers 52 and the line bundle 56 to the data processing system 57, to which the output signals of the display element 54 are also continuously fed.
  • the data processing system 57 now uses a previously entered program and the continuously supplied data from the measuring members 49 and the display member 54 to first determine the respective size and the respective direction of the concentricity deviations for all main bearing journals 2a, 2b and 2c and then calculates the standard dimensions ⁇ Sn and ⁇ Sh and the straightening forces to be exerted by the pressure rollers 25 on the main bearing journals 2a, b, c, all values and dependencies relating to similar workpiece types stored in the database 59 being able to be taken into account.
  • the data processing system 57 converts the determined directional forces into analogue control signals for the control elements 37a of the actuators 37.
  • crankshaft to be machined remains in the tong-like holders, while the directional control valves 33 and the actuators 37 are controlled into their basic position a .
  • the directional control valve 41 is transferred to position b .
  • the crankshaft to be machined is set back into its characteristic orbital motion, while at the same time the lines 31 are initially only connected to the pump 43 via the limit valves 46.
  • the data processing system continuously transmits control signals which are fed to the control elements 37a via the line bundle 58 and the power amplifiers 48a, b, c.
  • their valve stems are displaced more or less in the direction of the positions b in accordance with the calculated directional forces, with the result that pressure is generated in the lines 36, which may lie between the minimum value of the limiting valve 46 and the maximum value of the limiting valve 40.
  • these are also controlled so that initially only straightening operations are carried out on the secondary levels on all main bearing journals.
  • These straightening operations are preferably carried out for a plurality or all of the main bearing journals simultaneously or in succession and in accordance with the above description in several successive steps, between which the crankshaft is measured again, so that the data obtained are stored in the database 59 and then new straightening parameters are calculated for the next step in each case can be.
  • the advantage here is that the direction in which a straightening operation is carried out on any main journal can be preselected only by the associated actuators 37 providing sufficiently large pressures in the lines 36 at the right moment, while at all other times the pressure in the lines 36 is reduced to a pressure that cannot effect a straightening operation. Since each individual main journal 2a, b, c also has its own bracket and control device , the various straightening operations can be carried out in a single operation even if different main and secondary levels are assigned to all main bearing journals.
  • the maximum system pressure is finally displayed on the limiting valve 44 in order to avoid the occurrence of critical overpressures.
  • the force meter 53 it is possible to constantly monitor the forces actually exerted on the pressure rollers 25 and, if necessary, to provide control circuits for the cylinders 28, so that the straightening forces calculated by the data processing system 57 actually actually apply to the workpieces 1 or the main bearing journal 2 be exercised.
  • the pressures supplied to the cylinders 28 during straightening can also be generated by controlling each actuator 37 with a device shown schematically in FIG. 5.
  • this device contains a sleeve 60, which is connected to the valve stem of the actuator 37 and in which a plunger 61 is displaceably guided.
  • the sleeve 60 has a vertically protruding arm 62 and the plunger 61 has a vertically protruding arm 63 which projects through a slot in the sleeve wall.
  • An adjusting screw 64 is rotatably but axially immovably mounted in the arm 63, the threaded portion of which projects through a threaded hole in the arm 62. Therefore, the distance of the end 65 of the plunger 61 protruding from the sleeve 60 from the valve stem can be changed by turning the adjusting screw.
  • the free end of the plunger 61 is pressed by a compression spring 37b acting on the valve stem against the control member in the form of a cam plate 67, which is fastened, for example, to a free end of the master shaft 8a and follows its rotary movements.
  • a compression spring 37b acting on the valve stem against the control member in the form of a cam plate 67 which is fastened, for example, to a free end of the master shaft 8a and follows its rotary movements.
  • the same as that described with reference to FIG. 3 Embodiment exerted a greater or lesser force on the pressure roller 25.
  • the cam plate 67 is fastened on the master shaft 8a by means of a fastening screw 68 and then always assumes the same rotational angle position relative to this and thus also to the crankshaft to be straightened.
  • cams 67 are used for straightening in the secondary and main planes, which are also precisely adjusted by rotating the shaft 8a in accordance with the directions in which the straightening forces are to be made effective.
  • the size of the maximum straightening force can be changed by turning the adjusting screws 64.
  • the straightening forces to be used would be very large.
  • substantially smaller straightening forces of, for example, up to 50 kN are sufficient if these are exerted along a selected section 69, which is indicated schematically in FIG. 6 by a widened line, and if this selected section 69 is rolled several times with the pressure roller 25.
  • the section 69 extends along the circumference of the main bearing journal 2 by approximately equal parts on both sides of the imaginary line over an arc of, for example, 10 ° to 20 ° in total.
  • the pressure acting on the cylinder 28 is expediently gradually increased to a maximum value before the pressure roller 25 hits the selected section 69, then is held at this maximum value along section 69 and finally gradually reduced after leaving section 69.
  • this increase and decrease in pressure can be predetermined by appropriate programs become.
  • this control takes place in that the circumference thereof is provided with an approximately circular section 70, a rising section 71, a further circular section 72 and a falling section 73, section 72 being that section of the main bearing journal 2 corresponds to, along which the pressure roller 25 exerts the straightening force required for the straightening operation. If it is desired with this type of control to reduce the time required for one revolution of the crankshaft to be machined, only the engine 13 needs to be set to a higher speed level whenever the pressure roller 25 is not on the selected section 69.
  • the straightening operation can also be carried out by subjecting the master shafts 8a, b and the crankshaft to be straightened to a reciprocating oscillating movement in such a way that the pressure rollers 25 always only overflow the preselected sections 69 and narrow neighboring sections.
  • the pressure acting on the pressure rollers 25 in the adjacent areas is expediently gradually increased or decreased.
  • the data processing system 57 or the cam disks 67 can optionally be used.
  • a reversing motor with a corresponding control is expediently used as the motor 13.
  • Another important parameter when straightening by cold rolling is the number of rollovers of the selected sections 69. Because during rollover, i.e. when the pressure rollers 25 act on the selected sections 69, flow can be prevented in the direction of the bottoms of the throats 6, which can only be compensated for by repeated rolling over, the pressure rollers are expediently guided at least five, preferably at least ten times over the selected section 69.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Forging (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Shafts, Cranks, Connecting Bars, And Related Bearings (AREA)

Claims (12)

  1. Procédé de laminage fixe et ensuite dressage d'un vilebrequin (1) monté tournant autour de son axe théorique qui présente un certain nombre de tourillons (2), de bras (5) et de manetons (4a à 4d) placés entre ces tourillons et de gorges (6a à 6d) faisant le tour des tourillons et des manetons faites aux endroits de raccordement de ceux-ci aux bras, le laminage fixe et le dressage étant faits par laminage à froid des parois des gorges au moyen d'outils (24, 25) pouvant être placés dans les gorges et mobiles perpendiculairement à l'axe théorique (3) et le vilebrequin étant, après mesure de son écart de coaxialité obtenu lors du laminage fixe relativement à l'axe théorique, dressé par exercice d'une pression au moyen des outils sur des parties choisies à l'avance (69) des parois des gorges, caractérisé par le fait que le laminage fixe est fait avant le dressage dans la zone de tous les tourillons et manetons (2, 4a à 4d), les écarts de coaxialité du vilebrequin (1) sont mesurés pour chacun des tourillons (2) et le dressage est fait sur ceux-ci de façon qu'après celui-ci, les écarts résiduels de coaxialité soient pour tous les tourillons (2) à l'intérieur de zones de tolérances fixées.
  2. Procédé selon la revendication 1, caractérisé par le fait que le laminage à froid est fait avec au moins un galet de pression (25), pendant le laminage à froid est produit un mouvement de rotation relatif entre la pièce (1) et le galet de pression (25) autour de l'axe (3) et une force produisant le dressage est exercée sur le galet de pression (25) au moins pendant tout le temps où celui-ci franchit la partie choisie à l'avance (69) de la paroi de la gorge.
  3. Procédé selon la revendication 2, caractérisé par le fait que la pièce (1) ou le galet de pression (25) est soumis à un mouvement oscillant de va-et-vient.
  4. Procédé selon la revendication 2, caractérisé par le fait que la pièce (1) ou le galet de pression (25) est soumis à un mouvement de rotation continu.
  5. Procédé selon l'une des revendications 3 et 4, caractérisé par le fait que la force exercée sur le galet de pression (25) est, avant que celui-ci accoste la partie choisie à l'avance, augmentée progressivement jusqu'à une valeur maximale, puis maintenue à cette valeur maximale et enfin, avant que celui-ci quitte cette partie (69), diminuée progressivement.
  6. Procédé selon les revendications 4 et 5, caractérisé par le fait que la vitesse angulaire du mouvement de rotation est augmentée pendant les périodes où le galet de pression (25) est en dehors de la partie choisie à l'avance (69).
  7. Procédé selon au moins une des revendications 1 à 6 de dressage de vilebrequins ayant un grand nombre de tourillons et de manetons, les axes des manetons étant tous dans un même plan principal contenant aussi l'axe théorique (3), caractérisé par le fait que le vilebrequin est dressé d'abord dans son plan secondaire et seulement ensuite dans son plan principal, le plan secondaire étant perpendiculaire au plan principal et contenant aussi l'axe théorique (3).
  8. Procédé selon au moins une des revendications 1 à 6 de dressage de vilebrequins ayant un grand nombre de tourillons et de manetons, les axes des manetons n'étant pas tous dans un même plan contenant l'axe théorique (3) et un ou deux manetons étant voisins de chaque tourillon, caractérisé par le fait que le vilebrequin est dressé d'abord dans ses plans secondaires et seulement ensuite dans ses plans principaux, pour chaque tourillon (2) étant défini comme plan principal le plan qui contient soit l'axe théorique (3) et l'axe de l'unique maneton voisin (4), soit l'axe théorique (2) et la bissectrice des deux plans qui passent chacun par l'axe d'un maneton (4) voisin et par l'axe théorique (3), le plan secondaire étant, pour chaque tourillon (2), perpendiculaire à un plan principal.
  9. Procédé selon au moins une des revendications 1 à 8, caractérisé par le fait que le dressage est fait par laminage à froid simultané des parois des gorges (6) de plusieurs tourillons (2) ou de tous les tourillons.
  10. Procédé selon au moins une des revendications 1 à 9, caractérisé par le fait que le dressage est fait par étapes successives, le vilebrequin (1 est remesuré après chaque étape et l'étape suivante est exécutée avec des paramètres de dressage modifiés corrigés en considération des étapes précédentes.
  11. Appareil pour la mise en oeuvre du procédé selon l'une des revendications 1 à 10, comportant des dispositifs de fixation du genre pince portés par deux arbres maîtres (8a, 8b) qui présentent chacun deux mâchoires articulées l'une à l'autre (18, 21 ou 19, 22) pour le serrage d'un tourillon ou maneton associé (2, 4) d'un vilebrequin (1), une mâchoire (18, 19) étant pourvue d'au moins un galet d'appui (23) et l'autre mâchoire (21, 22) pourvue d'au moins un galet de pression (25) destiné à être placé dans une gorge (6) et, lors de l'utilisation de l'appareil, le nombre de tourillons et de manetons (2, 4) du vilebrequin (1) correspondant au nombre de dispositifs de fixation, et comportant des dipositifs de commande des dispositifs de fixation pour la commande de la force de serrage des mâchoires (18, 21 ou 19, 22), à au moins un des dispositifs de fixation affectés aux tourillons (2) étant adjoint un dispositif de commande comportant un organe de mesure (49) pour la détermination des écarts de coaxialité dans la zone du tourillon (2) correspondant et un organe de réglage (37), cet organe de réglage (37) permettant de régler les forces exercées par les galets de pression (25) sur les tourillons (2) correspondants, en fonction de la position angulaire actuelle et des écarts de coaxialité déterminés, a des valeurs déterminées pour le dressage du tourillon (2) telles que les écarts de coaxialité restant après le dressage soient pour ce ou ces tourillons (2) à l'intérieur de zones de tolérances fixées, caractérisé par le fait qu'à chaque dispositif de fixation des tourillons (2) est adjoint un dispositif de commande pré sentant un tel organe de mesure (49) et un tel organe de réglage (37), les organes de réglage (37) permettant de régler les forces exercées par les galets de pression (25) à des valeurs déterminées pour le dressage des tourillons (2) telles que les écarts de coaxialité restant après le dressage soient pour tous les tourillons (2) à l'intérieur de zones de tolérances fixées.
  12. Appareil selon la revendication 11, caractérisé par le fait qu'il présente au moins un organe indicateur (54) relié à tous les dispositifs de commande et indiquant la position angulaire actuelle de rotation du vilebrequin (1).
EP88100107A 1987-01-17 1988-01-07 Procédé et appareil de dressage d'une pièce Expired - Lifetime EP0275876B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19873701223 DE3701223A1 (de) 1987-01-17 1987-01-17 Verfahren und vorrichtung zum richten eines werkstuecks
DE3701223 1987-01-17

Publications (3)

Publication Number Publication Date
EP0275876A2 EP0275876A2 (fr) 1988-07-27
EP0275876A3 EP0275876A3 (en) 1990-01-24
EP0275876B1 true EP0275876B1 (fr) 1995-04-05

Family

ID=6318985

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88100107A Expired - Lifetime EP0275876B1 (fr) 1987-01-17 1988-01-07 Procédé et appareil de dressage d'une pièce

Country Status (5)

Country Link
US (1) US4860566A (fr)
EP (1) EP0275876B1 (fr)
JP (1) JPS63212015A (fr)
KR (1) KR880008843A (fr)
DE (2) DE3701223A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10202564A1 (de) * 2002-01-24 2003-08-07 Hegenscheidt Mfd Gmbh & Co Kg Verfahren zum Fest- und Richtwalzen von Kurbelwellen

Families Citing this family (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5235838A (en) * 1987-07-13 1993-08-17 W. Hegenscheidt Gesellschaft Mbh Method and apparatus for truing or straightening out of true work pieces
DE3789961D1 (de) * 1987-07-13 1994-07-07 Hegenscheidt Gmbh Wilhelm Verfahren und Einrichtung zum Richten von Schlag aufweisenden Werkstücken.
DE10052753A1 (de) 2000-10-25 2002-05-08 Hegenscheidt Mfd Gmbh & Co Kg Gerät zum Festwalzen von Kurbelwellen
WO2002042018A1 (fr) * 2000-11-22 2002-05-30 Ingersoll Cm Systems, Inc. Appareil et procede de roulage de pieces
US6408663B1 (en) 2001-02-23 2002-06-25 Short Block Technologies, Inc. Method and apparatus for truing crankshafts
DE10308124B3 (de) * 2003-02-26 2004-09-23 Hegenscheidt-Mfd Gmbh & Co. Kg Verfahren zum Festwalzen von Übergängen zwischen Lagerzapfen und Wangen von Kurbelwellen
CN1314513C (zh) * 2003-12-11 2007-05-09 东风汽车有限公司 一种曲轴滚压强化工艺
US7188497B2 (en) * 2005-04-07 2007-03-13 International Engine Intellectual Property Company, Llc Method for straightening an eccentric shaft
JP5472051B2 (ja) * 2010-11-17 2014-04-16 三菱自動車工業株式会社 フィレットローリング加工装置及びフィレットローリング装置の異常判定方法
DE102010056616A1 (de) 2010-12-23 2012-06-28 Hegenscheidt-Mfd Gmbh & Co. Kg Verfahren zum Richtwalzen von Kurbelwellen
CN102784816B (zh) * 2012-08-13 2014-07-09 杭州电子科技大学 大型柴油机曲轴安装调试方法
CN104209811B (zh) * 2014-09-09 2016-11-16 南车戚墅堰机车有限公司 曲轴轴向加工余量自动分配方法
CN107030143A (zh) * 2017-05-27 2017-08-11 天润曲轴股份有限公司 曲轴完全残余压应力校直装置和工艺
FR3090424B1 (fr) * 2018-12-19 2021-04-09 Renault Sas Procédé de redressage d'un arbre par application d'un effort variable radial d'écrouissage sur l'arbre en rotation
JP7137220B2 (ja) * 2019-06-19 2022-09-14 上越工業株式会社 異形長尺ワークの曲り矯正装置及び直線状長尺ワークの製造方法

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1070955B (de) * 1959-12-10 Wilhelm Hegenscheidt Kommanditgesellschaft Erkelenz (RhId) Vorrichtung zum gleich zeitigen Festwalzen der Hohlkehlen und der Laufflache an den Kurbelzapfen und Lagerstellen λ on Kurbelwellen
GB957712A (en) * 1959-06-17 1964-05-13 Birmingham Small Arms Co Ltd Machines for rolling the bearing fillets of crankshafts
GB957711A (en) * 1959-06-17 1964-05-13 Birmingham Small Arms Co Ltd Machines for rolling the bearing fillets of crankshafts
GB957805A (en) * 1961-07-12 1964-05-13 Birmingham Small Arms Co Ltd Improvements in or relating to the working of metals
GB1004962A (en) * 1963-07-22 1965-09-22 Motor Industry Res Ass Method of and apparatus for treating crankshafts
DE3037688C2 (de) * 1980-10-06 1982-12-02 Wilhelm Hegenscheidt, Gmbh, 5140 Erkelenz Verfahren zum Festwalzen von Kurbelwellen
DE3108717C2 (de) * 1981-03-07 1984-10-04 Wilhelm Hegenscheidt Gmbh, 5140 Erkelenz Kurbelwellenfest- bzw. Glattwalzmaschine
DE3108780C2 (de) * 1981-03-07 1984-10-25 Wilhelm Hegenscheidt Gmbh, 5140 Erkelenz Kurbelwellenfest- bzw. Glattwalzmaschine
US4416130A (en) * 1981-03-20 1983-11-22 Industrial Metal Products Corporation Pulsing impact straightener
DE3224268C1 (de) * 1982-06-28 1984-01-05 Wilhelm Hegenscheidt Gmbh, 5140 Erkelenz Maschine fuer die Bearbeitung von Kurbelwellen
JPS59101228A (ja) * 1982-11-30 1984-06-11 Hino Motors Ltd クランクシヤフトの曲り矯正法と装置
DE3333603A1 (de) * 1983-09-16 1985-03-28 Toyoda Koki K.K., Kariya, Aichi Kurbelzapfen-walzeinrichtung
JPH101228A (ja) * 1996-06-17 1998-01-06 Ricoh Co Ltd 紙葉類積載装置

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10202564A1 (de) * 2002-01-24 2003-08-07 Hegenscheidt Mfd Gmbh & Co Kg Verfahren zum Fest- und Richtwalzen von Kurbelwellen
DE10202564B4 (de) * 2002-01-24 2005-08-11 Hegenscheidt-Mfd Gmbh & Co. Kg Verfahren zum Fest- und Richtwalzen einer Kurbelwelle für einen Verbrennungsmotor

Also Published As

Publication number Publication date
DE3701223A1 (de) 1988-07-28
KR880008843A (ko) 1988-09-13
US4860566A (en) 1989-08-29
DE3853485D1 (de) 1995-05-11
JPS63212015A (ja) 1988-09-05
EP0275876A3 (en) 1990-01-24
EP0275876A2 (fr) 1988-07-27

Similar Documents

Publication Publication Date Title
EP0275876B1 (fr) Procédé et appareil de dressage d'une pièce
DE3519382C2 (de) Mehrwalzenbiegevorrichtung
EP0299111B1 (fr) Procédé et dispositif de redressage de pièces présentant des parties excentrées
DE3037688C2 (de) Verfahren zum Festwalzen von Kurbelwellen
EP1779972B1 (fr) Procédé et dispositif de galetage de vilbrequins
DE4036283C2 (de) Verfahren und Vorrichtung zur Steuerung von Zylinderschleifmaschinen
DE2346796A1 (de) Automatisches richtverfahren und richtmaschine dafuer mit mehreren richtstellen
EP0394531B1 (fr) Machine à sertir
DE10024990C5 (de) Verfahren und Vorrichtung zum induktiven Härten von Kurbelwellen
EP0683012B1 (fr) Laminoir à métaux muni d'ensembles opposés d'unités à machines pour l'usinage d'une pièce centrée et procédé de laminage des gorges circulaires d'une pièce
EP3744436A1 (fr) Presse à redresser et procédé de redressage par cintrage des pièces allongées
DE3211489A1 (de) Verfahren und vorrichtung zur korrektur von sollform-abweichungen platisch verformbarer gegenstaende
DE19753426A1 (de) Vorrichtung und Verfahren zum Korrigieren von Rundlauffehlern
DE3011454A1 (de) Verfahren fuer die fertigbearbeitung von nockenwellen
DE2346797A1 (de) Automatisches richtverfahren und richtpresse dafuer mit einer richtstelle
EP0438205B1 (fr) Procédé et dispositif de redressage des bouts de pièces allongés
DE60115451T2 (de) Verfahren und formvorrichtung zum verformen eines hohlen werkstücks
DE3911930C2 (fr)
DE1070955B (de) Vorrichtung zum gleich zeitigen Festwalzen der Hohlkehlen und der Laufflache an den Kurbelzapfen und Lagerstellen λ on Kurbelwellen
EP2095892A1 (fr) Machine à laminer des profilés
EP0433819A2 (fr) Détermination de la caractéristique de cédage d'une cage ébaucheuse et finisseuse
EP1345715B1 (fr) Presse a forger dotee d'un dispositif de reglage situe cote matrice
EP1347849A1 (fr) Procede de fluotournage et dispositif de fluotournage
DE2456782A1 (de) Verfahren und vorrichtung zum richten von profilstahl
DE19938966C1 (de) Verfahren und Vorrichtung zum Herstellen eines bandförmigen Vormaterials aus Metall, insbesondere eines solchen Vormaterials welches in regelmäßig wiederkehrenden Abschnitten profiliert ist, und die Verwendung einer Vorrichtung dafür

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): DE ES FR GB IT NL SE

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

Designated state(s): DE ES FR GB IT NL SE

17P Request for examination filed

Effective date: 19900626

17Q First examination report despatched

Effective date: 19920225

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE ES FR GB IT NL SE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 19950405

Ref country code: ES

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19950405

Ref country code: FR

Effective date: 19950405

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 19950405

Ref country code: GB

Effective date: 19950405

REF Corresponds to:

Ref document number: 3853485

Country of ref document: DE

Date of ref document: 19950511

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Effective date: 19950705

EN Fr: translation not filed
NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
GBV Gb: ep patent (uk) treated as always having been void in accordance with gb section 77(7)/1977 [no translation filed]

Effective date: 19950405

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20041209

Year of fee payment: 18

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060801