EP3753647B1 - Entraînement par impact pour un outil à déplacer linéairement, ainsi que procédé de coupe d'un composant de tôle - Google Patents

Entraînement par impact pour un outil à déplacer linéairement, ainsi que procédé de coupe d'un composant de tôle Download PDF

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Publication number
EP3753647B1
EP3753647B1 EP20172386.3A EP20172386A EP3753647B1 EP 3753647 B1 EP3753647 B1 EP 3753647B1 EP 20172386 A EP20172386 A EP 20172386A EP 3753647 B1 EP3753647 B1 EP 3753647B1
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EP
European Patent Office
Prior art keywords
rotor
impact drive
impact
linear bearing
cutting
Prior art date
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EP20172386.3A
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German (de)
English (en)
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EP3753647A2 (fr
EP3753647A3 (fr
Inventor
Frank Rabe
Georg Frost
Herr Günter Fortmeier
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Benteler Automobiltechnik GmbH
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Benteler Automobiltechnik GmbH
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Priority claimed from DE102019116968.2A external-priority patent/DE102019116968A1/de
Application filed by Benteler Automobiltechnik GmbH filed Critical Benteler Automobiltechnik GmbH
Publication of EP3753647A2 publication Critical patent/EP3753647A2/fr
Publication of EP3753647A3 publication Critical patent/EP3753647A3/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/02—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously of the tool-carrier piston type, i.e. in which the tool is connected to an impulse member
    • 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
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the tools
    • 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
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/24—Perforating, i.e. punching holes
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25D—PERCUSSIVE TOOLS
    • B25D9/00—Portable percussive tools with fluid-pressure drive, i.e. driven directly by fluids, e.g. having several percussive tool bits operated simultaneously
    • B25D9/06—Means for driving the impulse member
    • B25D9/08—Means for driving the impulse member comprising a built-in air compressor, i.e. the tool being driven by air pressure

Definitions

  • the invention relates to a shock drive for a tool that can be moved linearly and to a method for cutting a sheet metal component.
  • the non-thermal pushing, punching, punching, cutting or joining of objects from a solid can be done by driving a moving body as a mass at a high speed against an object that is stationary or approximately stationary with respect to the mass, so that the kinetic Energy of the moving mass is almost completely transferred to the object hit during the quasi-inelastic impact process.
  • the drives used for impact, forming, cutting, setting or joining tools usually accelerate a mass, for example an impact body known as a hammer, firing pin or driving piston with a hard impact surface, which also generates the kinetic impulse through the impact on the The body of the tool or the one to be driven has a hard surface object transfers.
  • the DE 10 2016 125 510 B3 discloses a method for producing an opening in a thermoformed and press-hardened metallic sheet metal component, wherein an opening with a closed or open cutting line is produced by high-speed punching at a speed of a punch of more than 6 m / s without a counterholder adapted to the contour of the punch.
  • the speed of the stamp can be generated, for example, using a magnetic pulse, using pyrotechnic means or using electromagnetic pulse technology.
  • the DE 10 2007 054 533 B3 discloses a CNC punching machine in which the drive unit is formed by an electric linear direct drive and a hydromechanical amplification stage is additionally connected between the rotor of the electric linear direct drive and the upper tool.
  • Two drive mechanisms are combined with one another, with the rotor of the electric linear direct drive acting directly on a control slide which has control edges which cooperate to form a hydraulic follow-up control with corresponding second control edges formed on a guide bore to drive the piston.
  • the US 2013/0118766 A1 discloses a pneumatically driven hammer tool in which a hammer body is mounted in a housing and repeatedly acts on a body mounted in the housing under the influence of compressed air Tool hits. To dampen vibrations, elastic elements are arranged in the housing.
  • the US 2009/0326425 A1 discloses a medical device for treating the human or animal body using pressure or shock waves.
  • a hammer body is moved back and forth pneumatically in a housing. The hammer body hits a tool. This process is repeated at very high speed so that the desired pressure or shock waves are created.
  • the US 5,119,667 A discloses a shock drive according to the preamble of claim 1 for a tool to be moved linearly.
  • a linearly movable rotor is arranged in a stator housing, which has an inner end which is arranged in the stator housing and which has a free end for coupling to a tool.
  • a gas-filled pressure chamber is arranged in the stator housing, with an excess pressure relative to the environment prevailing or being able to be generated in the pressure chamber.
  • a first linear bearing is arranged in the stator housing, in which the inner end of the rotor is linearly guided.
  • the stator housing is adjoined by a guide housing, in which a second linear bearing is arranged at an axial distance from the first linear position, and in which the free end of the rotor is linearly guided.
  • the invention is based on the object of providing a shock drive for a tool that can be moved linearly, which is as compact as possible and suitable for use in a machine tool and which has a high level of performance and power density for a periodically repeating reversing operation.
  • the shock drive according to the invention is based on the fact that a linearly movable rotor for the shock drive is arranged in a stator housing.
  • the rotor has an inner end disposed in the stator housing and a free end for a tool. This end protrudes from the shock drive or the stator housing.
  • a gas-filled pressure chamber is arranged in the stator housing. There is excess pressure in the pressure chamber compared to the surroundings. At least the excess pressure relative to the environment can be generated.
  • the pressure in the pressure chamber is such that the rotor reaches a speed of at least 6 m/s over its limited travel due to the pressure built up.
  • the rotor moves back and forth exclusively within the shock drive.
  • a first linear bearing is arranged in the stator housing for linearly guiding the inner end of the rotor.
  • the stator housing is adjoined by a guide housing in which a second linear bearing is arranged at a distance from the first linear bearing.
  • the first or inner end of the movable rotor can also be referred to as a piston, which is adjacent to the pressure chamber.
  • the second, free end is, so to speak, the piston rod or plunger and forms the coupling point to a suitable tool.
  • the invention provides that the first linear bearing is arranged in the stator housing.
  • a second linear bearing is located at a distance from the first linear bearing on a guide housing that adjoins the stator housing. In this way, both ends of the linearly movable rotor are guided during the stroke movement of the shock drive.
  • the shock drive has a quasi-built-in pneumatic energy storage.
  • the energy from this energy storage is transferred to the runner when the runner is released.
  • the rotor which was previously moved against the pressure chamber and held in the position subjected to the pressure, is accelerated from a rest or first end position into a second end position and, in the process, absorbs kinetic energy from the pressure chamber.
  • the pulse strength of the shock drive can be controlled pneumatically.
  • the pneumatic drive or the pneumatic energy storage has great performance in relation to the installation space and is also very suitable for periodically repeating reversing operation.
  • a prerequisite for that Reversing is the setting of the masses moved by the rotor to the standby state using external power.
  • the acceleration of the runner's mass occurs pneumatically during the impact.
  • the rotor Due to the built-in energy storage, it is necessary that the rotor can be locked by a retaining device in a retracted and pressurized position.
  • the retracted position corresponds to the ready position. In this standby position, the expansion of the pressure chamber is reduced by the movable rotor. If the retaining device is released, the linearly movable rotor, driven by the gas pressure, shoots towards the guide housing. When the rotor has reached its end position and can no longer be moved in the direction of the guide housing, the rotor must be returned for the next use.
  • the rotor is coupled to a reset device in order to transfer the rotor from an extended position to the starting position.
  • the shock drive requires a kink-resistant, shear- and tensile-resistant housing, which preferably delimits a cylindrical cavity for the pressure chamber.
  • a sealing body can be inserted into the cavity, which enables the cavity to be filled with a gas or a gas mixture and which prevents the gas or the gas mixture from escaping from the cavity.
  • the runner is also resistant to buckling for power transmission.
  • the guide housing has a stop buffer that the rotor touches in its end position. After releasing the retaining device, the rotor is accelerated towards the guide housing and braked by contact with the workpiece and by the stop buffer.
  • the second linear bearing is arranged adjacent coaxially to the rotor in the vicinity of the stop buffer. In order to minimize energy loss due to friction, the rotor in the shock drive must be mounted particularly smoothly. The two linear bearings effect a particularly low-friction bearing of the rotor.
  • the linear bearings can be made as bearing shells or as bearing rings made of a permanent magnetic material, a partially crystalline polymer (e.g. polyoxymethylene (POM), polyamide (PA) or polyphenylene sulfide (PPS)).
  • the components in question can also consist of a metal coated with a dry lubricant and/or carbon.
  • the linear bearing can be cooled by heat conduction to the surrounding housing components. The heat can also be transferred to the rotor or to a fluid heat carrier through heat convection.
  • the first and/or the second linear bearing are liquid or gas cooled.
  • a certain amount of cooling results from the fact that a fluid heat transfer medium is used, which can be a sliding or lubricant.
  • a suitable heat transfer medium is a liquid with sufficiently low surface tension and viscosity or a gas that expands from a gas storage and flushes through the storage.
  • the guide housing has at least one vent opening.
  • the vent opening preferably extends along the stroke path of the rotor, so that there is no braking increase in pressure over the entire length of the acceleration path.
  • the rotor is mounted with sufficient play in the linear bearings.
  • thermodynamic energy required for the impact at a speed of at least 6 meters per second is preferably stored in the difference between the fluid pressures acting on the cross-sectional area of the rotor from inside the stator housing and from outside the stator housing.
  • the retaining device for holding the rotor in a ready position may comprise a movable locking body which can be brought into engagement with a locking projection of the plunger.
  • the restraint device can also be a clutch include, which can cause a magnetic, pneumatic, hydraulic or mechanical adhesion between the rotor and the housing. The runner is released from the ready position by triggering or relaxing the restraint device.
  • a sealing body surrounding the gas volume is preferably arranged in the pressure chamber.
  • This can be a sealing bellows made of an elastomer. If no sealing bellows is inserted into the pressure chamber, at least sealants are required to seal the pressure chamber from the gap between the rotor and the stator housing. Sealing rings or sealing membranes can be used. Elastomers or metallic materials are suitable for this.
  • the pressure chamber or the pneumatic energy storage can be designed to be fillable.
  • the pressure chamber can be fed with a gas or with a gas mixture via an energy storage device arranged outside the shock drive via a compressed gas line and, if necessary, via a check valve.
  • the pressure chamber or the built-in pneumatic energy storage can be temperature controlled. Heating increases the pressure and viscosity of the gas.
  • the temperature control is preferably carried out electrically.
  • a pair of electrodes from at least one electrical energy storage device arranged outside the shock drive can emit electricity to control the temperature control.
  • the external power-operated setting of the rotor or the mass to be moved by the rotor into the standby state is preferably carried out by means of an electrically and/or a pneumatically controllable drive, preferably by means of a servo-pneumatic linear drive (pneumatic piston-cylinder device with a distance transducer).
  • the rotor is preferably held and released by means of an electrically and/or pneumatically switchable axial clutch, for example by means of an electromagnetic clutch (holding magnet) or a fluid pressure-operated clutch (centering clamp).
  • the advantage of the shock drive according to the invention is the small masses in relation to the shock energy, which develop a high dynamic or a large shock acceleration.
  • the small moving masses lead to low reaction forces on adjacent components and on the bearings involved.
  • the shock drive according to the invention has a high power density with a very compact design made of mostly cylindrical objects and a very small space requirement. It is possible to accommodate a tool, for example a hole punch, in a free end of the rotor.
  • the rotor is preferably a body with a circular cylindrical cross-sectional area over the axial length.
  • the axial length of the rotor is at least twice the outer diameter of the rotor.
  • the high energy density in the built-in pneumatic energy storage leads to a trapezoidal force-displacement characteristic.
  • An energy supply during burst operation is not necessary, but it can, if necessary, increase the acceleration process.
  • the energy content can be continuously changed via the position of the rotor in the gas-filled cavity (clamping or adjustment path) and/or the gas pressure.
  • a high energy density in the built-in pneumatic energy storage saves line or transmission losses that would arise from supplying or increasing the energy density from an external energy storage.
  • the operating or maintenance effort is low. This means that the service life of such a shock drive is long. No pyrotechnics or combustion power is used. There are no exhaust gases that need to be dissipated. Therefore, the shock drive poses no risk of fire or smoke.
  • the shock drive according to the invention does not require a large electrical voltage or current. Consequently, the shock drive does not pose any danger from electricity.
  • the risk of the rotor and bearing jamming or welding is low because both components can be used with sufficient play.
  • the gas pressure is preferably maintained by a corresponding sealing body or even by a bellows, so that the rotor can be installed within the housing with a large tolerance for play.
  • the construction of the shock drive according to the invention is possible with tried and tested components and normal components.
  • the shock drive according to the invention is particularly suitable in industrial and automation technology as a drive for presses, hammers and for operating forming tools, cutting tools, setting tools and joining tools.
  • the shock drive according to the invention has advantages over designs with helical compression springs.
  • the rectangular energy area under the force-displacement characteristic curve should be mentioned.
  • the tension path is almost directly proportional to the potential energy.
  • the clamping force to be overcome by the restoring device is almost constant, with the holding force to be generated by the retaining device corresponding to the clamping force.
  • the clamping force is pressure dependent.
  • a pressure range of 15 bar to 150 bar can correspond to a force F of 0.3 kN to 3 kN.
  • the pressure chamber can store the pressurized gas for around two years until a minimum amount of gas is refilled.
  • the so-called adiabatic cutting process based on the adiabatic effect not only depends on the kinetic energy introduced or on the depth of penetration of the linearly moved tool into the workpiece, but is essentially driven by the thermal power with which the workpiece is kinetic energy is converted into the substance-specific heat of fusion.
  • the depth with which the tool penetrates the workpiece is ideally not limited by an end stop, but should preferably be limited by natural braking, which occurs with a certain kinetic energy and, if the elasticity of the impact partners is overcome, at a sufficiently high speed tool penetrating the workpiece. Therefore, in order to achieve adiabatic cutting, the cutting punch can be driven by a force that is approximately constant over the acceleration path. It is therefore not necessary to accelerate a cutting punch with a hydraulic, pneumatic or magnetic pulse in addition to the approximately constant force in order to realize the adiabatic separation process.
  • the spring characteristic of the pneumatic energy storage that drives the rotor which does not include the origin point of the force-displacement diagram.
  • the energy transferred from the shock drive to the tool corresponds approximately to the trapezoidal or rectangular area under the characteristic curve, and is therefore greater for a given (maximum) positioning force and a given (maximum) positioning path than with a screw, plate or blade -Feather.
  • the mass to be moved and the internal friction of the shock drive can be smaller than with a steel spring, which means that the energy can be released with greater power.
  • the smaller moving mass of the shock drive according to the invention protects the components, which, in contrast to a solid spring, are not subject to shock-related softening, plastic deformation (compression) or relaxation of the spring body.
  • the pressure chamber of the shock drive according to the invention must be filled with a gas with a viscosity that is as small as possible compared to the ambient condition. Nitrogen is suitable for this. Water vapor, hydrogen and carbon dioxide have a lower viscosity than nitrogen, but the effort required to store these gases in the same state over a longer period of time is greater.
  • the minimum viscosity of nitrogen is at a temperature of T ⁇ 250 K (-23 °C).
  • the minimum viscosity is at a pressure of around 20 MPa (200 bar).
  • the shock drive according to the invention is suitable for the linear movement of a tool for the purpose of adiabatic cutting, in particular for so-called adiabatic punching.
  • high-speed shear cutting produces a smooth shear surface with open structural connections with a high surface energy
  • adiabatic piercing produces a crack-free cutting edge with a metal structure changed as a result of the melting and solidification process, which is insensitive to stress-induced crack formation and to crack growth from a hardened material environment .
  • the material environment hardened as a result of mechanical stresses or sliding resistance in the structure becomes less capable of binding for oxidizing substances and less receptive to diffusion substances due to the closed structural bonds in the solidification view, which have a lower surface energy than a fracture or shear surface. This reduces susceptibility to corrosion and hydrogen-induced brittleness.
  • the preferably cylindrical rotor almost completely fills the bores or the cavity in the stator housing and encloses the pressurized gas cushion. Due to the lower mass density, the gas cushion moves less sluggishly than a viscous liquid or an elastic solid with the same volume, but requires a sufficiently tight container.
  • the area of the rotor immersed in the bore of the stator housing is preferably designed with a smooth material and a constant diameter.
  • the linear bearing inserted into the stator housing serves as a low-friction spacer between the pressure-resistant stator housing and the outer surface of the rotor.
  • the pressure chamber is preferably sealed from the environment by a sealing body that is also very low-friction and is preferably floating between the housing parts, i.e. H. is mounted between the stator housing and the guide housing.
  • the sealing body passes over the casing of the rotor.
  • the second linear bearing serves to position the free end of the rotor and therefore preferably has less play with the rotor than the first linear bearing.
  • a shoulder is designed on the runner. This paragraph is moved along the vents. Through these openings, the rotor can also be operated from the outside to move the rotor to the ready position, i.e. H. to tension or charge the energy storage device.
  • the invention also relates to a method for cutting a sheet metal component according to claim 12.
  • the trapezoidal force-distance curve of the gas pressure spring drive ensures that the speed and heat generation remain higher during penetration and cutting than with "conventional" adiabatic cutting.
  • the process is particularly suitable for hardenable steel materials for hot forming with the following chemical analysis (all data in wt.%), remainder Fe and melting-related impurities and with Rm>1300 MPa: carbon (C) 0.19 to 0.25 silicon (Si) 0.15 to 0.30 manganese (Mn) 1.10 to 1.40 phosphorus (P) 0 to 0.025 sulfur (S) 0 to 0.015 chrome (CR) 0 to 0.35 Molybdenum a n (Mon) 0 to 0.35 titanium (Ti) 0.020 to 0.050 boron (B) 0.002 to 0.005 aluminum (Al) 0.02 to 0.06.
  • the following steel material for hot forming achieves Rm >1800 MPa and is also suitable for the process according to the invention, although here too all information is in% by weight (rest: Fe and impurities caused by melting).
  • C carbon
  • 0.3-0.4 preferred 0.32-0.38 Si silicon
  • Mn manganese
  • 0.8-1.5 P phosphorus
  • Ultra-high-strength steel also known as UHSS
  • UHSS ultra-high-strength steel
  • These include the following alloy groups: high-manganese austenitic twinning induced plasticity (TWIP) steel, Dual phase steel (for example DP1000), complex phase steel (for example CP980 or CP1180) and martensitic steel.
  • TWIP high-manganese austenitic twinning induced plasticity
  • Dual phase steel for example DP1000
  • complex phase steel for example CP980 or CP1180
  • martensitic steel The cold-formed trimmed sheet metal components have a tensile strength of at least 800 MPa, preferably at least 980 MPa, in particular at least 1180 MPa.
  • the Figure 1 shows a shock drive 1 with a stator housing 2, which is located at the top of the image plane.
  • the stator housing 2 is joined to a guide housing 3, which forms the lower half of the housing.
  • the stand housing 2 is designed to be thick-walled due to the internal pressure and the buckling resistance. It has a cylindrical, elongated cross section with a central bore in which a linearly movable rotor 4 is located.
  • the rotor 4 has an inner end 5 which is located in the upper stator housing 2. Its free lower end 6 protrudes from the bottom of the guide housing 3. It is designed to be a coupling (not shown) with a tool, in particular with a hole tool.
  • Both the stator housing 2 and the guide housing 3 are designed with circumferential flanges 7, 8 at their mutually facing ends.
  • the opposite flanges 7, 8 are fastened to one another via screw bolts 9.
  • the Figure 2 shows that four screw bolts 9 are arranged over the circumference of the flanges 7, 8 symmetrically to the longitudinal section plane. Also shows Figure 2 the cylindrical cross section of the stator housing 2.
  • the outer diameter of the two housings, i.e. H. the stator housing 2 and the guide housing 3 are identical.
  • the sealing body 10 surrounds the rotor 4 on the outside.
  • the rotor 4 therefore passes through the sealing body 10.
  • the sealing body 10 is configured annularly. It has several annular chambers which are separated by sealing lips which point towards the rotor 4.
  • a first linear bearing 11 is arranged in the stator housing 2, which surrounds the rotor 4 on the circumference.
  • a second linear bearing 12 that surrounds the slimmer, plunger-like lower end 6 of the rotor 4.
  • the diameter of the second linear bearing 12 is smaller than the diameter of the first linear bearing 11.
  • a cylindrical pressure chamber 13 Inside the stator housing 2 there is a cylindrical pressure chamber 13. On the one hand, the pressure chamber 13 borders on a floor 14 at the upper end of the stator housing 2. On the other hand, the pressure chamber 13 is limited by the inner end 5 of the rotor 4. In the pressure chamber 13 there is a gas volume which is under an excess pressure p relative to the surrounding atmosphere. The gas is in particular nitrogen or contains nitrogen.
  • a bellows-shaped sealing body 15 made of an elastomeric material is arranged in the pressure chamber 13. By moving the rotor 4 downwards, the bellows-shaped sealing body 15 is expanded by the excess pressure p. The bellows-shaped sealing body 15 can be pressurized via a channel 16 in the base 14.
  • valve 17 adjacent to the base 14, which prevents the compressed gas from escaping unintentionally.
  • the pressure within the pressure chamber 13 can be adjusted via the valve 17.
  • the Runner 4 is held in a retracted position. If the rotor 4 is extended, the rotor 4 moves downward in the image plane under the influence of the gas pressure in the pressure chamber 13.
  • the rotor 4 can be moved up to a stop buffer 18, which is at the lower end of the guide housing 3 inside of the guide housing is arranged.
  • the stop buffer 18 surrounds the slim, shaft-like area of the rotor 4 in a ring.
  • An additional or exclusive stop within the stand housing is also possible.
  • the flanges 7, 8 and the screw connection 9 are not absolutely necessary.
  • the stop buffer 18 made of an elastomeric material is also an end stop. From this position, the runner 4 must be returned for the next operation. This is done by means of a reset device 19 shown schematically, which in this case is coupled to the lower end 6 of the rotor 4. The reset device 19 moves the rotor 4 towards the pressure chamber 13, so that the rotor 4 is prestressed. In its upper end position, as in the Figure 1 is shown, a retaining device 20 intervenes, which locks the rotor 4 in this retracted position. By releasing the retaining device, the rotor 4 is released so that the impact drive 1 exerts an impact force on the workpiece.
  • the guide housing 3 has several ventilation openings 21 arranged on the circumference.
  • a total of four of these openings extend in a slot shape in the longitudinal direction of the guide housing 3. They are arranged evenly over the circumference of the guide housing 3 symmetrically to the longitudinal section plane.
  • the exemplary embodiment of the Figure 3 differs from that of Figure 1 only because there is no bellows-shaped sealing body 15 in the pressure chamber 13. In this exemplary embodiment, only the sealing body 10 arranged in the middle area is used. Due to the otherwise identical features to the exemplary embodiment Figure 1 Reference is made to the description there regarding how it works.
  • the Figure 4 shows a micrograph through a hot-formed sheet metal component 22 with a tensile strength Rm >1300 MPa and with an opening that is made by a linearly moved tool 23 in the form of a cutting punch.
  • the opening is made by high-speed punching in the direction of impact P1 with an impact speed of at least 6 m/s.
  • the following figures show an upper corner area 24 of the said opening and a lower corner area 25, enlarged again 10 times.
  • the two micrographs show, based on the lighter edge zones, that the sheet metal component 22 is provided with a coating on both sides (AlSi). Furthermore, the structure of the sheet metal component 22 is according to the micrograph in Figure 5 predominantly martensitic.
  • the cutting surface 26 in the image plane on the right is smooth.
  • a martensite assembly line 27 can be seen.
  • the formed martensite structure can be seen within the martensite assembly line 27.
  • the martensite needles are curved in an arc shape corresponding to the cutting direction of the cutting punch.
  • the martensite conveyor belt 27 is covered by a smooth layer 28.
  • the thickness of this smooth layer 28 increases towards the lower corner area 25.
  • This smooth layer has an austenitic and/or ferritic structure.
  • the smooth layer 28 has a smaller thickness than the martensite flow belt 27.
  • the thickness of the smooth layer 28 is in a range of 0.1 to 5 ⁇ m and that of the martensite flow layer 27 is in a range of 10 to 100
  • a similar micrograph with an analogous cut surface also results, for example, on cold-formed sheet metal components made from a martensitic steel alloy with a tensile strength of at least 1000 MPa.

Claims (12)

  1. Entraînement par à-coups (1) pour un outil (23) à déplacer linéairement, présentant les caractéristiques suivantes :
    a) un rotor (4) mobile linéairement est agencé dans un boîtier de stator (2), le rotor présentant une extrémité intérieure (5) qui est agencée dans le boîtier de stator (2) et présentant une extrémité libre (6) pour le couplage à un outil (23) ;
    b) une chambre de pression (13) remplie de gaz est agencée dans le boîtier de stator (2), chambre dans laquelle une surpression (p) par rapport à l'environnement règne ou peut être générée (13) ;
    c) un premier palier linéaire (11) est agencé dans le boîtier du stator (2), palier linéaire dans lequel l'extrémité intérieure (5) du rotor (4) est guidée de manière linéaire ;
    d) un boîtier de guidage (3) se raccorde au boîtier de stator (2), boîtier de guidage dans lequel un second palier linéaire (12) est agencé à une distance axiale du premier palier linéaire (11), dans lequel l'extrémité libre (6) est guidée de manière linéaire,
    d') dans lequel le rotor (4) est couplé à un dispositif de rappel (19) pour faire passer le rotor (4) d'une position déployée à une position initiale,
    caractérisé en ce que
    e) la surpression (p) régnant ou pouvant être générée dans la chambre de pression (13) est dimensionnée de sorte que le rotor (4) accélère sur une course de réglage à une vitesse d'impact d'au moins 6 m/s,
    f) dans lequel le rotor (4) peut être bloqué dans une position rétractée au moyen d'un dispositif de retenue (20).
  2. Entraînement par à-coups (1) selon la revendication 1, caractérisé en ce que le rotor (4) touche dans sa position finale un tampon de butée (18) qui est agencé dans le boîtier de guidage (3).
  3. Entraînement par à-coups (1) selon la revendication 1 ou 2, caractérisé en ce que le second palier linéaire (11) est agencé de manière adjacente et coaxiale au rotor, à proximité du tampon de butée (18).
  4. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le premier et/ou le second palier linéaire (11, 12) sont refroidis par un liquide ou un gaz, le liquide ou le gaz utilisé pour le refroidissement traversant le palier linéaire (11, 12).
  5. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 4, caractérisé en ce que le boîtier de guidage (3) présente au moins un orifice d'aération (21).
  6. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le dispositif de retenue (20) comprend au moins un corps de blocage monté mobile.
  7. Entraînement par à-coups (1) selon la revendication 1, caractérisé en ce que le dispositif de retenue (20) pour retenir le rotor (4) présente un embrayage qui peut être actionné au moyen d'une force magnétique, pneumatique, hydraulique ou mécanique.
  8. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'un corps d'étanchéité (15) entourant le volume de gaz est agencé dans la chambre de pression (13).
  9. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la chambre de pression (13) peut être tempérée afin d'influencer l'état thermique du gaz.
  10. Entraînement par à-coups (1) selon la revendication 9, caractérisé en ce que la thermorégulation peut être commandée électriquement par la chambre de pression (4).
  11. Entraînement par à-coups (1) selon l'une quelconque des revendications 1 à 11, caractérisé en ce qu'une extrémité libre (6) d'un rotor (4) mobile linéairement est couplée à un outil pour créer une ouverture dans une pièce de tôle métallique ayant une résistance à la traction Rm > 800 MPa.
  12. Procédé de découpe d'une pièce en tôle (22) avec une résistance à la traction Rm > 800 MPa en acier au manganèse-bore durcissable, avec les caractéristiques objectives selon la revendication 1 et avec un poinçon de découpe, dans lequel le poinçon de découpe heurte la pièce en tôle (22) avec une vitesse d'impact d'au moins 6 m/s, dans lequel le poinçon de coupe est complètement freiné par le composant en tôle lui-même et l'énergie d'impact est complètement convertie en chaleur, de sorte qu'une surface de coupe (26) présente une couche lisse (28) d'austénite et/ou de ferrite d'une épaisseur de 0,1 - 5 µm et, facultativement, une couche (27) de martensite d'une épaisseur de 10 - 100 µm.
EP20172386.3A 2019-06-18 2020-04-30 Entraînement par impact pour un outil à déplacer linéairement, ainsi que procédé de coupe d'un composant de tôle Active EP3753647B1 (fr)

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DE102019116550 2019-06-18
DE102019116968.2A DE102019116968A1 (de) 2019-06-18 2019-06-24 Stoßantrieb für ein linear zu bewegendes Werkzeug, Blechbauteil sowie Verfahren zum Schneiden eines Blechbauteils

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EP3753647A3 EP3753647A3 (fr) 2021-03-10
EP3753647B1 true EP3753647B1 (fr) 2023-10-04

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Publication number Priority date Publication date Assignee Title
US5119667A (en) * 1991-06-21 1992-06-09 Hollis Freddy C Pneumatic hammer apparatus
DE102006062356B3 (de) * 2006-12-22 2008-04-24 Storz Medical Ag Medizinisches Gerät zur Behandlung des menschlichen oder tierischen Körpers mit mechanischen Druck- oder Stoßwellen
DE102007054533C5 (de) * 2007-11-15 2012-04-05 Hoerbiger Automatisierungstechnik Holding Gmbh CNC-Stanzmaschine
JP5082051B2 (ja) * 2011-02-05 2012-11-28 アピュアン株式会社 エアーハンマー工具、及び該エアーハンマー工具の打撃力調整方法
DE102016125510B3 (de) * 2016-12-22 2018-04-12 Benteler Automobiltechnik Gmbh Warmgeformtes metallisches Blechbauteil sowie Verfahren zur Herstellung einer Öffnung in einem solchen Blechbauteil

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ES2962875T3 (es) 2024-03-21
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