EP2604361A1 - Tensioning wedge device for fastening tools to tool machines - Google Patents
Tensioning wedge device for fastening tools to tool machines Download PDFInfo
- Publication number
- EP2604361A1 EP2604361A1 EP11193563.1A EP11193563A EP2604361A1 EP 2604361 A1 EP2604361 A1 EP 2604361A1 EP 11193563 A EP11193563 A EP 11193563A EP 2604361 A1 EP2604361 A1 EP 2604361A1
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- European Patent Office
- Prior art keywords
- wedge
- clamping screw
- clamping
- counter
- face
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- 238000005242 forging Methods 0.000 claims description 18
- 125000006850 spacer group Chemical group 0.000 claims description 4
- 230000007704 transition Effects 0.000 claims description 3
- 230000006978 adaptation Effects 0.000 claims description 2
- 230000004323 axial length Effects 0.000 claims description 2
- 230000000295 complement effect Effects 0.000 claims description 2
- 230000006378 damage Effects 0.000 description 5
- 230000002093 peripheral effect Effects 0.000 description 4
- 241000600039 Chromis punctipinnis Species 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 238000006731 degradation reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
Images
Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
- B21J13/00—Details of machines for forging, pressing, or hammering
- B21J13/02—Dies or mountings therefor
- B21J13/03—Die mountings
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B30—PRESSES
- B30B—PRESSES IN GENERAL
- B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
- B30B15/02—Dies; Inserts therefor; Mounting thereof; Moulds
- B30B15/026—Mounting of dies, platens or press rams
Definitions
- the invention relates to a Spannkeilvarraum for attachment of tools to machine tools and in particular for attachment of dies to forging hammers or presses.
- the forging hammers may be, for example, top pressure hammers or counter hammers.
- forging presses please refer to eccentric forging presses and hydraulic open-die forging presses.
- a screw press is also a forging press.
- a clamping wedge device has a wedge and a counter wedge, which are each provided with a through hole. Through the two through holes extending through a clamping screw having a screw head and a threaded end opposite this, on which a clamping nut is screwed.
- the clamping nut has a through hole with an internal thread, which is in threaded engagement with the external thread of the clamping screw.
- Between the screw head and the wedge or the counter wedge is an outboard disc spring package.
- Spannkeilvoriquesen are for example in DE-PS 29 51 662 .
- DE-GM 18 54 268 .
- clamping wedge devices have basically proven in practice. Due to the high dynamic loads during use, for example, by reversing the mass acceleration during the placement of the dies, it is in clamping wedge devices wear parts with different service life of the wedges and built-in parts. Through various optimizations, the service lives of tensioning wedge devices have already been significantly improved in recent years. However, ever larger and more powerful machines continue to require improved tension wedge devices that must withstand ever-increasing dynamic loads over longer periods of time,
- the object of the invention is to provide a clamping wedge device for mounting tools on machine tools, in particular of dies in forging hammers or presses, in which the risk of destruction under extreme loads and relatively large dimensions is reduced.
- the field of application of the clamping wedge devices is intended by the previously realizable Spannkeilinn of about 500 mm for z.
- overpressure and counterheat hammers can be extended to 1 000 mm and more (eg up to 1500 mm), because also the production equipment to increase the work from earlier 40 to 80 kJ to today 130 to 400 kJ per stroke z. B. have increased a blacksmith's hammer.
- the clamping wedge device has, between the clamping screw head and the end face of the one of the two wedge elements facing the latter, a disc spring packet which comprises a plurality of disc spring rings and which can be compressed by a travel which is still given depending on the degree of pretensioning of the clamping screw.
- a disc spring packet which comprises a plurality of disc spring rings and which can be compressed by a travel which is still given depending on the degree of pretensioning of the clamping screw.
- Within the through hole of that wedge or counter wedge element on the end face of the plate spring assembly is present, there are a first and a second bore portion, which follow one another.
- the first bore portion opens into the end face and is designed substantially cylindrical, while the adjoining second bore portion is conically tapered, also the clamping screw has within its extending through the bore of this wedge member a substantially cylindrical, backlash executed first shaft portion and an adjoining second, tapered conical shaft section.
- the conical shaft section In the tensioned state of the clamping screw, the conical shaft section has an axial minimum distance to the conical bore section. In other words, so are the two conical sections to this minimum distance axially offset from each other, so that their conical surfaces do not lie against each other.
- the minimum distance is equal to or greater than the sum of the maximum possible travel of the plate spring package and in addition ca, 0.3 to 0.8 times the spring travel of the plate spring package.
- the clamping screw cross-section is expediently designed as an expansion screw in that it can stretch to a yield strength of between 0.2% to 0.5% of its length, depending on the properties of the material of which it is made.
- the clamping wedge device is not destroyed even under the highest loads.
- the minimum distance under load expediently to be chosen so that even elastic side deformations of the clamping screw and in particular its clamping screw shaft does not immediately lead to a contacting of the conical surfaces between clamping screw shank and through hole. It has been found in tests that, in particular for large clamping bar lengths in the range between 0.5 m to more than 1 m and in particular up to about 1.5 m on the clamping wedge device side loads act that lead to an elastic arcuate deformation.
- the clamping screw shank deforms arcuately, with the result that the clamping screw shaft moves within the through holes of the two wedge elements and move the conical surfaces closer to each other.
- this could result in a speedy destruction of the clamping wedge device by the inventive proposal to leave a predetermined manner above specified minimum distance between the conical surfaces, the risk of destruction of the clamping wedge device due contacting the conical Surfaces of through hole and clamping screw shaft are counteracted.
- the two conical walls of the conical bore section and of the conical shaft section can basically be the same or different.
- each point on the conical surface for example of the conical shaft section, has the same axial distance to the conical surface of the conical bore section.
- the cone angle of the bore portion is greater than that of the shaft portion, depending on the location of two spaced points on the two cone surface different distances, but the smallest distance should be at least equal to the minimum distance according to the invention.
- the clamping screw shaft is guided axially and without play with its first cylindrical shaft portion within the first cylindrical bore portion of the through hole. Due to the cylindrical guidance of the clamping screw shaft in the cylindrical bore section of the through hole, a centric guidance of the clamping screw in the clamping wedge device is ensured. This also reduces the risk of destruction under extreme stress on the clamping wedge device, as is particularly true in large-format and long (up to one meter in length and more) Spannkeilvorraumen.
- the size of the spring travel is determined empirically according to the length of the clamping wedge device and corresponds to the tightening torque of the clamping nut and the required spring pressure.
- the required spring pressure is determined empirically from the size of the side surface (one-sided contact surface on the machine or the die) of the clamping wedge device (clamping surface). He should be chosen so that sufficient Contact pressure on the inner wedge halves is present to press the wedge halves to generate the clamping force for the tools.
- the disc spring assembly either has a plurality of oppositely oriented or in groups in the same direction and from group to group oppositely oriented plate spring rings with a given in the flattened state inner diameter, wherein the inner diameter of the plate spring rings is greater than the outer diameter of that portion of the clamping screw shaft, which surrounds the plate spring package.
- the clamping screw shank of the clamping screw between the clamping screw head and the external thread end is free from male threads. It is advantageous in such a design that there is an outer peripheral recess (also referred to as a free cut) at the transition to the male thread end.
- an outer circumferential recess also referred to as a free cut
- the outer circumferential recess expediently has a depth which is substantially equal to the height of the external thread at the external thread end of the clamping screw shaft.
- the diameter of the clamping screw shaft in the region of the clearance or the outer circumferential recess is therefore equal to the core diameter of the external thread end. In his remaining Area between the outer peripheral recess and the clamping screw head may therefore have a larger diameter of the clamping screw shank than in the region of the outer circumferential recess.
- the clamping nut a first end face on which the clamping nut is supported on a contact surface of the wedge or the at least one counter wedge element, and a second end face with an adjoining thereto tool engagement surface for screwing the
- the clamping nut with the male thread end of the clamping screw shaft has an internally threaded bore extending through the clamping nut and that the internal thread of the clamping screw nut ends at an axial distance from the first end face of the clamping screw nut.
- the radial depth of Spannschraubenmutterbohrung is substantially equal to the internal thread height of the clamping nut, which Clamping nut can therefore be drilled accordingly at its first end face.
- the clamping screw shaft has within its cylindrical and / or conical shaft portion a slot which extends in the axial extension of the clamping screw, and that extends through the slot a through hole crossing locking pin.
- the longitudinal extension of the slot is to enable a relative displacement of the Clamping screw in the through hole chosen by the minimum distance between the two conical shaft and bore sections.
- a further advantageous embodiment of the invention can be provided that is arranged between the clamping screw head and the disc spring assembly for adaptation to the axial length of the diaphragm spring assembly used one of several, different axial thicknesses spacer rings.
- the different thickness spacer rings provide compensation for different length disc spring assemblies on the clamping screw head and the distance between this and the wedge element facing this.
- the wedge element may have two mutually adjoining, mutually inclined oblique wedge surfaces, wherein each of these wedge surfaces each abuts a counter wedge element with its counter wedge surface and the end faces of the two counter wedge elements facing away from each other, and being between the two end faces of the counter wedge elements and by the wedge element through the clamping screw extends.
- Such a clamping wedge device with two mutually inclined inclined wedge surfaces and two counter wedge elements is for example in DE-A-10 2006 042 359 described.
- the forging press or forging hammer 10 has a machine frame 12 with a press table 14.
- a press ram 16 is slidably guided in the direction of the arrow 18.
- the press table 14 and the press ram 16 are each provided with a dovetail-shaped tool receiving recess 20, 22 viewed in front view, in which conically widening projections 24, 26 of the lower half 28 and the upper half 30 of a die 32 are arranged.
- a clamping wedge device 34 On both sides of these projections 24,26 is in each case a clamping wedge device 34, which are provided for wedging the projections 24 and 26 in the respective tool receiving recesses 20 and 22 and thus for fixing the lower and upper die halves 28,30.
- the clamping wedge device 34 has a first wedge element 36 and a second counter wedge element 38, which have substantially the same outer contours and are arranged facing each other.
- Each wedge element 36, 38 has a larger-area end face 40, 42 and an oblique wedge surface 44, 46.
- the larger-area end face 40 or 42 is opposite to a rather small-sized further end face 48 and 50, respectively.
- Through each of the wedge elements 36,38 extends a through hole 52,54 which connects the respective end face 40 and 42 with the wedge surface 44 and 46 of the respective wedge element 36 and 38, respectively.
- a clamping screw 56 extends with a clamping screw head 58 at its one axial end and a clamping nut 60 at its other axial end.
- the clamping screw 56 comprises a clamping screw shank 62 which extends from the clamping screw head 58 and forms an externally threaded end 64 at its opposite end.
- a plate spring package 66 having a plurality of plate spring rings 68 which are arranged in groups in the same direction and from group to group in opposite directions or individually in opposite directions.
- Between the plate spring package 66 and the clamping screw head 58 is a spacer ring 69th
- the clamping wedge device 34 can be stretched, as is well known.
- the through hole 52 has a extending from the end face 40 of the first cylindrical bore portion 70 and an adjoining conically tapered second bore portion 72.
- the clamping screw shaft 62 has a first substantially cylindrical shaft portion 74 and an adjoining conical second shaft portion 76.
- this distance 78 is dimensioned so that it at least equal to the remaining spring travel of the plate spring package 66 (corresponding to the path by which the plate spring package 66 until complete compression itself can shorten axially) zuzuglich 0.3 times to 0.8 times, in particular 0.5 times the spring travel.
- the distance 78 should be slightly larger than this minimum distance, namely to be able to compensate for axial relative movements of the clamping screw within the through holes without the conical surfaces abutting.
- the clamping screw shaft 62 is secured (in this embodiment, the wedge member 36) by a locking pin 80 against turning the clamping screw 56 when screwing the clamping nut 60.
- the locking pin 80 extends transversely through the through-hole 52 and is received by a slot 82 of the clamping screw shaft 62.
- the counter-screw shaft 62 for preventing co-rotation in its central region may have a polygonal cross-section which is slightly larger than the thread diameter.
- the pin also has the task to simplify the installation and removal of the clamping wedge device 34.
- the axial extent of the elongated hole 82 is dimensioned so that the clamping screw 56 can move according to their loads, without the locking pin 80 sheared off or the like. is damaged.
- the clamping screw shaft 62 in the region of its transition to the threaded end 64 on an outer circumferential recess 84.
- the diameter of the clamping screw shaft 62 is reduced relative to its adjacent to the clamping screw head 58 adjacent area.
- the external thread 86 is axially spaced from the remaining part of the clamping screw 56.
- the clamping nut 60 has conventionally a through hole 88 which is provided with an internal thread 90 for screwing to the external thread 86 of the external thread end 64.
- the internal thread 90 of the clamping nut 60 does not extend to the inside first end face 92 and the outer second end face 94 of the clamping nut 60 but ends at an axial distance from these two end faces 92,94.
- the latter has an inner diameter which is equal to or greater than the outer diameter of the external thread 86 of the externally threaded end 64 Fig. 2 can be seen on the inner peripheral recesses 96,98.
Abstract
Description
Die Erfindung betrifft eine Spannkeilvarrichtung zur Befestigung von Werkzeugen an Werkzeugmaschinen und insbesondere zur Befestigung von Gesenken an Schmiedehämmern oder -pressen. Dabei kann es sich bei den Schmiedehämmern beispielsweise um Oberdruck- oder Gegenschlaghämmer handeln, Als Beispiele fur Schmiedepressen sei hier auf Exzenterschmiedepressen und hydraulische Freiformschmiedepressen verwiesen. Ferner handelt es sich auch bei einer Spindelpresse um eine Schmiedepresse.The invention relates to a Spannkeilvarrichtung for attachment of tools to machine tools and in particular for attachment of dies to forging hammers or presses. The forging hammers may be, for example, top pressure hammers or counter hammers. For examples of forging presses, please refer to eccentric forging presses and hydraulic open-die forging presses. Furthermore, a screw press is also a forging press.
Es ist bekannt, die beiden Hälften von Gesenken mittels Spannkeilvorrichtungen an Pressenstößel und -tisch eines Schmiedehammers bzw, einer Schmiedepresse zu befestigen. Eine Spannkeilvorrichtung weist einen Keil sowie einen Gegenkeil auf, die jeweils mit einer Durchgangsbohrung versehen sind. Durch die beiden Durchgangsbohrungen hindurch erstreckt sich eine Spannschraube, die einen Schraubenkopf und ein diesem gegenüberliegendes Gewindeende aufweist, auf das eine Spannschraubenmutter aufschraubbar ist. Die Spannschraubenmutter weist eine Durchgangsbohrung mit einem Innengewinde auf, das in Gewindeeingriff mit dem Außengewinde der Spannschraube steht. Zwischen dem Schraubenkopf und dem Keil bzw. dem Gegenkeil befindet sich ein außenliegendes Tellerfederpaket. Während sich der Spannschraubenkopf über das Tellerfederpaket an dem Keil abstützt, stützt sich dementsprechend die Spannschraubenmutter an dem Gegenkeil ab, und zwar jeweils an einander abgewandten Stirnflächen von Keil und Gegenkeil, so dass sich durch Festziehen der Spannschraubenmutter der Keil und der Gegenkeil entlang einer Anlageebene gegeneinander verschieben lassen. Dadurch verändert sich die Breite der Spannkeilvarrichtung, d.h. der Abstand der außenliegenden Seitenflächen beider Keile. Auf diese Weise kann dann ein Werkzeug in einer Werkzeugaufnahme verkeilt und damit gehalten werden.It is known to attach the two halves of dies by means of clamping wedge devices to the press ram and table of a forging hammer or a forging press. A clamping wedge device has a wedge and a counter wedge, which are each provided with a through hole. Through the two through holes extending through a clamping screw having a screw head and a threaded end opposite this, on which a clamping nut is screwed. The clamping nut has a through hole with an internal thread, which is in threaded engagement with the external thread of the clamping screw. Between the screw head and the wedge or the counter wedge is an outboard disc spring package. While the clamping screw head is supported by the plate spring assembly on the wedge, accordingly, the clamping nut is supported on the counterwedge, in each case on opposite faces of wedge and counterwedge, so that by tightening the clamping nut the wedge and the counterwedge along a bearing plane against each other let move. As a result, the width of Spannkeilvarrichtung, ie the distance of the outer side surfaces of both wedges changed. In this way, a tool can then be wedged in a tool holder and thus held.
Spannkeilvorrichtungen sind beispielsweise in
Die bekannten Spannkeilvorrichtungen haben sich in der Praxis grundsätzlich bewährt. Aufgrund der hohen dynamischen Belastungen während des Einsatzes, beispielsweise durch die Umkehrung der Massenbeschleunigung während des Aufsetzens der Gesenke, handelt es sich bei Spannkeilvorrichtungen um Verschleißteile mit unterschiedlichen Standzeiten der Keile und Einbauteile. Durch diverse Optimierungen konnten die Standzeiten von Spannkeilvorrichtungen in den letzten Jahren bereits erheblich verbessert werden. Immer größere und leistungsstärkere Maschinen jedoch erfordern weiterhin verbesserte Spannkeilvorrichtungen, die den immer höheren dynamischen Belastungen uber immer längere Zeiträume standhalten müssen,The known clamping wedge devices have basically proven in practice. Due to the high dynamic loads during use, for example, by reversing the mass acceleration during the placement of the dies, it is in clamping wedge devices wear parts with different service life of the wedges and built-in parts. Through various optimizations, the service lives of tensioning wedge devices have already been significantly improved in recent years. However, ever larger and more powerful machines continue to require improved tension wedge devices that must withstand ever-increasing dynamic loads over longer periods of time,
Aufgabe der Erfindung ist es, eine Spannkeilvorrichtung zur Befestigung von Werkzeugen an Werkzeugmaschinen, insbesondere von Gesenken in Schmiedehämmern oder -pressen zu schaffen, bei der die Gefahr einer Zerstörung bei extremen Belastungen und relativ großen Abmessungen reduziert ist. Der Einsatzbereich der Spannkeilvorrichtungen soll dabei von den bisher realisierbaren Spannkeillängen von ca. 500 mm für z. B. Oberdruck- und Gegenschlaghämmer auf 1 000 mm und mehr (z. B. bis zu 1.500 mm) erweitert werden, weil sich auch die Produktionsanlagen zur Steigerung der Arbeitsleistung von fruher 40 bis 80 kJ auf heute 130 bis 400 kJ pro Schlag z. B. eines Schmiedehammers erhöht haben.The object of the invention is to provide a clamping wedge device for mounting tools on machine tools, in particular of dies in forging hammers or presses, in which the risk of destruction under extreme loads and relatively large dimensions is reduced. The field of application of the clamping wedge devices is intended by the previously realizable Spannkeillängen of about 500 mm for z. B. overpressure and counterheat hammers can be extended to 1 000 mm and more (eg up to 1500 mm), because also the production equipment to increase the work from earlier 40 to 80 kJ to today 130 to 400 kJ per stroke z. B. have increased a blacksmith's hammer.
Zur Lösung dieser Aufgabe wird mit der Erfindung eine Spannkeilvorrichtung zur Befestigung von Werkzeugen an Werkzeugmaschinen, insbesondere von Gesenken in Schmiedehämmern oder -pressen vorgeschlagen, wobei die Spannkeilvorrichtung versehen ist mit
- einem mindestens eine schräg verlaufende Keilfläche sowie eine Stirnfläche aufweisenden Keilelement, das eine sich zwischen der Stirnfläche und der mindestens einen Keilfläche erstreckende Durchgangsbohrung aufweist,
- mindestens einem Gegenkeilelement, das eine schräg verlaufende Gegenkeilfläche zur Anlage an der mindestens einen Keilfläche des Keilelements sowie eine Stirnfläche und eine sich zwischen der Gegenkeilfläche und der Stirnfläche erstreckende Durchgangsbohrung aufweist,
- einer sich durch die Durchgangsbohrungen des Keilelements und des mindestens einen Gegenkeilelements erstreckenden Spannschraube, die einen Spannschraubenkopf sowie einen Spannschraubenschaft mit einem dem Spannschraubenkopf gegenüberliegenden Außengewindeende und eine Spannschraubenmutter zum Gewindeeingriff mit dem Außengewindeende des Spannschraubenschafts aufweist,
- wobei der Spannschraubenkopf, die Spannschraubenmutter und/oder das Außengewindeende des Spannschraubenschafts zumindest teilweise von den Stirnflächen des Keil- und des mindestens einen Gegenkeilelements abstehen,
- einem den Spannschraubenschaft der Spannschraube zwischen dessen Spannschraubenkopf und der diesem zugewandten Stirnfläche des Keil- bzw. des mindestens einen Gegenkeilelements umgebenden Tellerfederpaket, das mehrere eine Materialdicke und -im entspannten Zustand betrachtet - eine axiale Höhe aufweisende Tellerfederringe umfasst und das um einen in Abhängigkeit vom Grad einer Vorspannung vorgegebenen Federweg noch komprimierbar ist,
- wobei die Durchgangsbohrung des Keilelements oder des mindestens einen Gegenkeilelements in einem ersten Bohrungsabschnitt, der an der dem Spannschraubenkopf zugewandten Stirnfläche des Keil- bzw. des mindestens einen Gegenkeilelements endet, im Wesentlichen zylindrisch (und spielfrei) ist und sich an diesen ersten Bohrungsabschnitt ein zweiter, sich verjungender konischer Bohrungsabschnitt anschließt, und
- wobei der Spannschraubenschaft einen ersten, im Wesentlichen zylindrisch ausgeführten Schaftabschnitt, der sich durch den ersten Bohrungsabschnitt der Durchgangsbohrung erstreckt, aufweist und sich an den zylindrischen ersten Schaftabschnitt des Spannschraubenschafts ein zweiter, sich verjüngender konischer Schaftabschnitt anschließt.
- a wedge element having at least one inclined wedge surface and an end face, which has a through bore extending between the end face and the at least one wedge face,
- at least one counter-wedge element, which has an obliquely running counter-wedge surface for bearing against the at least one wedge surface of the wedge element and an end face and a through bore extending between the counter wedge surface and the end face,
- a tightening bolt extending through the through holes of the wedge member and the at least one counter wedge member having a tightening screw head and a tightening bolt shank having an externally threaded end opposite the tightening screw head and a tightening screw nut for threadably engaging the male threaded end of the tightening bolt shank;
- wherein the clamping screw head, the clamping screw nut and / or the external thread end of the clamping screw shaft project at least partially from the end faces of the wedge and of the at least one counter wedge element,
- a clamping spring shank of the clamping screw between the clamping screw head and the end face of the wedge or the at least one counter-wedge element surrounding the plate spring packet, which considers several a material thickness and -im relaxed state - having an axial height plate spring rings and the one depending on the degree a preload given travel is still compressible,
- wherein the through hole of the wedge member or the at least one counter wedge member in a first bore portion terminating at the end face of the wedge and the at least one counter wedge member facing the tightening screw head is substantially cylindrical (and free of play) and a second, second, and first bore portion; adjoining tapered conical bore section, and
- wherein the clamping screw shank has a first, substantially cylindrically shaped shank portion which extends through the first bore portion of the through hole, and adjoins the cylindrical first shank portion of the clamping screw shank, a second, tapered conical shaft portion.
Bei dieser Spannkeilvorrichtung ist erfindungsgemäß vorgesehen,
- dass bei in der Durchgangsbohrung befindlichem Spannschraubenschaft deren konischer Schaftabschnitt von dem konischen Bohrungsabschnitt der Durchgangsbohrung einen Mindestabstand aufweist, der zumindest gleich der Summe aus dem maximal noch möglichen Federweg des Tellerfederpakets und zusätzlich dem ca. 0,3 bis 0,8-fachen des Federweges zur Kompensation einer potentiellen Durchbiegung des Keils unter Belastungen und einer Dehnung der Spannschraube ist.
- that located in the through hole clamping screw shank whose conical shaft portion of the conical bore portion of the through hole has a minimum distance which is at least equal to the sum of the maximum possible spring travel of the plate spring package and in addition about 0.3 to 0.8 times the spring travel Compensation of a potential deflection of the wedge under loads and an elongation of the clamping screw is.
Die erfindungsgemäße Spannkeilvorrichtung weist zwischen dem Spannschraubenkopf und der diesem zugewandten Stirnfläche des einen der beiden Keilelemente ein Tellerfederpaket auf, das mehrere Tellerfederringe umfasst und das um einen in Abhängigkeit vom Grad der Vorspannung der Spannschraube noch gegebenen Federweg komprimierbar ist. Innerhalb der Durchgangsbohrung desjenigen Keil- bzw. Gegenkeilelements an dessen Stirnfläche das Tellerfederpaket anliegt, existieren ein erster und ein zweiter Bohrungsabschnitt, die aufeinanderfolgen. Der erste Bohrungsabschnitt mündet in die Stirnfläche ein und ist im Wesentlichen zylindrisch ausgeführt, während der sich anschließende zweite Bohrungsabschnitt konisch verjüngend ausgebildet ist, Auch die Spannschraube weist innerhalb ihres sich durch die Bohrung dieses Keilelements erstreckenden Abschnitts einen im Wesentlichen zylindrisch, spielfrei ausgefuhrten ersten Schaftabschnitt und einen sich daran anschließenden zweiten, sich verjungenden konischen Schaftabschnitt auf. Im gespannten Zustand der Spannschraube weist der konische Schaftabschnitt einen axialen Mindestabstand zum konischen Bohrungsabschnitt auf. Mit anderen Worten sind also die beiden konischen Abschnitte um diesen Mindestabstand axial gegeneinander versetzt, so dass ihre Konusflächen nicht aneinander liegen. Der Mindestabstand ist dabei gleich der oder größer als die Summe aus dem maximal möglichen Federweg des Tellerfederpakets und zusätzlich ca, dem 0,3 bis 0,8-fachen des Federweges des Tellerfederpakets.The clamping wedge device according to the invention has, between the clamping screw head and the end face of the one of the two wedge elements facing the latter, a disc spring packet which comprises a plurality of disc spring rings and which can be compressed by a travel which is still given depending on the degree of pretensioning of the clamping screw. Within the through hole of that wedge or counter wedge element on the end face of the plate spring assembly is present, there are a first and a second bore portion, which follow one another. The first bore portion opens into the end face and is designed substantially cylindrical, while the adjoining second bore portion is conically tapered, also the clamping screw has within its extending through the bore of this wedge member a substantially cylindrical, backlash executed first shaft portion and an adjoining second, tapered conical shaft section. In the tensioned state of the clamping screw, the conical shaft section has an axial minimum distance to the conical bore section. In other words, so are the two conical sections to this minimum distance axially offset from each other, so that their conical surfaces do not lie against each other. The minimum distance is equal to or greater than the sum of the maximum possible travel of the plate spring package and in addition ca, 0.3 to 0.8 times the spring travel of the plate spring package.
Der Spannschraubenquerschnitt ist zweckmäßigerweise als Dehnschraube ausgelegt, indem sie sich in Abhängigkeit von den Eigenschaften des Materials, aus dem sie besteht, bis zu einer Streckgrenze mit einem Wert zwischen 0,2 % bis 0,5 % ihrer Länge dehnen kann.The clamping screw cross-section is expediently designed as an expansion screw in that it can stretch to a yield strength of between 0.2% to 0.5% of its length, depending on the properties of the material of which it is made.
Durch die Tatsache, dass auch im vollständig komprimierten Zustand des Tellerfederpakets die beiden konischen Flächen der Durchgangsbohrung und des Spannschraubenschafts einen Abstand voneinander aufweisen, wird dem Umstand Rechnung getragen, dass die Spannkeilvorrichtung auch unter höchsten Belastungen nicht zerstört wird. Darüber hinaus ist der Mindestabstand unter Belastung zweckmäßigerweise so zu wählen, dass auch elastische Seitenverformungen der Spannschraube und insbesondere ihres Spannschraubenschafts nicht sogleich zu einer Kontaktierung der konischen Flächen zwischen Spannschraubenschaft und Durchgangsbohrung führt. Es hat sich nämlich bei Versuchen herausgestellt, dass insbesondere bei großen Spannkeillängen im Bereich zwischen 0,5 m bis über 1 m und insbesondere bis ca. zu 1,5 m auf die Spannkeilvorrichtung Seitenbelastungen wirken, die zu einer elastischen bogenförmigen Verformung fuhren. Dadurch verformt sich auch der Spannschraubenschaft bogenförmig, und zwar mit der Folge, dass sich der Spannschraubenschaft innerhalb der Durchgangsbohrungen der beiden Keilelemente bewegt und die konischen Flächen näher aneinander rücken. Würde es nun zu einer Kontaktierung der konischen Flächen kommen, so könnte dies eine baldige Zerstörung der Spannkeilvorrichtung nach sich ziehen, Durch den erfindungsgemäßen Vorschlag, einen in oben angegebener Weise vorgegebenen Mindestabstand zwischen den konischen Flächen zu belassen, kann der Gefahr einer Zerstörung der Spannkeilvorrichtung infolge eines Kontaktierens der konischen Flächen von Durchgangsbohrung und Spannschraubenschaft entgegengewirkt werden.Due to the fact that the two conical surfaces of the through hole and the clamping screw shaft have a distance from each other even in the fully compressed state of the disc spring package, the circumstance is taken into account that the clamping wedge device is not destroyed even under the highest loads. In addition, the minimum distance under load expediently to be chosen so that even elastic side deformations of the clamping screw and in particular its clamping screw shaft does not immediately lead to a contacting of the conical surfaces between clamping screw shank and through hole. It has been found in tests that, in particular for large clamping bar lengths in the range between 0.5 m to more than 1 m and in particular up to about 1.5 m on the clamping wedge device side loads act that lead to an elastic arcuate deformation. As a result, the clamping screw shank deforms arcuately, with the result that the clamping screw shaft moves within the through holes of the two wedge elements and move the conical surfaces closer to each other. Would it come to a contact of the conical surfaces, this could result in a speedy destruction of the clamping wedge device by the inventive proposal to leave a predetermined manner above specified minimum distance between the conical surfaces, the risk of destruction of the clamping wedge device due contacting the conical Surfaces of through hole and clamping screw shaft are counteracted.
Die beiden Konuswmkel des konischen Bohrungsabschnitts und des konischen Schaftabschnitts können grundsätzlich gleich oder unterschiedlich sein. Im Falle gleicher Konuswinkel weist jeder Punkt auf der Konusfläche beispielsweise des konischen Schaftabschnitts den gleichen axialen Abstand zur konischen Fläche des konischen Bohrungsabschnitts auf. Ist beispielsweise der Konuswinkel des Bohrungsabschnitts größer als derjenige des Schaftabschnitts, so existieren je nach Lage zweier beabstandeter Punkte auf den beiden Konusfläche unterschiedlich große Abstände, wobei jedoch der kleinste Abstand mindestens gleich dem erfindungsgemäßen Mindestabstand sein sollte.The two conical walls of the conical bore section and of the conical shaft section can basically be the same or different. In the case of identical cone angles, each point on the conical surface, for example of the conical shaft section, has the same axial distance to the conical surface of the conical bore section. For example, if the cone angle of the bore portion is greater than that of the shaft portion, depending on the location of two spaced points on the two cone surface different distances, but the smallest distance should be at least equal to the minimum distance according to the invention.
In weiterer vorteilhafter Ausgestaltung der Erfindung ist vorgesehen, dass der Spannschraubenschaft mit seinem ersten zylindrischen Schaftabschnitt innerhalb des ersten zylindrischen Bohrungsabschnitts der Durchgangsbohrung axial und spielfrei geführt ist. Durch die zylindrische Führung des Spannschraubenschafts in dem zylindrischen Bohrungsabschnitt der Durchgangsbohrung ist eine zentrische Führung der Spannschraube in der Spannkeilvorrichtung gewährleistet. Auch dies reduziert die Gefahr der Zerstörung bei extremer Belastung der Spannkeilvorrichtung, wie dies insbesondere bei großformatigen und langen (bis zu einem Meter Länge und mehr) Spannkeilvorrichtungen gegeben ist.In a further advantageous embodiment of the invention it is provided that the clamping screw shaft is guided axially and without play with its first cylindrical shaft portion within the first cylindrical bore portion of the through hole. Due to the cylindrical guidance of the clamping screw shaft in the cylindrical bore section of the through hole, a centric guidance of the clamping screw in the clamping wedge device is ensured. This also reduces the risk of destruction under extreme stress on the clamping wedge device, as is particularly true in large-format and long (up to one meter in length and more) Spannkeilvorrichtungen.
Die Größe des Federweges wird empirisch entsprechend der Länge der Spannkeilvorrichtung ermittelt und korrespondiert mit dem Anzugsdrehmoment der Spannschraubenmutter und dem erforderlichen Federdruck.The size of the spring travel is determined empirically according to the length of the clamping wedge device and corresponds to the tightening torque of the clamping nut and the required spring pressure.
Der erforderliche Federdruck wird empirisch aus der Größe der Seitenfläche (einseitige Anlagefläche an der Maschine bzw. dem Gesenk) der Spannkeilvorrichtung (Spannfläche) ermittelt. Er sollte so gewählt sein, dass ausreichender Anpressdruck auf den inneren Keilhälften vorhanden ist, um die Keilhälften zur Erzeugung der Spannkraft für die Werkzeuge anzupressen.The required spring pressure is determined empirically from the size of the side surface (one-sided contact surface on the machine or the die) of the clamping wedge device (clamping surface). He should be chosen so that sufficient Contact pressure on the inner wedge halves is present to press the wedge halves to generate the clamping force for the tools.
Beim schlagartigen Aufsetzen der Werkzeuge und beim Abbau der Umformenergie zum Gesenkschmieden werden auch die Werkzeuge und Spannkeilvorrichtungen elastisch verformt. Das Tellerfederpaket baut dabei auch seine Federkraft ab, wobei der Abbau nicht so weit gehen sollte, dass sich die Spannmutter lockern kann.In the sudden placement of the tools and the reduction of the forming energy for die forging and the tools and clamping wedge devices are elastically deformed. The disc spring assembly also reduces its spring force, the degradation should not go so far that the nut can loosen.
Das Tellerfederpaket weist entweder mehrere jeweils gegensinnig ausgerichtete oder in Gruppen gleichsinnig und von Gruppe zu Gruppe gegensinnig ausgerichtete Tellerfederringe mit einem im flachgedrückten Zustand gegebenen Innendurchmesser auf, wobei der Innendurchmesser der Tellerfederringe größer ist als der Außendurchmesser desjenigen Abschnitts des Spannschraubenschafts, den das Tellerfederpaket umgibt. Dies hat den Vorteil, dass die Tellerfederringe auch bei vollständig komprimiertem Tellerfederpaket nicht von außen an dem Spannschraubenschaftabschnitt, den das Tellerfederpaket umgibt, anliegt.The disc spring assembly either has a plurality of oppositely oriented or in groups in the same direction and from group to group oppositely oriented plate spring rings with a given in the flattened state inner diameter, wherein the inner diameter of the plate spring rings is greater than the outer diameter of that portion of the clamping screw shaft, which surrounds the plate spring package. This has the advantage that the plate spring rings, even with fully compressed disc spring assembly is not from the outside of the clamping screw shaft portion, which surrounds the disc spring assembly abuts.
Normalerweise ist der Spannschraubenschaft der Spannschraube zwischen dem Spannschraubenkopf und dem Außengewindeende frei von Außengewindegängen, Vorteilhaft ist es bei einem derartigen Design, dass sich am Ubergang zum Außengewindeende eine Außenumfangsvertiefung (auch als Freischnitt bezeichnet) befindet. Durch diese Außenumfangsvertiefung, ab der sich dann das Außengewinde bis zur dem Spannschraubenkopf gegenüberliegenden Stirnfläche der Schraube erstreckt, kann die Gefahr von Zerstörungen (Abrissen) der Spannschraube infolge von Belastungen weitestgehend reduziert werden. Die Außenumfangsvertiefung weist zweckmäßigerweise eine Tiefe auf, die im Wesentlichen gleich der Höhe des Außengewindes am Außengewindeende des Spannschraubenschafts ist. Der Durchmesser des Spannschraubenschafts im Bereich des Freischnitts bzw. der Außenumfangsvertiefung ist also gleich dem Kerndurchmesser des Außengewindeendes. In seinem verbleibenden Bereich zwischen der Außenumfangsvertiefung und dem Spannschraubenkopf kann der Spannschraubenschaft demnach einen größeren Durchmesser aufweisen als im Bereich der Außenumfangsvertiefung.Normally, the clamping screw shank of the clamping screw between the clamping screw head and the external thread end is free from male threads. It is advantageous in such a design that there is an outer peripheral recess (also referred to as a free cut) at the transition to the male thread end. By this outer circumferential recess, from which then extends the external thread to the clamping screw head opposite end face of the screw, the risk of destruction (breaks) of the clamping screw due to stress can be largely reduced. The outer circumferential recess expediently has a depth which is substantially equal to the height of the external thread at the external thread end of the clamping screw shaft. The diameter of the clamping screw shaft in the region of the clearance or the outer circumferential recess is therefore equal to the core diameter of the external thread end. In his remaining Area between the outer peripheral recess and the clamping screw head may therefore have a larger diameter of the clamping screw shank than in the region of the outer circumferential recess.
In weiterer vorteilhafter Ausgestaltung der Erfindung kann vorgesehen sein, dass die Spannschraubenmutter eine erste Stirnfläche, an der sich die Spannschraubenmutter an einer Anlagefläche des Keil- bzw. des mindestens einen Gegenkeilelements abstutzt, und eine zweite Stirnfläche mit einer sich an diese anschließende Werkzeugangriffsfläche zum Verschrauben der Spannschraubenmutter mit dem Außengewindeende des Spannschraubenschafts aufweist, dass sich durch die Spannschraubenmutter eine Innengewindebohrung erstreckt und dass das Innengewinde der Spannschraubenmutter mit axialem Abstand zu der ersten Stirnfläche der Spannschraubenmutter endet. Bei dieser Ausgestaltung der Spannschraubenmutter ist deren Innengewinde nicht bis zur dem Spannschraubenkopf zugewandten ersten Stirnfläche der Spannschraubenmutter fortgesetzt, sondern endet im axialen Abstand zu diesem, wobei vorteilhafterweise auch hier gilt, dass die radiale Tiefe der Spannschraubenmutterbohrung im Wesentlichen gleich der Innengewindehöhe der Spannschraubenmutter ist, die Spannschraubenmutter an ihrer ersten Stirnfläche also entsprechend aufgebohrt sein kann.In a further advantageous embodiment of the invention can be provided that the clamping nut a first end face on which the clamping nut is supported on a contact surface of the wedge or the at least one counter wedge element, and a second end face with an adjoining thereto tool engagement surface for screwing the The clamping nut with the male thread end of the clamping screw shaft has an internally threaded bore extending through the clamping nut and that the internal thread of the clamping screw nut ends at an axial distance from the first end face of the clamping screw nut. In this embodiment of the clamping nut whose internal thread is not continued to the clamping screw head facing first end face of the clamping nut, but ends at an axial distance to this, advantageously also applies here that the radial depth of Spannschraubenmutterbohrung is substantially equal to the internal thread height of the clamping nut, which Clamping nut can therefore be drilled accordingly at its first end face.
Auch an der zweiten Stirnfläche der Spannschraubenmutter existiert zweckmäßigerweise ein axialer Abstand zum Innengewinde. Es existiert in diesem Bereich also genauso wie an der ersten Stirnfläche ein (innenliegender) Freischnitt in Form einer Innenumfangsvertiefung.Also on the second end face of the clamping screw nut expediently exists an axial distance from the internal thread. It exists in this area so as well as at the first end face an (internal) free cut in the form of an inner circumferential recess.
In weiterer vorteilhafter Ausgestaltung der Erfindung kann vorgesehen sein, dass der Spannschraubenschaft innerhalb seines zylindrischen und/oder konischen Schaftabschnitts ein Langloch aufweist, das in axialer Erstreckung der Spannschraube verläuft, und dass sich durch das Langloch ein die Durchgangsbohrung querender Sicherungsstift erstreckt. Die Längserstreckung des Langlochs wird dabei zur Ermöglichung einer relativen Verschiebung der Spannschraube in der Durchgangsbohrung um den Mindestabstand der beiden konischen Schaft- und Bohrungsabschnitte gewählt.In a further advantageous embodiment of the invention can be provided that the clamping screw shaft has within its cylindrical and / or conical shaft portion a slot which extends in the axial extension of the clamping screw, and that extends through the slot a through hole crossing locking pin. The longitudinal extension of the slot is to enable a relative displacement of the Clamping screw in the through hole chosen by the minimum distance between the two conical shaft and bore sections.
In weiterer vorteilhafter Ausgestaltung der Erfindung kann vorgesehen sein, dass zwischen dem Spannschraubenkopf und dem Tellerfederpaket zur Anpassung an die axiale Länge des verwendeten Tellerfederpakets einer von mehreren, unterschiedliche axiale Dicken aufweisenden Distanzringen angeordnet ist. Die unterschiedlich dicken Distanzringe sorgen für eine Kompensation unterschiedlich langer Tellerfederpakete an dem Spannschraubenkopf und den Abstand zwischen diesem und dem diesem zugewandten Keilelement.In a further advantageous embodiment of the invention can be provided that is arranged between the clamping screw head and the disc spring assembly for adaptation to the axial length of the diaphragm spring assembly used one of several, different axial thicknesses spacer rings. The different thickness spacer rings provide compensation for different length disc spring assemblies on the clamping screw head and the distance between this and the wedge element facing this.
Zur weiteren Verbesserung der versatzfreien Führung der Keil- und Gegenkeilflächen kann ferner vorgesehen sein, dass die schrägverlaufenden Keil- und Gegenkeilflächen - im Querschnitt durch die aneinander liegenden Keil- und Gegenkeilelemente betrachtet - zueinander komplementäre, gerade, sich zu einer im Wesentlichen Trapez- und/oder V-Form ergänzende Linienabschnitte abweisen.To further improve the offset-free guidance of the wedge and counter wedge surfaces may further be provided that the oblique wedge and counter wedge surfaces - viewed in cross section through the juxtaposed wedge and counter wedge elements - complementary, straight, to a substantially trapezoidal and / or reject V-shape supplementary line segments.
Schließlich kann das Keilelement zwei sich aneinander anschließende, gegeneinander geneigte schrägverlaufende Keilflächen aufweisen, wobei an jeder dieser Keilflächen jeweils ein Gegenkeilelement mit seiner Gegenkeilfläche anliegt sowie die Stirnseiten der beiden Gegenkeilelemente einander abgewandt sind, und wobei sich zwischen den beiden Stirnseiten der Gegenkeilelemente und durch das Keilelement hindurch die Spannschraube erstreckt. Eine derartige Spannkeilvorrichtung mit zwei gegeneinander geneigten schrägverlaufenden Keilflächen und zwei Gegenkeilelementen ist beispielsweise in
Die Erfindung wird nachfolgend anhand eines Ausfuhrungsbeispiels und unter Bezugnahme auf die Zeichnung näher erläutert. Im Einzelnen zeigen dabei:
- Fig. 1
- eine Vorderansicht eines Schmiedehammers bzw. einer Schmiedepresse zur Verdeutlichung des Einsatzes einer Spannkeilvorrichtung zur Befestigung von Gesenkhälften und
- Fig. 2
- einen Horizontalschnitt durch eine Spannkeilvorrichtung gemäß II-II der
Fig. 1 .
- Fig. 1
- a front view of a forging hammer or a forging press to illustrate the use of a clamping wedge device for attachment of die halves and
- Fig. 2
- a horizontal section through a clamping wedge device according to II-II of
Fig. 1 ,
Anhand von
In
Durch die beiden miteinander fluchtenden Durchgangsbohrungen 52,54 erstreckt sich eine Spannschraube 56 mit einem Spannschraubenkopf 58 an ihrem einen axialen Ende und einer Spannschraubenmutter 60 an ihrem anderen axialen Ende. Die Spannschraube 56 umfasst einen Spannschraubenschaft 62, der sich von dem Spannschraubenkopf 58 aus erstreckt und an seinem diesem gegenuberliegenden Ende ein Außengewindeende 64 bildet. Zwischen dem Spannschraubenkopf 58 und der diesem gegenüberliegenden Stirnfläche 40 ist der Spannschraubenschaft 62 von einem Tellerfederpaket 66 umgeben, das mehrere Tellerfederringe 68 aufweist, die entweder gruppenweise gleichsinnig und von Gruppe zu Gruppe gegensinnig oder aber einzeln gegensinnig angeordnet sind. Zwischen dem Tellerfederpaket 66 und dem Spannschraubenkopf 58 befindet sich ein Distanzring 69.Through the two aligned through
Durch Drehen der in diesem Ausführungsbeispiel unverlierbar im Gegenkeilelement 38 angeordneten Spannschraubenmutter 60 kann die Spannkeilvorrichtung 34 gespannt werden, wie dies an sich bekannt ist.By turning the captive in this embodiment, the clamping element in the
Wie in
Der Spannschraubenschaft 62 ist (in diesem Ausführungsbeispiel am Keilelement 36) durch einen Sicherungsstift 80 gegen ein Mitdrehen der Spannschraube 56 beim Aufschrauben der Spannschraubenmutter 60 gesichert. Der Sicherungsstift 80 erstreckt sich quer durch die Durchgangsbohrung 52 hindurch und ist von einer Langlochbohrung 82 des Spannschraubenschafts 62 aufgenommen. Alternativ kann der Spannschraubenschaft 62 zur Verhinderung des Mitdrehens in seinem mittleren Bereich einen polygonalen Querschnitt aufweisen, der geringfügig größer ist als der Gewindedurchmesser. Der Stift hat daruber hinaus die Aufgabe, den Ein- und Ausbau der Spannkeilvorrichtung 34 zu vereinfachen. Die axiale Erstreckung der Langlochbohrung 82 ist so bemessen, dass die Spannschraube 56 sich ihren Belastungen entsprechend bewegen kann, ohne dass der Sicherungsstift 80 abgeschert o.dgl. beschädigt wird.The clamping
Wie ebenfalls in
Die Spannschraubenmutter 60 weist in herkömmlicherweise eine Durchgangsbohrung 88 auf, die mit einem Innengewinde 90 zur Verschraubung mit dem Außengewinde 86 des Außengewindeendes 64 versehen ist. Das Innengewinde 90 der Spannschraubenmutter 60 erstreckt sich nicht bis zu der innenliegenden ersten Stirnfläche 92 und der außenliegenden zweiten Stirnfläche 94 der Spannschraubenmutter 60 sondern endet mit axialem Abstand zu diesen beiden Stirnflächen 92,94. Innerhalb der beiden vom Innengewinde 90 freien Bereiche der Durchgangsbohrung 88 der Spannschraubenmutter 60 weist diese einen Innendurchmesser auf, der gleich dem Außendurchmesser des Außengewindes 86 des Außengewindeendes 64 ist bzw. auch größer als dieser sein kann, was in
Claims (12)
dadurch gekennzeichnet ,
characterized ,
Priority Applications (3)
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EP11193563.1A EP2604361B1 (en) | 2011-12-14 | 2011-12-14 | Tensioning wedge device for fastening tools to tool machines |
PL11193563T PL2604361T3 (en) | 2011-12-14 | 2011-12-14 | Tensioning wedge device for fastening tools to tool machines |
ES11193563.1T ES2560606T3 (en) | 2011-12-14 | 2011-12-14 | Wedge fixing device for fixing tools on machine tools |
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EP11193563.1A EP2604361B1 (en) | 2011-12-14 | 2011-12-14 | Tensioning wedge device for fastening tools to tool machines |
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EP2604361A1 true EP2604361A1 (en) | 2013-06-19 |
EP2604361B1 EP2604361B1 (en) | 2015-10-28 |
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CN113547143A (en) * | 2020-04-26 | 2021-10-26 | 航天科工惯性技术有限公司 | Thin-wall structural part clamping device |
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2011
- 2011-12-14 EP EP11193563.1A patent/EP2604361B1/en active Active
- 2011-12-14 ES ES11193563.1T patent/ES2560606T3/en active Active
- 2011-12-14 PL PL11193563T patent/PL2604361T3/en unknown
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DE4029171A1 (en) | 1990-09-14 | 1992-03-19 | Feuerbacher Umformtechnik Schi | Clamping wedge system for holding dies during forging and pressing - comprises wedge, opposing wedge and clamping screw with gap in between and inward facing projections in vibrating area |
DE9007763U1 (en) | 1990-09-14 | 1995-05-11 | Thorsten Broer Ruest Und Schmi | Wedge clamping device |
DE9414094U1 (en) | 1994-08-31 | 1994-10-20 | Thorsten Broer Ruest Und Schmi | Wedge clamping device |
DE29604287U1 (en) | 1996-03-08 | 1996-05-15 | Zimmer Hans Gmbh | Clamping wedge device for fixing die tools |
DE29609162U1 (en) | 1996-05-22 | 1996-07-11 | Eisele Oliver | Strand seal |
DE29916856U1 (en) | 1999-09-24 | 2000-01-05 | Broer Thorsten | Wedge device |
DE20303909U1 (en) | 2003-03-12 | 2004-01-15 | Broer, Thorsten | Clamping wedge device for fixing tools on machine tools, especially forging dies in forging hammers/presses, comprises a wedge, counter-wedge, poppet pin, adjusting nut, and locking device preventing movement of the wedge and counter-wedge |
DE20303910U1 (en) | 2003-03-12 | 2004-01-15 | Broer, Thorsten | Clamping wedge device for fixing tools on machine tools, especially forging dies in forging hammers/presses, comprises a contact plane having a thicker section intersecting the under sides of a wedge and counter-wedge |
DE102006042359A1 (en) | 2005-09-14 | 2007-03-15 | Broer, Thorsten | Clamping wedge device to fit countersinks and hammers to machine tools has double wedge element, two counter-wedge elements and clamping element |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN113547143A (en) * | 2020-04-26 | 2021-10-26 | 航天科工惯性技术有限公司 | Thin-wall structural part clamping device |
Also Published As
Publication number | Publication date |
---|---|
ES2560606T3 (en) | 2016-02-22 |
PL2604361T3 (en) | 2016-05-31 |
EP2604361B1 (en) | 2015-10-28 |
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