EP3277449A2 - Schmiedehammer mit elektrischem linearantrieb - Google Patents
Schmiedehammer mit elektrischem linearantriebInfo
- Publication number
- EP3277449A2 EP3277449A2 EP16712861.0A EP16712861A EP3277449A2 EP 3277449 A2 EP3277449 A2 EP 3277449A2 EP 16712861 A EP16712861 A EP 16712861A EP 3277449 A2 EP3277449 A2 EP 3277449A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- linear
- rotor
- guide
- bear
- decoupling
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005242 forging Methods 0.000 title claims abstract description 94
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Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J7/00—Hammers; Forging machines with hammers or die jaws acting by impact
- B21J7/20—Drives for hammers; Transmission means therefor
- B21J7/22—Drives for hammers; Transmission means therefor for power hammers
- B21J7/30—Drives for hammers; Transmission means therefor for power hammers operated by electro-magnets
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B1/00—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen
- B30B1/42—Presses, using a press ram, characterised by the features of the drive therefor, pressure being transmitted directly, or through simple thrust or tension members only, to the press ram or platen by magnetic means, e.g. electromagnetic
Definitions
- the underlying invention relates to a forging hammer with an electric linear drive.
- a forging hammer with linear drive is for example from the
- a hammer bear is designed as a linear rotor of a linear motor and has attached thereto magnets or secondary parts, which are taken longitudinally displaceably together with the hammer bear in a stationary formed primary part.
- the hammer bear formed as a linear runner is moved up and down by corresponding operation of the linear motor, so that forging operations can be carried out at the base of the down movement.
- an object of the present invention seen in further developing the known forging hammer, in particular to provide alternative and / or improved embodiments of a forging hammer with linear drive.
- a forging hammer which comprises an electric, in particular electro-magnetic, linear drive with a linear rotor and with this, ie the linear rotor, for the purpose of carrying out forging movements coupled bear or hammer bear.
- an electric linear drive is to be understood as meaning, in particular, an electric, in particular electromagnetically operating, linear motor in which the linear rotor is attached to a forging frame in order to carry out a linear translational movement, in particular in the longitudinal direction of the linear rotor , Stator is guided or stored.
- it may be a permanent magnet excited linear motor, in particular solenoid linear motor.
- a linear motor this can be formed, for example, as a synchronous linear motor, for example in a cylindrical design, for. B. with a cylindrical stator and a central, cylindrical through hole in which a cylindrical linear rotor is guided.
- the linear motor may be an electromagnetically operating or operable tubular linear motor.
- the linear rotor and bear are connected to one another with the interposition of a decoupling structure acting indirectly and / or directly between the linear rotor and the bear.
- the decoupling structure can be designed and set up for indirect and / or direct decoupling, in particular flexurally elastic decoupling, of linear rotors and bears, which is particularly advantageous in the case of an electromagnetic linear motor, in particular a permanent magnet-excited linear motor as described by the invention described herein.
- a decoupling structure acting on the runners and / or stator during operation mechanical load, for. B. in the form of longitudinal, transverse, torsional and / or shear vibrations can be reduced. So can in particular a safe running of the linear motor and associated reliable forging results can be achieved.
- the decoupling structure for example in the form of a two- or three-dimensionally formed connecting structure with elasto-mechanical properties, can be designed and set up such that the linear rotor is at least partially offset by relative movements of the bear during a forging movement relative to the linear rotor, in particular by elasto-mechanical Tilgerm mechanisms, can be decoupled.
- Relative movements should be understood as meaning, in particular, those movements of the bear relative to the linear runner which occur and are caused, in particular, by the primary movement and / or in connection with the primary up and down movement, or reciprocation, of the bear and / or forging Blacksmithing during the operation of the blacksmith's hammer.
- the primary movement as such can be considered as a synchronous movement of linear and bear.
- Deviating relative movements of the bear can also be referred to as secondary movements of the bear.
- the interposed, in particular flexurally elastic or elasto-mechanical, decoupling structure between linear rotor and bear can in particular ensure that linear rotors and bear are at least partially, preferably completely, decoupled from each other in view of the secondary movements occurring during operation in the bear; can be.
- a substantial, elasto-mechanical decoupling between linear motor and bear can be achieved, which less stringent requirements for the mechanical strength of the components used in the linear motor are required.
- One, in particular elasto-mechanical, decoupling or a compensation of relative movements can be achieved in particular by the decoupling structure or at least a portion of the decoupling structure bending elastic, in particular vibration and / or torsionally elastic, deformable, and for the purpose of compensation can be deformed accordingly, so that a transfer of the respective secondary movement of the bear can be at least largely avoided or attenuated on the linear rotor.
- the decoupling structure may be an elasto-mechanically acting damping structure.
- the decoupling structure may comprise different types of secondary movements, eg tilting relative to the longitudinal axis, displacements transverse to the longitudinal axis, transverse vibrations with respect to the longitudinal axis, respectively specifically designed or configured decoupling segments or decoupling regions.
- a decoupling region may include one or more tapers, cuts, beads, apertures, recesses, longitudinal and / or transverse grooves, cavities, etc.
- any secondary movements of the bear such as vibrations, displacements, deformations and / or tilting, are not transmitted, or at least essentially not, to the linear motion.
- the present invention is based in particular on the finding that in forging hammers with electric linear drive, which have no decoupling structure, in particular the said secondary movements can lead to the fact that the barrel, in particular linear barrel, of the linear rotor in FIG associated stator is adversely affected.
- flexurally elastic decoupling structure in particular in relation to the bending elasticity of the material of the bear and / or the linear rotor and / or directly to the decoupling structure of adjacent components and / or Ratio of different sections of the decoupling structure as such is to be understood as a relative measure to the effect that the decoupling structure or a portion thereof may have a specifically higher, in particular elasto-mechanical, bending elasticity than the material of the bear and / or the linear rotor and / or the components directly adjacent to the decoupling structure and / or that at least the section of the decoupling structure can have a specifically higher bending elasticity than further sections of the decoupling structure or adjacent areas.
- a relative to adjacent or adjacent components or sections targeted higher bending elasticity can be implemented or be, for example, that compared to the adjacent or adjacent components, the decoupling structure is at least partially tapered in the direction transverse, in particular perpendicular to the direction of movement of the linear rotor or has a taper.
- a corresponding taper may, for example, have a concave curvature or otherwise shaped in cross-section along the direction of movement of the linear rotor.
- a taper formed in connection with the decoupling structure can be embodied, for example, such that a diameter of the decoupling structure measured transversely to the direction of movement of the linear rotor, in particular of a section of the decoupling structure, by a factor between 0.85 to 0.97, in particular by a factor of approximately 0.95, is smaller than a correspondingly measured diameter of an adjacent or adjoining component and / or of a further section of the decoupling structure.
- a tapering portion may be present, the diameter transverse to the direction of movement of the linear rotor by a factor between 0.85 to 0.97, in particular by a factor of about 0.95 is smaller than a measured transversely to the direction of movement of the linear rotor maximum diameter of decoupling structure.
- a bending elasticity that is specifically higher than adjacent or adjacent components or sections of the decoupling structure can be achieved or be characterized in that the surface area of cross sections or cross-sectional areas of the decoupling structure is at least partially selectively varied, at least in sections, transverse to the direction of movement.
- the decoupling structure or a portion thereof may be formed in its two- or three-dimensional geometric structure such that the surface area of cross-sectional areas varies in the direction parallel to the direction of movement.
- the two- or three-dimensional structure may have one or more tapers, cuts, beads, depressions, passages, recesses, cavities, etc., which are formed such that surface areas of cross-sectional areas of the decoupling structure between a maximum and a parallel direction in a direction parallel to the direction of movement minimum value, or vary.
- a reduction of the area compared to adjacent or adjacent components or sections may for example be in the range between 0.65 to 0.95, in particular about 0.90. It should be noted at this point that a reduction of the surface area does not necessarily have to be accompanied by a reduction of the total diameter of the decoupling structure transversely to the direction of movement.
- a reduction in the cross-sectional area may be associated with an increase in the overall diameter.
- corresponding three-dimensional structures for the decoupling structure can be designed so that a comparatively low material fatigue is achieved, and thus a comparatively long service life for the decoupling structure can be achieved in operation with continued flexurally elastic loading of the decoupling structure.
- the decoupling structure may comprise at least one, in particular elasto-mechanically designed, flexurally elastic, decoupling element, which may be configured and arranged in such a way that the linear winder can make secondary movements of the beam occurring longitudinally and / or transversely to the longitudinal axis of the linear winder during a forging movement.
- the flexurally elastic decoupling element can in particular be designed in such a way that over the course of the decoupling element parallel to the direction of movement of the linear rotor the mentioned variation in diameter and / or in the surface area of the cross-sectional areas is achieved or implemented.
- the Entkoppl ungsstru ktur may be integrally formed with the linear rotor, said z. B. end of a Kol rod or piston-like
- Rod or structure can be formed. It is also possible that the decoupling structure is designed as a separate constructional element and is connected in a positive, material, and / or non-positive manner to the linear rotor and / or a piston of the same.
- decoupling elements With one or more corresponding decoupling elements, it can be achieved, for example, that longitudinal movements and / or transversely to the longitudinal movement direction of the linear rotor can be counteracted if necessary, so that, for example, at least partial oscillation decoupling of linear rotors and the like occurs nd Bear, during operation, an advantageous geometry of the air gap between the linear rotor and stator can be achieved or maintained. Furthermore, it is possible to have one or more decoupling elements, the mechanical load, in particular
- the linear rotor in the operation of the forge to reduce at least, for example, at least partially to pay off, in particular such that a BeCdigu ng of the linear rotor and possibly it or it mounted therein Permanentmag can be avoided nets.
- the forging hammer of the further comprises a first linear guide, or linear bearing, formed between the stator of the linear drive and the bear, in particular with the central axis of the linear drive, in which the linear actuator is in the longitudinal direction is guided and stored.
- the first linear guide can be, for example, a bearing, such as a rolling or sliding bearing, in particular a sliding or guide bush, by which the linear actuator is movably mounted in the axial direction, and transverse to the axial direction, in particular free of play or substantially play-free, supported.
- a stabilization of the axial travel of the linear rotor in particular a stabilization of the axial travel of the linear rotor, in particular the axial position of the linear rotor in the stator can be achieved in cooperation with the decoupling structure.
- supportive of the decoupling structure transversely to the axial direction occurring deflections that may occur during operation of the forging hammer as by secondary movements of the bear on the linear rotor, at least counteracted.
- Due to the position and running stabilization of the linear rotor can also be achieved that the geometry, shape and / or width of the air gap formed between the linear rotor and stator is stabilized during forging operation, and caused by forging variations in the air gap geometry is at least suppressed or at least largely avoided can. This leads in particular to improved drive properties of the linear drive and thus, at least indirectly, to improved forging results.
- the forging hammer further comprises on a side facing away from the bear of the linear drive a second linear guide, in which or through which the linear rotor is guided in the longitudinal direction, and in particular is supported transversely to the longitudinal direction.
- the second linear guide may for example be formed as a guide bush, bearing or the like, and may in particular be connected to or attached to a housing or a support structure and / or the stator or attached thereto.
- the second linear guide may be formed, for example, as a type, in particular closed on one side, bush or sleeve in which a corrugated responding part or section of the linear rotor during operation of the forging hammer can be performed.
- a length of the bushing or sleeve measured in the axial direction, ie, parallel to the direction of movement of the linear rotor is at least as great as 1 times the diameter of the linear rotor.
- the linear rotor is mounted on the one hand movable in the axial direction, and that the linear rotor is transverse to the axial direction, in particular free of play or largely free of play, supported or supported.
- a particularly stable running of the linear rotor can be achieved if the electric linear drive has both the first and the second linear guide.
- the linear arsonr is supported axially on either side of the stator, on the one hand in the first linear guide facing the bear and on the other hand in the second linear guide facing away from the bear.
- the linear rotors, the first and second linear guide may be formed and formed relative to each other, that over an entire linear motion cycle of the linear rotor is always guided and supported in both the first and second linear guide.
- the linear rotor, the first and second linear guide may be formed such that the bear in the mounted state facing first axial end portion of the linear rotor always in the first linear guide, and facing away from the bear in the mounted state second axial end portion are always guided in the second linear guide.
- the linear rotor and stator at least over the respective overlap region of linear and stator linearly aligned, in the case of a cylindrical linear motor concentric, ie axially aligned are arranged to each other.
- variations of the air gap are largely avoided.
- first and second linear guide By using the first and second linear guide, it is possible to implement a linear drive with a linear motor, in which case the linear rotor is moved in a central rotor space, for example a linear motor.
- a stator in the form of a through hole or through hole, a stator is guided with a hollow cylindrical geometry, wherein the first and second linear guide are arranged on opposite axial end faces or front ends of the stator, so that guide elements, such as guide bushes, the first and second linear guide axially aligned with the runner space.
- the width of the air gap measured between the linear rotor and the stator can be, for example, 2 mm.
- the first and / or second linear guide may be present or formed in or on a supporting or supporting structure for a linear motor of the electric linear drive.
- the first and / or second linear guide can be present or formed on or in a housing structure for a linear electric motor of the electric linear drive.
- Support or support structure may be, for example, components of the housing structure.
- the housing structure can, for. B. as a supporting element, for example, have a housing base on which the stator of the linear motor supported, in particular fixed and supported, can be.
- the first linear guide may be formed in or on the housing bottom, wherein the first linear guide at least partially mounted in a through hole of the housing bottom and fixed, the through hole, in particular through hole may be formed such that it is axially aligned with the rotor space is formed, and the linear rotor can be moved therein during operation in accordance with the respective linear movement.
- the first Linear Technologyu ng for example, a Gleitlagerstruktu r, z. B. u m
- the second Linear plaition On a side facing away from the first Lineartechnologyu end face, in particular on a side facing away from the housing bottom end face of the housing or the stator, the second Linear humidity tion can be formed.
- the second Linearriosu ng can one, in particular with a, for example, externally formed, Stützstruktu r provided, leadership cyl inder u mong.
- the guide cylinder may be mounted on a support plate or guides, with support ribs connecting the guide plate and the guide cylinder to the mechanical stabilizer.
- the housing may comprise a housing jacket attached to the housing bottom and / or to the lateral support walls, which is designed to surround at least the stator of the linear motor in the mounted state.
- the housing shell may include one or more with each other verbu ndene housing shell elements, each surrounding a portion of the stator of the linear motor protective.
- the housing jacket elements are preferably detachably connected to one another, for example by means of flanges formed corresponding to one another and flanges formed on mutually adjacent housing jacket elements.
- the housing shell elements can be connected to one another and to the housing bottom and / or the support walls trained cylinders, cylindrical shells or cylinder shell parts, for example, cylinder half shells include.
- a corresponding modular design of the housing offers particular advantages in terms of about to be performed maintenance.
- the housing in particular the housing bottom, on one side facing the bear comprises one or more stop buffers, which are designed such that in the event of a, in particular extraordinary, collision between the bear and the housing caused by the collision mechanical Strain for the linear motor can at least be mitigated or buffered.
- the housing as such may be mounted on a base of the forge hammer in embodiments with the linear motor mounted in and on the housing.
- the underframe may have a bear guide formed and adapted to the linear guide of the bear, which is formed on or in the subframe and / or is mechanically connected between the subframe and the housing.
- the bear guide is advantageously connected to the base frame, and the linear motor and the housing are preferably connected to the base frame in such a way that the linear motor at least largely corresponds to the mechanical connection existing over the base frame between the linear drive and the bear and bear guide is mechanically decoupled.
- interposed absorber or damping elements or structures can be provided, for example, between the undercarriage and the linear drive.
- the linear rotor at least in the connection region to the decoupling structure, and / or the decoupling structure as such may have a piston-type, in particular a rod-like, cylinder structure.
- the decoupling structure may be configured such that the flexural strength is reduced with respect to components or elements of the forge hammer that are directly adjacent or contiguous therewith, in particular by a factor less than the flexural strength of the adjacent components and / or elements.
- a ratio of the diameter of the cylindrical structure to the length of the decoupling structure formed between the linear slide and the bear is in the range between 1/5 to 1/2.
- the decoupling structure is formed between a linear rotor or an extension connected to the linear rotor and a fixing structure designed for fastening the bear to the linear rotor.
- the attachment structure can be formed, for example, as a wedge or conical segment that can be connected to the bear in a form or friction fit, in particular engaging in the bear in the axial direction.
- a comparatively robust and reliable connection between the bear and the linear rotor can be achieved by providing the decoupling structure.
- a forging hammer may be provided, which may be formed, for example, according to the embodiments described above, and which comprises one or the electric linear drive with one or the linear rotor.
- the linear rotor may comprise one of a plurality of axially arranged in a succession of permanent magnets, and extending in the axial direction extending magnet portion.
- a cylindrical extension may adjoin the magnet section in its extension at one axial end of the linear rotor, for example, or in which, for example, the decoupling structure described herein and / or the attachment structure described herein for attachment to the bear can be trained / can.
- the permanent magnets of the magnet portion may be formed in embodiments, for example, as magnetic ring disks and arranged axially aligned one behind the other.
- a cylindrical mag- can be achieved netabêt, which can be performed for example in a cylindrical rotor space of a stator with a hollow cylindrical geometry.
- the linear rotor can have a central piston rod which passes through central through-holes of the magnetic ring disks.
- the magnetic ring discs can be plugged or threaded onto a piston rod, so that the piston rod passes through the through holes and the magnetic ring disks are arranged axially aligned with each other.
- Piston rod and magnetic ring discs can be regarded as a cylindrical magnetization structure for the linear rotor, so to speak.
- the magnetic ring discs can be set in and transverse to the longitudinal direction aligned on the linear rotor or be. Accordingly, in embodiments on both sides, for example at the end, of the magnet section existing or attached fasteners, such as clamping nuts may be provided.
- the fastening elements and the piston rod may for example be designed so that permanent magnets and piston rod can be clamped together by the fasteners, for example, for the purpose of improving the mechanical stability.
- the permanent magnets may be provided and arranged in the magnet section in such a way or have a configuration according to which the permanent magnets in the axial direction are alternately radially and axially alternately magnetized alternately.
- a magnetization structure with alternately successive radial magnetization and axial magnetization has proved to be particularly advantageous with regard to use in a forging hammer, in particular using a stator with a hollow cylindrical geometry.
- Shims, in particular peelable laminations can be arranged in configurations between axially successive permanent magnets.
- Such laminations for example in the form of stainless steel laminations, can be interposed, for example, to compensate for manufacturing tolerances of the permanent magnets and / or for setting a respective magnetization structure.
- the magnet section for example comprising by intermediate laminations together on a piston rod strained permanent magnets with particular annular geometry, a suitable for forging hammers linear rotors can be implemented.
- a neodymium-iron-boron (NdFeB) material is preferably used as a material for the permanent magnets.
- NdFeB neodymium-iron-boron
- the permanent magnets may also be made of other materials, and, in particular, the permanent magnets may be formed as a sintered body.
- the linear rotor may comprise at least one guide sleeve in an area adjoining the magnet section, preferably immediately adjacent thereto.
- an outer surface of the guide sleeve forms a bearing surface, by means of which the linear rotor in the first or second linear guide can be mounted to be movable in the longitudinal direction.
- the guide sleeve can be designed so that they rest for supporting or supporting the linear rotor with an outer surface on an inner surface of the linear guide or can be slidably mounted.
- it may have one or more Gleit Resultssringe according to further embodiments.
- the outer diameter of Gleit Adjustsringe is chosen so that these in a trained as a guide bushing linear guide, for example, the second linear guide, can be slidably received.
- the guide sleeve may be formed so that only the guide sleeve is in contact with a corresponding guide surface, so that the guide sleeve can be considered in this respect as part of a linear bearing for the linear rotor.
- an abutment sleeve can be provided on an end of the magnetic section opposite the guide sleeve, which can in particular be designed to interact with a stop present on the first linear guide in order, for example, to restrict the possible freedom of movement of the linear rotor in the longitudinal direction.
- the linear rotator may be designed such that it is mounted or can be mounted on two regions spaced apart from one another in the longitudinal direction, preferably directly adjacent to longitudinal ends of the magnet section.
- an outer surface of at least the magnet portion is provided with a coating in order to protect at least the permanent magnets against external influences, such as dirt, dust, moisture, etc.
- a resin especially epoxy resin, or a material comprising a resin can be used.
- the linear drive can be designed as a cylindrical, ie tubular, linear motor.
- the linear rotor but at least the magnetic portion or the magnetized part of the linear rotor, have a cylindrical shape with preferably approximately circular cross-section.
- the stator may be formed with a cylindrical central passage.
- the linear motor can be designed as a permanent magnet excited synchronous linear motor. With corresponding forging hammers, forgings can be comparatively accurately and precisely controlled.
- a traversing or Hu bweg of the linear rotor can for example be between 700mm and 800mm, in particular at about 750mm.
- the invention proposed herein also applies to other lifting paths, in particular larger or even smaller lifting paths of the linear rotor.
- a linear motor of the linear drive paral lel to Bewegu ngsrichtu ng of the linear rotor have a mod ularen structure.
- the linear actuator may have a predetermined but variable number of permanent magnets arranged one behind the other.
- the stator can, for example, connected in parallel to the movement direction in series, each having a predetermined, but variable number of magnet coils, for example comprising one each Spu lenenesti and a corresponding Spu lenwicklu ng, have.
- the housing may, for example, have one of the several series-connected Gepurg elements. With the modular design, it is possible to adapt the linear motor flexibly according to the respective requirements and boundary conditions.
- the linear motor having a housing with a, in particular modu lar constructed one or more part housing shell, which is supported on a housing bottom or a bottom plate.
- a housing with a, in particular modu lar constructed one or more part housing shell which is supported on a housing bottom or a bottom plate.
- a housing bottom or a bottom plate For mechanical ampli ng reinforcing ngside, in particular Verstärku ngsrippen, may be present between the bottom plate and the housing shell.
- the bottom plate can have a fastening interface, by means of which the linear motor can be attached to a support frame of the linear hammer.
- the bottom plate may in particular be designed such that, for. B. on the underside, different fastening ungsterrorismstellen u can be m so that it is possible me to mount a respective linear motor to different linear hammers.
- the housing, in particular the bottom plate or the housing bottom, one or the support frame of the linear hammer can be non-positively connected. For example, provided at respective corners of the bottom plate, screw connections can be used for fastening.
- a corresponding screw connection may include in embodiments, for example, between screw elements, such as screw head and / or nut, a damping element and / or damping bearing element, for example a metal rubber bearing.
- the bottom plate or the housing bottom can be mounted and secured by means of intermediate damping or Tilgerangn on the hammer frame.
- damping elements and / or damping strips and other damping or Tilgerbaumaschine that are present between the linear motor and hammer frame, contribute to the decoupling of the linear motor from the hammer frame, so that mechanical shocks, vibrations and the like. That occur in forging operations, at least can be mitigated , so that an immediate loading of the linear motor with occurring mechanical forces can be at least reduced.
- FIG. 1 is a perspective view of a forge hammer
- FIG. 2 is a sectional view of the forge hammer
- FIG. 3 a detail of the forge hammer according to FIG. 2;
- FIG. 4 shows another detail of the forging hammer according to FIG. 2
- FIG. 5 shows an exemplary embodiment of a section of a linear rotor
- FIG. Fig. 6 is a perspective view of another embodiment of a forging hammer
- FIG. 7 is a sectional view of the forging hammer of the further embodiment.
- FIG. 1 shows a perspective view of a forging hammer 1, with a hammer frame 2 with two lateral uprights 3 for supporting a crosshead 4.
- forging hammer 1 may comprise a lower insert 5, which may be fixed by means of an insert wedge 6 in the hammer frame 2, and a receptacle 7 for a lower hammer die 8, which in the sectional view of the forge hammer 1 facing FIG. 2 can be seen.
- the forging hammer 1 further comprises a tubular solenoid linear motor 9 fastened and supported on the upper crosshead 4, in particular a solenoid permanent-magnet synchronous linear motor.
- the solenoid linear motor 9 designed as an electric linear drive comprises a stator 10 and a linear rotor 11 guided therein in the longitudinal direction (see FIG. 2).
- the linear rotor 11 is coupled to a bear 12, which in turn is guided in two bear guides 13 formed on the uprights 3, so that the bear 12 can be moved up and down by the electric linear motor 9.
- the solenoid linear motor 9 is accommodated in a housing 32.
- the housing 32 has a modular design and, in the example shown in the figures, comprises a housing bottom 33 with an attached cylindrical first housing jacket 34 fixed thereto.
- the first housing shell 34 is connected to the housing bottom 33, for example by material bonding. verbu countries, and by means of first support ribs 35, or support bracket, compared to the housing bottom 33 mechanically stiffened.
- the housing 32 furthermore comprises a cylindrical second housing shell 36, which is connected via a detachable flange connection 37 to the first housing jacket 34, in the present example, in a frictional manner.
- a further linear bearing 38 is fastened, which comprises a base plate 39 and a cylindrical guide bushing 15 fastened to the base plate 39, in particular materially.
- the guide bush 15 and base plate 39 are mechanically stiffened against one another by means of second support ribs 40 or support brackets attached thereto.
- the solenoid linear motor 9 is based on the housing bottom 33 of the housing 32 with the base of the forging hammer 1, ie the stands 3 verbu States. Specifically, the housing bottom 33 is screwed with T-shaped stator heads of the stator 3. Positioning elements and / or dampers or absorber elements can be present between the housing bottom 33 and the stator heads. The dampers or absorber elements can be designed, a Transmission of mechanical shocks and / or vibrations from the chassis to the housing 32 at least damp.
- the bear 12 carries thereon an upper hammer die 14 corresponding to the lower hammer die 8.
- the bear 12 In operation of the forging hammer 1, the bear 12 is moved up and down by corresponding drive of the linear rotor 11 by the solenoid linear motor 9, wherein at lower base points of the bear 12 respective Schmiedeoperatio- nen on a (not shown) workpiece can be performed.
- the linear rotor 11 is formed like a piston rod, and has a length measured parallel to the longitudinal axis L which is greater than the length of the stator 10 measured parallel to the longitudinal axis.
- the guide bushing 15 is arranged in alignment and in extension of the running axis or guide axis L of the solenoid linear motor 9 and designed so that the linear rotor 11 is guided in the longitudinal direction and supported transversely to the longitudinal direction.
- a support bearing 16 is present, which in the illustration of FIG. 3, which shows an enlarged detail of FIG. 2 shows, can be seen in more detail.
- the support bearing 16 is arranged in alignment with the longitudinal axis L and aligned with the upper guide bushing 15, and designed and arranged such that the linear roller 11 is guided therein in the longitudinal direction, and is supported transversely to the longitudinal direction.
- the linear rotor 11 has, at the end facing the bear 12, a piston rod extension 17, which in the retracted position of the linear rotor 11, as shown in FIG. 2 and FIG. 4, extends between the support bearing 16 and the bear 12.
- the piston rod extension 17 comprises a piston section 18, a fastening structure 19 provided at the distal end, and a decoupling structure 20 located between the piston section 18 and the fastening structure.
- the attachment structure 19 is designed in the form of a wedge or conically tapered section, and connected by means of a retaining bush 21 in a corresponding recess or a passage or blind hole of the bear 12 form-fitting, in particular frictionally engaged with the bear 12.
- the decoupling structure 20 comprises a flexurally elastic decoupling section 22 arranged between the piston extension and the fastening structure 19.
- the decoupling section 22 has a greater bending elasticity than the adjacent components and materials.
- the increased bending elasticity or reduced bending stiffness in relation to the adjacent or directly adjoining components or materials can be effected, for example, by one or more constrictions formed in the region of the decoupling structure, for example with a concave structure with respect to the longitudinal axis L, by using or according to flexural elastic material, by cuts, recesses, breakthroughs etc ..
- ratios in the range of 0.80 to 0.97, or 0.85 to 0.95, with which comparatively advantageous elasticity properties can be achieved for forging operations, are also possible.
- the guide bush 15, the support bearing 16 and the decoupling structure 20 together such that linear rotor 11 and bear 12 are decoupled with respect to relative movements of the bear 12 relative to the linear rotor 11, and the linear rotor 11 is properly guided in the stator 10.
- the decoupling structure 20, in particular the decoupling section 22 and / or decoupling section 22 and piston section 18, does not cause secondary movements of the bear 12 during a forging operation, for example in the form of tilting with respect to the longitudinal axis, displacements or oscillations transverse to the longitudinal axis or the like , or not fully transferred to the linear rotor 11.
- Support bearing 16 and guide bushing 15 with respect to the position and the run of the linear rotor 11 in the stator 10, and stabilizing a formed between the linear rotor 11 and stator 10 in the interior of the linear motor 9 air gap stabilizing, and contribute in particular that a transfer of secondary movements of the Bear 12 on the linear rotor 11 can be avoided.
- the proposed measures ie. In particular, the provision of the decoupling structure 20, the lower support bearing 16 and the upper guide bushing 15 can be achieved that the linear actuator 11 is optimally guided in the stator 10.
- FIG. 5 shows an embodiment of a portion of the linear rotor 11.
- the linear rotor 11 of FIG. 5 includes an approximately centered axially extending magnet portion 23.
- the magnet portion 23 includes a plurality of first permanent magnets 24 and second permanent magnets 25.
- the first permanent magnets 24 are the axially magnetized permanent magnets, while the second permanent magnets 25 are radially magnetized permanent magnets.
- the first permanent magnets 24, measured in the direction parallel to the longitudinal axis L, are narrower than the second permanent magnets 25.
- the permanent magnets 24, 25 are formed as annular discs, with a central through hole.
- the linear rotor 11 has a piston rod 26, which passes through the through holes of the permanent magnets 24, 25 and forms a central seat for the permanent magnets 24, 25.
- the linear rotor 11 Immediately adjacent to the magnet section 23, the linear rotor 11 has a guide sleeve 27 with a plurality of Gleit Resultssringen.
- An inner surface of the guide bush 15 can accordingly be designed as an abutment surface for the Gleitrine- insurance rings.
- the permanent magnets 24, 26, laminations and the guide sleeve 27 are fastened by means of mutually secured to the piston rod 26 or fixed clamping nuts 28, each of which abut against a stop nut 29.
- the clamping nuts 28 and stop nuts 29 and corresponding attachment points, in particular thread, the piston rod 26 and the piston rod 26 as such are designed such that proper attachment of the stop nuts 29 and clamping nuts 28, the permanent magnets 24, 25 and piston rod 26 are clamped together. In particular, in this way an improved mechanical stability, in particular of the magnet section 23, can be achieved.
- the magnet portion 23 may have a protective coating, which may for example consist of an epoxy resin or may comprise an epoxy resin. By means of a corresponding coating, in particular the permanent magnets 23, 24 of the magnet section 23 can be protected against external influences.
- the hollow cylindrical geometry stator 10 of the tubular solenoid linear motor 9 can be arranged along the longitudinal direction L and spaced apart from each other ring coils 30 (see FIG. 2).
- the toroidal coils 30 can be controlled in such a way that the magnet section 23 is moved up and down in the stator, whereby corresponding forging movements of the bear 12 are carried out.
- the stator 10 with ring coils 30 may, as for example in the embodiment of FIG. 2, housed in the modular housing 32, in particular be secured therein.
- Flange connection 37 of the housing halves can be achieved so that the components located within the housing 32 are comparatively easily accessible, for example for maintenance purposes and the like.
- An interface of the stator 10 or of the housing 32 with which the solenoid linear motor 9 is fastened to the hammer frame 2 can be designed such that the linear drive constructed as described herein is also retrofitted, in other words retrofitted, to existing forging hammers can.
- stop buffers 31 can be provided on an underside of the housing bottom.
- the housing 32, in particular the housing wall, and / or the linear bearing 38 may have corresponding air inlet and outlet elements.
- the housing 32 may be formed such that stator 10 and linear rotor 11 are substantially encapsulated, in particular mechanically encapsulated, and largely protected from external influences. In particular, in the case of partial or even complete encapsulation, it may be necessary to provide the aforementioned pressure compensation elements.
- FIG. 6 shows a perspective view of another embodiment of another forging hammer 1a.
- the further forging hammer 1.1 has a similar structure as the forging hammer 1 according to FIG. 1, wherein, unless otherwise described, designated by like reference numerals elements and components have mutually corresponding and / or corresponding functions and / or properties.
- the forging hammer 1 according to FIG. 1 includes the other
- L linear motor which is also designed as a solenoid linear motor, and will be referred to below under the name of another linear motor 9.1 reference.
- the further linear motor 9.1 which in FIG. 7 is shown in section, comprises a stator 10, which compared to the embodiment of FIG. 1 and FIG. 2 is shortened.
- the stator of the further linear motor 9.1 can be measured in the longitudinal direction, for example, to be half as long as that of the linear motor of FIG. 1 and FIG. 2.
- Correspondingly shortened in the other linear motor 9.1 and the linear rotor 11 may be formed, wherein the magnetic portion and the adjoining portions of the linear rotor 11 corresponding to the in FIG. 5 example can be configured.
- the housing 32 Due to the shortened shape of the further linear motor 9.1, which is designed as a tubular linear motor, the housing 32 comprises only one housing shell 34.
- the one housing shell 34 is similar to the embodiment of FIG.
- FIG.2 mounted on a housing bottom 33, in particular welded.
- housing shell 34 and housing bottom 33 via first support ribs 35 are supported against each other, wherein the first support ribs 35 and the housing bottom 33 z. B. can be welded together.
- linear bearing 38 attached, in particular screwed.
- the linear bearing 38 is according to the embodiment of FIG. 1 to FIG. 4 trained, and it is made to corresponding statements.
- the further linear motor 9.1 accommodated in the housing 32 is connected to the hammer frame 2 via the housing bottom 33.
- the housing bottom 33 is non-positively connected to the hammer frame 2, wherein provided in the present example at respective corners of the housing bottom 33 screw 41 are used.
- a corresponding screw connection 41 may, for example, comprise a metal rubber bearing 43 between the screw head 42. 1 and the screw nut 42. 2.
- the housing bottom 33 may be mounted and secured by means of intermediate damping or Tilgerangn 44 on support heads 45 of the hammer frame 2. This structure and this fastening manner substantially corresponds to that of the forging hammer 1 according to FIG. 1 to FIG. 4th
- the metal rubber bearings 43 and / or damping or Tilgerologicaln 44 contribute in particular to the decoupling of the linear motor 9, 9.1 from the hammer frame, so that mechanical shocks, vibrations and the like. which occur in forging operations, at least can be mitigated so that an immediate action on the linear motor 9, 9.1 with occurring mechanical forces can be at least reduced.
- linear motor 9.1 results in yet another advantage, because by the modular design of housing 32, linear rotor 11, comprising z. B. more cascaded annular permanent magnets, and also stator 10, which may include a plurality of successively wound bobbin 46 with corresponding coil windings as needed, in particular the length of the linear motor can be varied at least within certain limits and to that extent comparatively flexible adapted to respective requirements.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
- Forging (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015105172.9A DE102015105172B4 (de) | 2015-04-02 | 2015-04-02 | Schmiedehammer |
PCT/EP2016/056805 WO2016156319A2 (de) | 2015-04-02 | 2016-03-29 | Schmiedehammer mit elektrischem linearantrieb |
Publications (2)
Publication Number | Publication Date |
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EP3277449A2 true EP3277449A2 (de) | 2018-02-07 |
EP3277449B1 EP3277449B1 (de) | 2021-12-29 |
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ID=55642463
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP16712861.0A Active EP3277449B1 (de) | 2015-04-02 | 2016-03-29 | Schmiedehammer mit elektrischem linearantrieb |
Country Status (4)
Country | Link |
---|---|
US (1) | US11097334B2 (de) |
EP (1) | EP3277449B1 (de) |
DE (1) | DE102015105172B4 (de) |
WO (1) | WO2016156319A2 (de) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102015105172B4 (de) | 2015-04-02 | 2023-05-04 | Langenstein & Schemann Gmbh | Schmiedehammer |
CN106513551A (zh) * | 2017-01-03 | 2017-03-22 | 上海蒙塔萨汽车零部件有限公司 | 一种汽车零部件加工生产用的锻造装置 |
CN108188316A (zh) * | 2018-04-04 | 2018-06-22 | 安阳锻压数控设备有限公司 | 一种锻造钢球的制造设备系统及生产工艺 |
TWI826459B (zh) | 2018-07-09 | 2023-12-21 | 日商索尼半導體解決方案公司 | 比較器及攝像裝置 |
DE102019110889A1 (de) * | 2019-04-26 | 2020-10-29 | Langenstein & Schemann Gmbh | Antriebseinheit mit Linearantrieben für eine Umformmaschine und Umformmaschine mit einer solchen Antriebseinheit |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
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DE1654160U (de) | 1952-11-28 | 1953-04-16 | Fritz Hanemann | Baerschloss fuer fallhaemmer. |
DE1654160A1 (de) | 1967-02-28 | 1970-08-06 | Guenther Rochelt | Schnellspann-Wechselrahmen |
US3709083A (en) | 1971-03-18 | 1973-01-09 | N Doherty | Electrically actuated punch press |
DE2456481C3 (de) * | 1974-11-29 | 1980-07-17 | Hans Dipl.-Ing. 5609 Hueckeswagen Beche | Gegenschlaghammer |
DE2500605A1 (de) * | 1975-01-09 | 1976-07-15 | Hans Dipl Ing Beche | Prellschlag-daempfer fuer gegenschlaghaemmer mit hoher leistung |
JPS56135629A (en) * | 1980-03-26 | 1981-10-23 | Hitachi Constr Mach Co Ltd | Oil-pressure type drop hammer |
US5357779A (en) * | 1990-09-07 | 1994-10-25 | Coors Brewing Company | Can body maker with magnetic ram bearing and redraw actuator |
CN2093048U (zh) | 1990-11-24 | 1992-01-15 | 沂源县科学技术委员会 | 电磁锤 |
US6466119B1 (en) * | 1996-09-06 | 2002-10-15 | Chester Drew | Magnetic circuit |
US6313551B1 (en) | 2000-02-04 | 2001-11-06 | Nikon Corporation | Magnet array for a shaft-type linear motor |
US7378765B2 (en) * | 2004-08-09 | 2008-05-27 | Oriental Motor Co., Ltd. | Cylinder-type linear motor and moving part thereof |
JP2008043993A (ja) * | 2006-08-21 | 2008-02-28 | Murata Mach Ltd | リニアモータ搭載プレス機械 |
DE102008059607B4 (de) | 2008-11-28 | 2018-11-29 | Robert Bosch Gmbh | Vorrichtung zum Stanzen |
DE202008018169U1 (de) | 2008-12-22 | 2011-12-23 | Schuler Pressen Gmbh | Kurzhubgesenkhammer mit elektrischem Direktantrieb |
US7944096B2 (en) * | 2009-06-05 | 2011-05-17 | Hiwin Mikrosystem Corp. | Stator mechanism of linear motor |
PL65677Y1 (pl) | 2009-08-28 | 2011-11-30 | Kopex Technology Spółka Z Ograniczoną Odpowiedzialnością | Młot elektryczny |
JP5890296B2 (ja) * | 2012-11-22 | 2016-03-22 | ヤマハファインテック株式会社 | 直進移動機構 |
KR101462561B1 (ko) * | 2013-12-18 | 2014-11-17 | 아이엠씨(주) | 프레스 장치 |
DE102015105172B4 (de) | 2015-04-02 | 2023-05-04 | Langenstein & Schemann Gmbh | Schmiedehammer |
DE102015116881B4 (de) * | 2015-10-05 | 2024-01-25 | Langenstein & Schemann Gmbh | Umformmaschine, insbesondere Schmiedehammer |
-
2015
- 2015-04-02 DE DE102015105172.9A patent/DE102015105172B4/de active Active
-
2016
- 2016-03-29 US US15/563,491 patent/US11097334B2/en active Active
- 2016-03-29 WO PCT/EP2016/056805 patent/WO2016156319A2/de active Application Filing
- 2016-03-29 EP EP16712861.0A patent/EP3277449B1/de active Active
Also Published As
Publication number | Publication date |
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DE102015105172A1 (de) | 2016-10-06 |
EP3277449B1 (de) | 2021-12-29 |
DE102015105172B4 (de) | 2023-05-04 |
US20180085820A1 (en) | 2018-03-29 |
WO2016156319A2 (de) | 2016-10-06 |
WO2016156319A3 (de) | 2016-12-01 |
US11097334B2 (en) | 2021-08-24 |
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