CA2700576C - Wedge drive with slider receiving means - Google Patents
Wedge drive with slider receiving means Download PDFInfo
- Publication number
- CA2700576C CA2700576C CA2700576A CA2700576A CA2700576C CA 2700576 C CA2700576 C CA 2700576C CA 2700576 A CA2700576 A CA 2700576A CA 2700576 A CA2700576 A CA 2700576A CA 2700576 C CA2700576 C CA 2700576C
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- Canada
- Prior art keywords
- slider element
- receiving means
- slider
- wedge
- set forth
- Prior art date
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- Expired - Fee Related
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Classifications
-
- 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
- B30B1/40—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 wedge means
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D19/00—Flanging or other edge treatment, e.g. of tubes
- B21D19/08—Flanging or other edge treatment, e.g. of tubes by single or successive action of pressing tools, e.g. vice jaws
- B21D19/082—Flanging or other edge treatment, e.g. of tubes by single or successive action of pressing tools, e.g. vice jaws for making negative angles
- B21D19/084—Flanging or other edge treatment, e.g. of tubes by single or successive action of pressing tools, e.g. vice jaws for making negative angles with linear cams, e.g. aerial cams
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Machine Tool Units (AREA)
- Clamps And Clips (AREA)
- Processing Of Stones Or Stones Resemblance Materials (AREA)
- Mounting, Exchange, And Manufacturing Of Dies (AREA)
- Connection Of Plates (AREA)
- Bearings For Parts Moving Linearly (AREA)
Abstract
In the case of a wedge drive (1) with a slide element receptacle (2), a movable slide element (3) and a driver element (5), wherein sliding surfaces (301, 302) are provided between the slide element (3) and the driver element (5), a dovetail-like or prismatic guiding device (6) is provided between the slide element (3) and the slide element receptacle (2).
Description
Wedge drive with slider receiving means The invention concerns a wedge drive or cotter key comprising a slider element receiving means, a movable slider element and a driver element, and wherein sliding surfaces are provided between the slider element to and the driver element, wherein a dovetail-like or prism guide with sliding surfaces provided at the driver element and of the slider element receiving means, is arranged between the slider element and the slider element receiving means.
The invention furthermore concerns a slider element for a wedge drive with a slider element receiving means and a driver element, the slider element being arranged between the slider element receiving means and the driver element, wherein the slider element is provided with a dovetail-like or prismatically formed side with sliding surfaces.
A wedge drive which is also referred to as a slider serves basically for 2o diverting pressing forces to stamping or shaping tools in order thereby to be able to cut, perforate or shape in particular regions of bodywork portions, which are of an inclined or undercut configuration. In that arrangement the wedge drive includes at least one slider element receiving means, a movable slider element and a driver element. The slider element receiving means which has such as rigid is usually connected to apart of the press or the pressing tool, in which press or pressing tool the wedge drive is intended to implement the stamping or shaping operations. A wedge drive is referred to as an upper part slider if the slider element receiving means thereof is fixed in the upper part of the pressing tool, which is connected to the moving pressing ram. Reference is made to a lower part slider if the slider element receiving means thereof is connected to the lower pressing tool which is fixed on the rigid press table. Irrespective of the part to which the slider element receiving means of the wedge drive is connected, it usually has a linear guide means in which the movable slider element is reciprocatable, but as such it is fixedly connected to the slider element receiving means. The driver element is usually in the form of a rigid element fixedly connected to the part of the pressing tool, to which the slider element receiving means is not fastened. The driver element usually has inclined wedge portions and therewith serves as a drive 4o element in relation the movable slider element.
In the situation involving a substantially perpendicular advance movement of a pressing tool, which is referred to as the working stroke, the slider element which is in its rearward position comes to bear against the rigidly standing driver element and supported thereby is advanced by way of the inclined positioning thereof (wedge shape) facing in the working direction. In that situation the inclination of the linear guide means of the slider element receiving means is matched to the inclined positioning of the driver element so that no acceleration of the movable slider element is involved, in relation to the actual pressing speed. The movable slider element is thus only driven by the pressing tool and urged controlledly forwardly or outwardly in order to be able to perform the stamping or shaping work. In the rearward stroke movement in which the pressing tool has moved beyond its bottom dead center position and the two parts are moving away from each other again, the movable slider element is usually pushed back into its original position by means of a suitably designed 1o resilient element, whereupon the procedure can be re-started. The return force required for the return movement of the slider element is usually between 2 and 10% of the actual working force and the weight of the slider element. In that respect, decisive aspects in regard to the magnitude of the pressing force are the dimensions of the surfaces for transmitting the pressure, which are referred to as sliding surfaces, the respective inclinations of the linear guide means in the slider element receiving means and the inclined positioning of the driver element as well as the cooperation of the surfaces and inclinations and the structure of the slider element itself. The pressures to be transmitted are usually between a few 100 kN and several 10,000 kN.
The linear guide means in the slider element receiving means was intended to guide the movable slider element with as little play as possible and in so doing to withstand high pressing forces and afford long service lives. To permit burr-free cutting or perforating of a workpiece a tolerance in terms of accuracy of movement of the movable slider element of a maximum of 0.02 mm is required. If that tolerance is not met, the workpieces which are cut or perforated or shaped in some other way can no longer be placed one upon the other in accurate register relationship so that errors in the basic bodywork structure occur and/or workpieces rubbing against each other means that faster corrosion occurs, the bodywork constructed is of reduced strength and possibly an increased amount of noise is generated by virtue of sheet metal parts which come loose. To avoid all those disadvantages, the requirement in particular in the automobile industry is that a wedge drive provides for extremely high levels of accuracy of movement and permanently withstands the pressing pressures required or makes them available in relation to the stamping or shaping tool.
In order to afford the required accuracy of movement here, various concepts have been developed, of which some are set forth hereinafter. By way of example slider guide means with side sliding plates and driver elements arranged at a right angle as well as a screwed cover plate for holding the slider element are known. Slider guide means of that kind admittedly withstand very high pressing forces and lateral thrust forces but they are very complicated and costly to manufacture as a high level of manual co-ordination complication and expenditure is required for matching the guide play between the elements. A further problem which has been found is inadequate protection in regard to the slider guide means falling apart, in which case the whole of the slider weight plus the rearward attachment forces act on the fastening screws of the cover plate and can very rapidly overload them. In addition such a slider guide means is comparatively large in structural size and is therefore unsuitable for constructing small sliders.
Slider guide means are also known having lateral angle bars and a driver plate arranged at a right angle. Unlike the above-discussed slider guide means the combination of the lateral sliding plates with a cover plate leads to a reduction in the amount of structural space required so that in particular it is also possible as a result to construct smaller slider sizes.
It will be noted however that high forces act on the fastening screws of the angle bars and as a result provide that there is a relatively high risk of accident. In addition the complication and expenditure in terms of coordinating the co-operating elements for matching the guide play is high so that additional costs are also incurred here.
A further kind of slider guide which is used includes lateral sliding and cover plates which are inclined at an angle of 45 . They are therefore arranged approximately in a roof-shaped configuration. That makes it possible to achieve a reduction in structural width as the cover bars and the sliding plates are arranged one over the other and not one beside the other. It will be noted however that the structural space required is still very great so that it is scarcely possible to produce small sliders. In addition the traction forces occurring have a detrimental effect on the fastening screws of the cover plates, and that leads to a high level of process uncertainty.
A further known structure includes a slider guide means with a driver plate and one or two column guide means with bushes in order to hold the slider element laterally and to prevent it from dropping out. The use of a guide column with a driver plate means that admittedly only still comparatively small structural spaces are required and it is possible to achieve considerably less expensive manufacture than when using the above-mentioned solutions in the state of the art. It will be noted however that the column guide means, due to the type of structure involved, is not capable of compensating for high lateral pressures. In addition it cannot carry any heavyweight slider elements so that those slider elements produce less pressing forces and are more susceptible to trouble in the pressing procedure.
A further kind of slider element guide arrangement is known for example from EP 1 035 965 61. This arrangement provides for a clamping embracing relationship in respect of the slider element guide means, wherein the driver element provides a prism guide and sliding plates are inserted between the driver element and the slider element. The roof shape involved means that very high slider forces are possible, while entailing small structural spaces, and equally a very accurate guide play so that the wedge drive or the slider element guide means is stable and has a long working life. It will be noted however that manufacture of the clamping guide means, because of the expensive cutting machining operations required to achieve a precise fitting shape, is really complicated and cost intensive as a result.
Further wedge drives are also known for example from EP 1259371131, DE 198 60 178 C1 and EP 1 197 319 131.
FR-A-2 421 030 discloses a wedge drive of the kind mentioned in the beginning of the description which is used for a work-piece clamping device. The device comprises a base plate (driver element), a ram (slider element receiving means) and a wedge (slider element) located between the base plate and the ram, the wedge having an inclined surface facing the ram, the facing surface of the ram being inclined at the same angle, whereby the wedge is driven by a screw along the base plate for altering the separation between the base plate and the ram. The wedge has a dovetail-shaped projection with sliding surfaces for running in a corresponding groove of the base plate.
A wedge drive of the kind indicated in the beginning of the description is also known from DE 198 61 171 B4 as a radial press comprising an upper press yoke (slider element), a transverse pusher (slider element receiving means) having an inclined surface facing a correspondingly inclined surface of the upper press yoke. A
dovetail-like or T-like guide is provided between the transverse pusher and the upper press yoke including sliding surfaces.
All the above-described design concepts of a slider element guide means for a wedge drive have one or more sliding plates for the transmission of generally high pressing forces, and likewise suitably designed holding elements for holding the slider element in the guide provided for same. The sliding plates serve to permanently transmit the working pressures exerted by the pressing tool from the slider element receiving means and the driver element to the movable slider element and thus to guarantee the actual advancing drive effect. The holding elements serve for linearly holding the slider element on the sliding plates of the sliding element receiving means, in which case they permanently ensure the required accuracy of movement and are intended to possibly compensate for lateral thrust forces which occur in the shaping operation or in the cutting or stamping procedure.
Now the object of the present invention is to further develop a wedge drive in such a way that a guide for the movable slider element is provided, which permits still better motional accuracy than the solutions in the state of the art, which provides for optimum conversion of the pressing force which acts into the stamping or shaping movement, which compensates for lateral thrust forces even better than the state of the art and which provides a longer service life for the wedge drive than is hitherto possible with the solutions in the state of the art. The invention further 5 seeks to provide that a lower level of complication and expenditure is required when co-ordinating the wedge drives and more economical manufacture becomes a possibility.
For a wedge drive, as provided in the present application, that object is attained in 1o the that the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider receiving means to the slider element in a work stroke during which the slider element is moved outwardly between the driver element and the slider element receiving means, are arranged at an angle relative to each other which is bigger than 00 and smaller than 1800.
For a slider element, as provided in the present application, the object is attained in that the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider element receiving means to the slider element in a working stroke during which the slider element is moved outwardly between the 2o driver element and the slider element receiving means, are arranged at an angle relative to each other.
That therefore provides a wedge drive or cotter key in which the movable slider element has a dovetail-like or prismatic side, wherein the slider element receiving means is in the form of a corresponding counterpart portion so that the slider element with its dovetail-like or prismatic side can engage into the slider element receiving means and can be guided and held therein, in the self-centering manner.
The surfaces on the slider element and/or the slider element receiving means, that are respectively provided by the dovetail shape and the prism shape, bear against 3o each other, in which case forces directed in different directions can be carried without any problem by virtue of the surfaces which are at an angle relative to each other, in the dovetail or prism shape. This guide means between the slider element receiving means and the slider element permits self-centering linear guidance for the slider element. The dovetail shape means that, after being inserted into the correspondingly shaped receiving configuration of the slider element receiving means, the movable slider element is safeguarded against falling out or lateral displacement, without further measures.
As guidance for the slider element along the slider element receiving means by virtue of the dovetail guide arrangement is possible with a high degree of precision and without being sensitive to lateral thrust forces as well as being inexpensive to manufacture, without the provision of further components in the form of a linear guide means, the result is a compact wedge drive with a very high level of accuracy of motion, which is also insensitive in relation to manufacturing tolerances.
As clamp guides or further elements are no longer required, not only can the costs be reduced in comparison with the solutions in the state of the art, but the process reliability is also increased and a possible risk of accident reduced. As the slider element only needs to be pushed into the slider element receiving means, assembly of the wedge drive is simplified in comparison with the solutions in the state of the art. It is possible to dispense with a cost-intensive operation of grinding in the guide elements as the prism guides or dovetail guide of the slider element receiving means, the slider element end the driver element are insensitive in relation to tolerances in manufacture. The self-centering effect achieved by the prism guides also leads to a very high level of accuracy in terms of motion in lo regard to carrying lateral thrust forces. By virtue of the compact structure of the wedge drive it is not only suitable for a small structural space available within a pressing tool, but, as will be appreciated, it is also suitable for uses involving larger dimensions.
Advantageously sliding surfaces are provided on the slider elements And or the slider element receiving means. In a particularly preferred feature the dovetail-like or prism guide means includes at least two sliding plates arranged at an angle relative to each other. Advantageously the sliding plates of the dovetail-like or prism guide means can be L-shaped in cross-section. It is further found to be advantageous if sliding plates are provided on all surfaces, which slide against each other, of the slider element and the slider element receiving means, so that in each case at least two sliding plates arranged at an angle relative to each other are provided on the slider element and the slider element receiving means. The sliding plates which are roof-shaped or L-shaped in cross-section can advantageously be so arranged that their inner narrow sides, by virtue of the outwardly inclined oblique positioning of the sliding plates, afford an undercut configuration in the form of the above-mentioned dovetail guide configuration.
By virtue of the provision of sliding plates at two sides of the slider element and the slider element receiving means respectively at the same time, wherein they are arranged symmetrically and in an L-shape or in a roof shape so that the shape of a dovetail guide means can be achieved, it is particularly advantageously possible to dispense with further, costintensive, linear holding elements. Furthermore, the manufacturing costs can be markedly reduced in comparison with the solutions in the state of the art as fewer components are provided than in the state of the art without in any way adversely affecting the mode of operation of the wedge drive but rather permitting more reliable and more secure operation without the provision of holding elements, but with an extremely high level of motion accuracy.
Advantageously the dovetail-like or prism guide means includes a positively locking connection between the slider element and the slider element receiving means. The provision of such a positively locking connection affords a compact unit, by way of which even high pressing forces can be transmitted without any problem. Furthermore that prevents the slider element and the slider element receiving means from unwantedly sliding out of each other as the positively locking relationship in the region of the dovetail or prism guide means and the mechanical contact between the two portions to be joined of the slider element and the slider element receiving means provides that the forces to be transmitted are in fact transmitted by way of the surfaces which are in contact with each other and which are at an angle relative to each other and in that respect assist with holding the component parts together, by virtue of their angular positioning.
It has further proven to be advantageous if the slider element receiving means is of a protruding configuration in the region of the sliding surfaces and/or the receiving means of the sliding plates. That provides a larger surface for the sliding movement of the slider element with respect to the slider element receiving means so that very good transmission of the pressing forces by way of those enlarged receiving surfaces is possible.
Advantageously the sliding plates can be releasably fixed to the slider element receiving means and/or the slider element, in particular by fixing screws. The releasability of the sliding plates from the slider element receiving means and the slider element respectively means that it is possible to replace them when wear occurs. It will be appreciated that in principle it would also be possible to equip the corresponding sliding surfaces of the slider element receiving means and the slider element in such a way that they can silde against each other, without the interposition of sliding plates. In that case however in the event of wear it would be necessary to replace the slider element receiving means and the slider element themselves so that it has proven to be less expensive and in 3o a operation easier in terms of handling if the arrangement has releasable sliding plates as then replacement thereof is possible quickly and without any problem.
The side of the slider element, which is of a dovetail-like or prismatic shape, advantageously has support surfaces as the sliding surfaces, in particular for the attachment of sliding plates. It has proven to be particularly advantageous in that respect to provide in each case two sliding plates which are arranged at an angle relative to each other as here it is possible to avoid arduous adjustment of four individual sliding plates which are arranged at an angle relative to each other. It is only necessary to implement adjustment at a respective one of the support surfaces for a respective sliding plate so that it is possible to rapidly change sliding plates.
Advantageously a wedge guide means is provided between the slider element and the driver element. That arrangement provides that very high forces can be carried while involving a comparatively small structural space, while at the same time accurate stable guidance for the slider element on the driver element upon movement thereof is possible.
Advantageously the wedge guide means includes two sliding plates arranged at an angle relative to each other. Those sliding plates advantageously comprise a material which assists with the sliding movement, in particular bronze with a solid lubricant. The provision of the sliding plates which are fastened in particular replaceably to the driver and/or slider element provides in a simple fashion that the plates can be replaced in the event of wear while in operation providing for optimum lo sliding movement of the surfaces, which are joined to each other, of the driver element and the slider element.
It has further proven to be advantageous if the dovetail-like or prism guide means and the wedge guide means are provided at an angle relative to each other on the slider element. The arrangement involving a plurality of angles relative to each other means that it is possible to reduce in particular the structural size of the wedge drive, thus affording a compact unit which can be used even with constricted space conditions within a pressing tool.
It is further found to be advantageous if the dovetail-like or prism guide means and the wedge guide means are provided at two mutually adjacent sides of the slider element. That makes it possible to improve the accuracy of movement but at the same time primarily also it is possible to reduce the structural size in comparison with the solutions in the state of the art which usually involve operative engagement on a driver element and operative engagement on the slider element receiving means at two mutually oppositely disposed sides of the slider element.
The slider element can have a third side adjacent to the other two sides, with a receiving means for receiving a processing tool. In that case the third side advantageously has at least two undercut configurations and/or grooves for the insertion of protruding elements of a receiving means for receiving a processing tool. The provision of such a separate receiving means for receiving a processing tool such as for example a perforating punch leads to simple replacement of the tool without any problem as it is only necessary for the receiving means to be removed from the third side of the slider element and replaced by another receiving means which for example carries a different tool. This totally eliminates a tedious procedure of screwing on and unscrewing the processing tool itself, possibly with drilling of further holes in the slider element. The provision of undercut configurations and/or grooves at the third side of the slider element means that the receiving means can be inserted there for example by being pushed into place, in which case further fixing is not even necessary as optimum transmission of force is already guaranteed in particular by virtue of the undercut configurations, due to the positively locking connection afforded thereby.
The invention furthermore concerns a slider element for a wedge drive with a slider element receiving means and a driver element, the slider element being arranged between the slider element receiving means and the driver element, wherein the slider element is provided with a dovetail-like or prismatically formed side with sliding surfaces.
A wedge drive which is also referred to as a slider serves basically for 2o diverting pressing forces to stamping or shaping tools in order thereby to be able to cut, perforate or shape in particular regions of bodywork portions, which are of an inclined or undercut configuration. In that arrangement the wedge drive includes at least one slider element receiving means, a movable slider element and a driver element. The slider element receiving means which has such as rigid is usually connected to apart of the press or the pressing tool, in which press or pressing tool the wedge drive is intended to implement the stamping or shaping operations. A wedge drive is referred to as an upper part slider if the slider element receiving means thereof is fixed in the upper part of the pressing tool, which is connected to the moving pressing ram. Reference is made to a lower part slider if the slider element receiving means thereof is connected to the lower pressing tool which is fixed on the rigid press table. Irrespective of the part to which the slider element receiving means of the wedge drive is connected, it usually has a linear guide means in which the movable slider element is reciprocatable, but as such it is fixedly connected to the slider element receiving means. The driver element is usually in the form of a rigid element fixedly connected to the part of the pressing tool, to which the slider element receiving means is not fastened. The driver element usually has inclined wedge portions and therewith serves as a drive 4o element in relation the movable slider element.
In the situation involving a substantially perpendicular advance movement of a pressing tool, which is referred to as the working stroke, the slider element which is in its rearward position comes to bear against the rigidly standing driver element and supported thereby is advanced by way of the inclined positioning thereof (wedge shape) facing in the working direction. In that situation the inclination of the linear guide means of the slider element receiving means is matched to the inclined positioning of the driver element so that no acceleration of the movable slider element is involved, in relation to the actual pressing speed. The movable slider element is thus only driven by the pressing tool and urged controlledly forwardly or outwardly in order to be able to perform the stamping or shaping work. In the rearward stroke movement in which the pressing tool has moved beyond its bottom dead center position and the two parts are moving away from each other again, the movable slider element is usually pushed back into its original position by means of a suitably designed 1o resilient element, whereupon the procedure can be re-started. The return force required for the return movement of the slider element is usually between 2 and 10% of the actual working force and the weight of the slider element. In that respect, decisive aspects in regard to the magnitude of the pressing force are the dimensions of the surfaces for transmitting the pressure, which are referred to as sliding surfaces, the respective inclinations of the linear guide means in the slider element receiving means and the inclined positioning of the driver element as well as the cooperation of the surfaces and inclinations and the structure of the slider element itself. The pressures to be transmitted are usually between a few 100 kN and several 10,000 kN.
The linear guide means in the slider element receiving means was intended to guide the movable slider element with as little play as possible and in so doing to withstand high pressing forces and afford long service lives. To permit burr-free cutting or perforating of a workpiece a tolerance in terms of accuracy of movement of the movable slider element of a maximum of 0.02 mm is required. If that tolerance is not met, the workpieces which are cut or perforated or shaped in some other way can no longer be placed one upon the other in accurate register relationship so that errors in the basic bodywork structure occur and/or workpieces rubbing against each other means that faster corrosion occurs, the bodywork constructed is of reduced strength and possibly an increased amount of noise is generated by virtue of sheet metal parts which come loose. To avoid all those disadvantages, the requirement in particular in the automobile industry is that a wedge drive provides for extremely high levels of accuracy of movement and permanently withstands the pressing pressures required or makes them available in relation to the stamping or shaping tool.
In order to afford the required accuracy of movement here, various concepts have been developed, of which some are set forth hereinafter. By way of example slider guide means with side sliding plates and driver elements arranged at a right angle as well as a screwed cover plate for holding the slider element are known. Slider guide means of that kind admittedly withstand very high pressing forces and lateral thrust forces but they are very complicated and costly to manufacture as a high level of manual co-ordination complication and expenditure is required for matching the guide play between the elements. A further problem which has been found is inadequate protection in regard to the slider guide means falling apart, in which case the whole of the slider weight plus the rearward attachment forces act on the fastening screws of the cover plate and can very rapidly overload them. In addition such a slider guide means is comparatively large in structural size and is therefore unsuitable for constructing small sliders.
Slider guide means are also known having lateral angle bars and a driver plate arranged at a right angle. Unlike the above-discussed slider guide means the combination of the lateral sliding plates with a cover plate leads to a reduction in the amount of structural space required so that in particular it is also possible as a result to construct smaller slider sizes.
It will be noted however that high forces act on the fastening screws of the angle bars and as a result provide that there is a relatively high risk of accident. In addition the complication and expenditure in terms of coordinating the co-operating elements for matching the guide play is high so that additional costs are also incurred here.
A further kind of slider guide which is used includes lateral sliding and cover plates which are inclined at an angle of 45 . They are therefore arranged approximately in a roof-shaped configuration. That makes it possible to achieve a reduction in structural width as the cover bars and the sliding plates are arranged one over the other and not one beside the other. It will be noted however that the structural space required is still very great so that it is scarcely possible to produce small sliders. In addition the traction forces occurring have a detrimental effect on the fastening screws of the cover plates, and that leads to a high level of process uncertainty.
A further known structure includes a slider guide means with a driver plate and one or two column guide means with bushes in order to hold the slider element laterally and to prevent it from dropping out. The use of a guide column with a driver plate means that admittedly only still comparatively small structural spaces are required and it is possible to achieve considerably less expensive manufacture than when using the above-mentioned solutions in the state of the art. It will be noted however that the column guide means, due to the type of structure involved, is not capable of compensating for high lateral pressures. In addition it cannot carry any heavyweight slider elements so that those slider elements produce less pressing forces and are more susceptible to trouble in the pressing procedure.
A further kind of slider element guide arrangement is known for example from EP 1 035 965 61. This arrangement provides for a clamping embracing relationship in respect of the slider element guide means, wherein the driver element provides a prism guide and sliding plates are inserted between the driver element and the slider element. The roof shape involved means that very high slider forces are possible, while entailing small structural spaces, and equally a very accurate guide play so that the wedge drive or the slider element guide means is stable and has a long working life. It will be noted however that manufacture of the clamping guide means, because of the expensive cutting machining operations required to achieve a precise fitting shape, is really complicated and cost intensive as a result.
Further wedge drives are also known for example from EP 1259371131, DE 198 60 178 C1 and EP 1 197 319 131.
FR-A-2 421 030 discloses a wedge drive of the kind mentioned in the beginning of the description which is used for a work-piece clamping device. The device comprises a base plate (driver element), a ram (slider element receiving means) and a wedge (slider element) located between the base plate and the ram, the wedge having an inclined surface facing the ram, the facing surface of the ram being inclined at the same angle, whereby the wedge is driven by a screw along the base plate for altering the separation between the base plate and the ram. The wedge has a dovetail-shaped projection with sliding surfaces for running in a corresponding groove of the base plate.
A wedge drive of the kind indicated in the beginning of the description is also known from DE 198 61 171 B4 as a radial press comprising an upper press yoke (slider element), a transverse pusher (slider element receiving means) having an inclined surface facing a correspondingly inclined surface of the upper press yoke. A
dovetail-like or T-like guide is provided between the transverse pusher and the upper press yoke including sliding surfaces.
All the above-described design concepts of a slider element guide means for a wedge drive have one or more sliding plates for the transmission of generally high pressing forces, and likewise suitably designed holding elements for holding the slider element in the guide provided for same. The sliding plates serve to permanently transmit the working pressures exerted by the pressing tool from the slider element receiving means and the driver element to the movable slider element and thus to guarantee the actual advancing drive effect. The holding elements serve for linearly holding the slider element on the sliding plates of the sliding element receiving means, in which case they permanently ensure the required accuracy of movement and are intended to possibly compensate for lateral thrust forces which occur in the shaping operation or in the cutting or stamping procedure.
Now the object of the present invention is to further develop a wedge drive in such a way that a guide for the movable slider element is provided, which permits still better motional accuracy than the solutions in the state of the art, which provides for optimum conversion of the pressing force which acts into the stamping or shaping movement, which compensates for lateral thrust forces even better than the state of the art and which provides a longer service life for the wedge drive than is hitherto possible with the solutions in the state of the art. The invention further 5 seeks to provide that a lower level of complication and expenditure is required when co-ordinating the wedge drives and more economical manufacture becomes a possibility.
For a wedge drive, as provided in the present application, that object is attained in 1o the that the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider receiving means to the slider element in a work stroke during which the slider element is moved outwardly between the driver element and the slider element receiving means, are arranged at an angle relative to each other which is bigger than 00 and smaller than 1800.
For a slider element, as provided in the present application, the object is attained in that the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider element receiving means to the slider element in a working stroke during which the slider element is moved outwardly between the 2o driver element and the slider element receiving means, are arranged at an angle relative to each other.
That therefore provides a wedge drive or cotter key in which the movable slider element has a dovetail-like or prismatic side, wherein the slider element receiving means is in the form of a corresponding counterpart portion so that the slider element with its dovetail-like or prismatic side can engage into the slider element receiving means and can be guided and held therein, in the self-centering manner.
The surfaces on the slider element and/or the slider element receiving means, that are respectively provided by the dovetail shape and the prism shape, bear against 3o each other, in which case forces directed in different directions can be carried without any problem by virtue of the surfaces which are at an angle relative to each other, in the dovetail or prism shape. This guide means between the slider element receiving means and the slider element permits self-centering linear guidance for the slider element. The dovetail shape means that, after being inserted into the correspondingly shaped receiving configuration of the slider element receiving means, the movable slider element is safeguarded against falling out or lateral displacement, without further measures.
As guidance for the slider element along the slider element receiving means by virtue of the dovetail guide arrangement is possible with a high degree of precision and without being sensitive to lateral thrust forces as well as being inexpensive to manufacture, without the provision of further components in the form of a linear guide means, the result is a compact wedge drive with a very high level of accuracy of motion, which is also insensitive in relation to manufacturing tolerances.
As clamp guides or further elements are no longer required, not only can the costs be reduced in comparison with the solutions in the state of the art, but the process reliability is also increased and a possible risk of accident reduced. As the slider element only needs to be pushed into the slider element receiving means, assembly of the wedge drive is simplified in comparison with the solutions in the state of the art. It is possible to dispense with a cost-intensive operation of grinding in the guide elements as the prism guides or dovetail guide of the slider element receiving means, the slider element end the driver element are insensitive in relation to tolerances in manufacture. The self-centering effect achieved by the prism guides also leads to a very high level of accuracy in terms of motion in lo regard to carrying lateral thrust forces. By virtue of the compact structure of the wedge drive it is not only suitable for a small structural space available within a pressing tool, but, as will be appreciated, it is also suitable for uses involving larger dimensions.
Advantageously sliding surfaces are provided on the slider elements And or the slider element receiving means. In a particularly preferred feature the dovetail-like or prism guide means includes at least two sliding plates arranged at an angle relative to each other. Advantageously the sliding plates of the dovetail-like or prism guide means can be L-shaped in cross-section. It is further found to be advantageous if sliding plates are provided on all surfaces, which slide against each other, of the slider element and the slider element receiving means, so that in each case at least two sliding plates arranged at an angle relative to each other are provided on the slider element and the slider element receiving means. The sliding plates which are roof-shaped or L-shaped in cross-section can advantageously be so arranged that their inner narrow sides, by virtue of the outwardly inclined oblique positioning of the sliding plates, afford an undercut configuration in the form of the above-mentioned dovetail guide configuration.
By virtue of the provision of sliding plates at two sides of the slider element and the slider element receiving means respectively at the same time, wherein they are arranged symmetrically and in an L-shape or in a roof shape so that the shape of a dovetail guide means can be achieved, it is particularly advantageously possible to dispense with further, costintensive, linear holding elements. Furthermore, the manufacturing costs can be markedly reduced in comparison with the solutions in the state of the art as fewer components are provided than in the state of the art without in any way adversely affecting the mode of operation of the wedge drive but rather permitting more reliable and more secure operation without the provision of holding elements, but with an extremely high level of motion accuracy.
Advantageously the dovetail-like or prism guide means includes a positively locking connection between the slider element and the slider element receiving means. The provision of such a positively locking connection affords a compact unit, by way of which even high pressing forces can be transmitted without any problem. Furthermore that prevents the slider element and the slider element receiving means from unwantedly sliding out of each other as the positively locking relationship in the region of the dovetail or prism guide means and the mechanical contact between the two portions to be joined of the slider element and the slider element receiving means provides that the forces to be transmitted are in fact transmitted by way of the surfaces which are in contact with each other and which are at an angle relative to each other and in that respect assist with holding the component parts together, by virtue of their angular positioning.
It has further proven to be advantageous if the slider element receiving means is of a protruding configuration in the region of the sliding surfaces and/or the receiving means of the sliding plates. That provides a larger surface for the sliding movement of the slider element with respect to the slider element receiving means so that very good transmission of the pressing forces by way of those enlarged receiving surfaces is possible.
Advantageously the sliding plates can be releasably fixed to the slider element receiving means and/or the slider element, in particular by fixing screws. The releasability of the sliding plates from the slider element receiving means and the slider element respectively means that it is possible to replace them when wear occurs. It will be appreciated that in principle it would also be possible to equip the corresponding sliding surfaces of the slider element receiving means and the slider element in such a way that they can silde against each other, without the interposition of sliding plates. In that case however in the event of wear it would be necessary to replace the slider element receiving means and the slider element themselves so that it has proven to be less expensive and in 3o a operation easier in terms of handling if the arrangement has releasable sliding plates as then replacement thereof is possible quickly and without any problem.
The side of the slider element, which is of a dovetail-like or prismatic shape, advantageously has support surfaces as the sliding surfaces, in particular for the attachment of sliding plates. It has proven to be particularly advantageous in that respect to provide in each case two sliding plates which are arranged at an angle relative to each other as here it is possible to avoid arduous adjustment of four individual sliding plates which are arranged at an angle relative to each other. It is only necessary to implement adjustment at a respective one of the support surfaces for a respective sliding plate so that it is possible to rapidly change sliding plates.
Advantageously a wedge guide means is provided between the slider element and the driver element. That arrangement provides that very high forces can be carried while involving a comparatively small structural space, while at the same time accurate stable guidance for the slider element on the driver element upon movement thereof is possible.
Advantageously the wedge guide means includes two sliding plates arranged at an angle relative to each other. Those sliding plates advantageously comprise a material which assists with the sliding movement, in particular bronze with a solid lubricant. The provision of the sliding plates which are fastened in particular replaceably to the driver and/or slider element provides in a simple fashion that the plates can be replaced in the event of wear while in operation providing for optimum lo sliding movement of the surfaces, which are joined to each other, of the driver element and the slider element.
It has further proven to be advantageous if the dovetail-like or prism guide means and the wedge guide means are provided at an angle relative to each other on the slider element. The arrangement involving a plurality of angles relative to each other means that it is possible to reduce in particular the structural size of the wedge drive, thus affording a compact unit which can be used even with constricted space conditions within a pressing tool.
It is further found to be advantageous if the dovetail-like or prism guide means and the wedge guide means are provided at two mutually adjacent sides of the slider element. That makes it possible to improve the accuracy of movement but at the same time primarily also it is possible to reduce the structural size in comparison with the solutions in the state of the art which usually involve operative engagement on a driver element and operative engagement on the slider element receiving means at two mutually oppositely disposed sides of the slider element.
The slider element can have a third side adjacent to the other two sides, with a receiving means for receiving a processing tool. In that case the third side advantageously has at least two undercut configurations and/or grooves for the insertion of protruding elements of a receiving means for receiving a processing tool. The provision of such a separate receiving means for receiving a processing tool such as for example a perforating punch leads to simple replacement of the tool without any problem as it is only necessary for the receiving means to be removed from the third side of the slider element and replaced by another receiving means which for example carries a different tool. This totally eliminates a tedious procedure of screwing on and unscrewing the processing tool itself, possibly with drilling of further holes in the slider element. The provision of undercut configurations and/or grooves at the third side of the slider element means that the receiving means can be inserted there for example by being pushed into place, in which case further fixing is not even necessary as optimum transmission of force is already guaranteed in particular by virtue of the undercut configurations, due to the positively locking connection afforded thereby.
The third side of the slider element can also be provided with at least one wedge surface, in which case the receiving means then preferably has a corresponding wedge surface to provide a positively locking connection between the slider element and the receiving means for the processing tool. Lateral thrust forces can be carried thereby and the transmission of force can be optimised.
During the working stroke the slider element is moved outwardly between the lo sliding surfaces, which are arranged in wedge form, of the driver element and the slider element receiving means, in which case the slider element receiving means and the driver element are movable towards each other perpendicularly, driven by the pressing stroke. The pressing force applied by the pressing tool corresponds in that respect to the counteracting force which the wedge drive applies for the work done by it, for example cutting, perforating or post-shaping a bodywork portion, wherein that is distributed to the sliding surfaces in dependence on the respective angular position of the individual sliding surfaces relative to each other. Due to the provision of sliding surfaces which are arranged at an angle relative to each other and which 2o are arranged in a roof shape or a prism shape relative to each other, the movable slider element is automatically centered between the slider element receiving means and the driver element or on the sliding surfaces thereof. That can provide a very high level of motion accuracy and lateral guidance for the slider element, while manufacturing tolerances or other inaccuracies caused by manufacture can be compensated and thus no longer have an adverse influence.
In the return motion of the slider element, referred to as the rearward strake, in which the pressing tool moves away from each other 3o and thus the slider element receiving means is moved away from the driver element, the slider element is retracted into the region between the slider element receiving means and the driver element. The forces acting on the slider element in the rearward stroke or in the return motion are restricted only by the weight of the slider element and the retraction forces acting on the slider element receiving means, the slider element and the driver element, as the pressing tool moves apart. The sliding surfaces of the slider element and the slider guide element, which run against each other in that situation, can be reduced in their dimensions in relation to the sliding surfaces which run against each other in the working stroke, so that the above-mentioned L-shape for the sliding surfaces on the dovetail guide means is found to be highly suitable in that respect.
In the case of a suspended upper part slider or wedge drive the weight of the slider element acts on the surfaces of the slider element receiving means, which bear in positively locking relationship against the slider element sliding surfaces of the dovetail guide arrangement, and exerts a downwardly directed spreading force on those surfaces of the sliding element receiving means. By virtue of the positively locking shoulder support for the slider element with respect to the slider element receiving means however those lateral thrust forces are compensated so that permanent and stable fixing of the slider element to the slider element 5 receiving means and the sliding plates on the slider element and the slider element receiving means is possible. Therefore the fixing screws of the sliding plates are not subject to any forces such as to damage them, in particular tensile forces.
lo The prism guide means or the dovetail-like guide means provided between the slider element and the slider element receiving means can thus be used to equip small, medium and large-format wedge drives, thus affording a large range of uses. Embodiments by way of example will be described in greater detail hereinafter to describe the invention more fully, with reference to the drawings in which:
Figure 1 shows a vertical cross-sectional view through a first embodiment of a wedge drive according to the invention with dovetail-like guide means, 2o Figure 2 shows a perspective view of the slider element receiving means and the slider element of the wedge drive of Figure 1, Figure 3 shows a perspective exploded view of the slider element receiving means and the slider element of Figure 2, Figure 4 shows a perspective view of a second embodiment of a wedge drive according to the invention with dovetail-like guide means between the slider element and the slider element receiving means, Figure 5 shows a perspective view of the wedge drive of Figure 4 without a driver element, Figure 6 shows a perspective side view of the wedge drive of Figure 4, Figure 7 shows a lateral plan view of the wedge drive of Figure 4, Figure 8 shows a sectional side view of the wedge drive of Figure 4, Figure 9 shows a perspective view inclinedly from above of the wedge drive shown in Figure 4 with fitted receiving means for a processing tool, Figure 10 shows a perspective view of the wedge drive provided with a receiving means for a processing tool as shown in Figure 9 with the driver element removed, and Figure 11 shows a perspective view of the wedge drive of Figure 10 with the receiving means for a processing tool removed and with the driver element removed.
Figure 1 shows a sectional view of a wedge drive 1 or cotter key comprising a slider element receiving means 2, a slider element 3 and a receiving means 4 for receiving a processing tool. A driver element connected to the slider element 3 is not visible in Figure 1 but can be found in the perspective view in Figure 4.
The slider element and the slider element receiving means are connected together by way of a dovetail-like or prism guide means 6. In this case the slider element 3 has a portion 30 of a dovetail-like configuration. It includes two sliding surfaces 31, 32, 33, 34 which are respectively disposed at an angle to each other on both sides. In this arrangement the two sliding surfaces 31 and 33 are smaller than the two sliding surfaces 32 and 34. The reason for this is that, in a working stroke, the pressing forces exerted by a pressing tool in which the wedge drive is arranged are transmitted from the slider receiving means to the slider 1 o element by way of the sliding surfaces 32, 34. In a return motion or a rearward strake movement of the pressing tool the slider element is retracted by way of the two sliding surfaces 31, 33, in which case a very much lesser force is exerted on the slider element so that those smaller dimensions for the sliding surfaces are adequate.
The slider element receiving means 2 has a portion 20 which is of a correspondingly opposite and equal configuration and which includes corresponding sliding surfaces 21 through 24 which each bear in positively locking relationship against the sliding surfaces 31 through 34. In addition the portion 30 of a dovetail-like configuration engages with a protruding portion 35 into a corresponding recess 25 in positively locking relationship in the slider element receiving means 2. The protruding portion 35 can only extend over apart of the longitudinal extent of the slider element and the slider element receiving means respectively.
In principle it is also possible not to provide such a protruding portion, in which case however the hold of the slider element and the slider element receiving means to each other is markedly improved by such a protruding portion 35 which engages in positively locking relationship into a corresponding recess 25 of the slider element receiving means.
As can further be seen from Figure 1, sliding plates are provided on the slider element receiving means and the slider element to form the corresponding sliding surfaces 21 through 24, and 31 through 34 respectively. The sliding plates 26, 27 on the slider element receiving means 2 are of an L-shaped cross-section in cross-section, whereas individual flat sliding plates 36, 37, 38, 39 are attached to the corresponding surfaces of the slider element, as can be better seen from Figure 3. The L-shaped sliding plates 26, 27 are fixed to the slider element 4o receiving means by fixing screws 28, 29. The sliding plates 36 through 39 are also fixed to the slider element by corresponding fixing screws, although these are not shown in Figure 1.
The provision of such a releasable fixing for the sliding plates to the slider element receiving means and the slider element respectively permits the sliding plates to be replaced without any problem, when wear is involved. The fixing screws are arranged in sunk relationship in the sliding plates so that the sliding movement of the sliding surfaces against each other is not impeded by the provision of the fixing screws.
As can be clearly seen in particular from the cross-sectional view in Figure 1 the slider element receiving means protrudes outwardly in the region of the dovetail-like guide means to provide a sufficiently large sliding surface 22, 24 for support and sliding movement on the slider element 3.
As can be further seen from Figure 1 the receiving means 4, for 1o receiving a processing tool, is provided with a T-shaped protrusion 40 and the slider element 3 is provided with a corresponding T-shaped groove 41.
By virtue of that arrangement the receiving means far the processing tool can be easily pushed into the T-shaped groove 41, whereby simple fixing and a secure hold on the slider element is possible. Instead of a T-shaped groove and a T-shaped protrusion, it is also possible to provide a wedge shape with corresponding grooves and protrusions in that region so that in addition it is also possible to provide a centering action and to provide for carrying lateral thrust forces in that region. As however there is no provision for movement of the slider element with respect to the receiving means, in most cases it is sufficient to provide the T-shaped groove and the T-shaped protrusion.
Figure 2 shows a perspective view of the detail of the slider element receiving means and the slider element, viewed inclinedly from below. The two are shown separately so that it is possible to view the sliding plates 26, 27 of the slider element receiving means 2 and the dovetail-shaped portion 20 of the slider element receiving means. In addition it is also possible to clearly see the portion 30 of the slider element, which is of a dovetail-like configuration, and also the sliding plates secured thereto, the fixing thereof 3o by screws also being indicated. As can be even better seen from the perspective exploded view in Figure 3 the respective sliding plates are fixed to the slider element receiving means and the slider element respectively by three fixing screws. The sliding plates have corresponding bores for receiving the fixing screws.
Figures 2 and 3 also show a wedge-shaped receiving surface 300 for connection to the driver element 5 which is to be seen in Figure 4. The wedge-shaped receiving surface 300 is divided into two and has two sliding surfaces 301, 302, to which respective sliding plates are attached, although the sliding plates are not to be seen in Figures 2 and 3. The wedge-shaped receiving surface 300 is at an angle both to the dovetail-shaped portion 30 and also the side with the T-shaped groove 41 for receiving the receiving means for the processing tool, thus affording an extremely compact structural shape far the slider element, substantially without unused side surfaces. That can also be seen in particular from the perspective view of the assembled wedge drive 1 shown in Figure 4, in which the slider element receiving means, the slider element, the driver element and the receiving means for the processing tool are assembled. It can also be seen in that respect that the driver element and the slider element are connected together by positively acting return clamps 7. They serve for better entrainment of the slider element In the rearward strake movement of the pressing tool. The positively acting return clamps 7 engage both on the slider element and also the driver element, in openings, recesses or grooves provided there.
It can be clearly seen from Figure 5 that the positively acting return 1o clamps 7, for that purpose, have protruding portions 70 which can engage into corresponding grooves in the driver element. It can also be seen from Figure 5 that sliding plates 303, 304 are fixed on the sliding surfaces 301, 302 by way of fixing screws 305.
The perspective view of the wedge drive 1 in Figure 6, which is turned through 900 relative to the view in Figure 4, shows a view on to the receiving means 4 for receiving a processing tool. It will be seen in that respect that the receiving means 4 is provided with a corresponding wedge surface comprising two sliding surfaces 43, 44 which can slide on a corresponding wedge portion 50 of the driver element 5.
It can be even better seen from the side view of the wedge drive 1 shown in Figure 7 that the portion 30 of a dovetail-like configuration, the wedge-shaped receiving surface 300 and the third side with the T-shaped groove 41 for receiving the receiving means 4 for the processing tool of the slider element 3 are respectively arranged at an angle relative to each other. Each of the sides of the slider element is also at an angle relative to the vertical or the horizontal respectively which are indicated by broken lines 8, 9 in Figure 7. Here once again it is possible to clearly see the extremely compact structural form of the wedge drive.
The corresponding side view in section of the wedge drive 1 shown in Figure 8 additionally shows a spring element 10 in the form of a gas pressure spring. It serves to retract the slider element back into its starting position in the rearward stroke movement of the pressing tool. That facilitates the retraction movement of the slider element in the rearward stroke movement so that a working stroke can be more rapidly performed again. Depending on the respective configuration of the wedge drive however it would even be possible to omit such a spring element, in particular when positively acting return devices of a special design in the form of the positively acting return clamps 7, for example in the form of positively acting returning devices with rolling frictional elements, are provided.
It can also be clearly seen once again from the perspective view on to the wedge drive 1 of Figure 9 that the slider element is of an extremely compact configuration by virtue of a suitable arrangement of its three sides with a portion of a dovetail-like configuration for engagement into the slider element receiving means, the T-shaped groove for receiving the receiving means 4 for the processing tool and the wedge-shaped receiving surface for co-operation with the driver element 5.
The perspective view of the wedge drive 1 from below with the driver element 5 removed, as shown in Figure 10, shows that the sliding plates 303, 304 can be of such a length that they also engage under the sliding surfaces 43, 44 of the wedge surface 42 of the receiving means 4 for the 1 o processing tool, that is to say no further sliding plates are provided here, but only the sliding plates 303, 304, so that this arrangement provides a unitary surface for co-operation with the corresponding wedge portion 50 of the driver element 5.
The sliding plates 303, 304, with the receiving means for the processing tool removed, can be seen once again from the perspective view of the wedge drive 1 from above as shown in Figure 11. It is also evident in this respect that suitable fixing to the receiving means for the processing tool is afforded by the provision of a bore 305 in the sliding plates 303, 304 2o and a corresponding fixing screw which however is not shown in Figure 11.
By way thereof, fixing of the receiving means 4 far the processing tool to the slider element can be still further improved and an even more stable unit is afforded.
The above-mentioned sliding plates on the slider element and the driver element as well as the slider element receiving means preferably comprise bronze with a solid lubricant to permit particularly good sliding motion of the corresponding pairs of sliding components against each other. It will be appreciated that in principle it is also possible to use other materials far the sliding plates, wherein a low level of friction in the surfaces which slide against each other means that particularly optimum movement of the slider element within the wedge drive is possible in the working stroke and the rearward stroke of the pressing tool in which the wedge drive is disposed.
Besides the embodiments described hereinbefore and illustrated in the Figures for wedge drives having a dovetail-like or prism guide means, it is also possible to form numerous further embodiments in which dovetail shaped sliding surfaces are provided between the slider element receiving means and the slider element or prism guides are provided between the slider element and the driver element and the slider element receiving means and the slider element. That markedly improves the respective accuracy of movement of the slider element between the slider element receiving means and the driver element in comparison with the state of the art, lateral thrust forces are absorbed and manufacturing tolerances on the slider element receiving means, the slider element and the guide element are compensated. The provision of only one dovetail-like or prism guide means between the slider element receiving means and the slider element makes it possible to save on further components which assist with the guidance action, and thus manufacture of the wedge drive can be markedly less expensive than in the state of the art.
List of references 1 wedge drive 2 slider element receiving means 3 slider element 4 receiving means for processing tool 5 driver element 6 dovetail-like or prism guide means l0 7 positively acting return clamp 8 vertical line 9 horizontal line spring element (gas pressure spring) portion 15 21 sliding surface 22 sliding surface 23 sliding surface 24 sliding surface recess 20 26 L-shaped sliding plate 27 L-shaped sliding plate 28 fixing screw 29 fixing screw portion of dovetail-like configuration 25 31 sliding surface 32 sliding surface 33 sliding surface 34 sliding surface protruding portion 30 36 sliding plate 37 sliding plate 38 sliding plate 39 sliding plate T-shaped protrusion 35 41 T-shaped groove 42 wedge surface 43 sliding surface 44 sliding surface wedge portion 4o 70 protruding portion 300 wedge-shaped receiving surface 301 sliding surface 302 sliding surface 303 sliding surface 45 304 sliding plate 305 bore
During the working stroke the slider element is moved outwardly between the lo sliding surfaces, which are arranged in wedge form, of the driver element and the slider element receiving means, in which case the slider element receiving means and the driver element are movable towards each other perpendicularly, driven by the pressing stroke. The pressing force applied by the pressing tool corresponds in that respect to the counteracting force which the wedge drive applies for the work done by it, for example cutting, perforating or post-shaping a bodywork portion, wherein that is distributed to the sliding surfaces in dependence on the respective angular position of the individual sliding surfaces relative to each other. Due to the provision of sliding surfaces which are arranged at an angle relative to each other and which 2o are arranged in a roof shape or a prism shape relative to each other, the movable slider element is automatically centered between the slider element receiving means and the driver element or on the sliding surfaces thereof. That can provide a very high level of motion accuracy and lateral guidance for the slider element, while manufacturing tolerances or other inaccuracies caused by manufacture can be compensated and thus no longer have an adverse influence.
In the return motion of the slider element, referred to as the rearward strake, in which the pressing tool moves away from each other 3o and thus the slider element receiving means is moved away from the driver element, the slider element is retracted into the region between the slider element receiving means and the driver element. The forces acting on the slider element in the rearward stroke or in the return motion are restricted only by the weight of the slider element and the retraction forces acting on the slider element receiving means, the slider element and the driver element, as the pressing tool moves apart. The sliding surfaces of the slider element and the slider guide element, which run against each other in that situation, can be reduced in their dimensions in relation to the sliding surfaces which run against each other in the working stroke, so that the above-mentioned L-shape for the sliding surfaces on the dovetail guide means is found to be highly suitable in that respect.
In the case of a suspended upper part slider or wedge drive the weight of the slider element acts on the surfaces of the slider element receiving means, which bear in positively locking relationship against the slider element sliding surfaces of the dovetail guide arrangement, and exerts a downwardly directed spreading force on those surfaces of the sliding element receiving means. By virtue of the positively locking shoulder support for the slider element with respect to the slider element receiving means however those lateral thrust forces are compensated so that permanent and stable fixing of the slider element to the slider element 5 receiving means and the sliding plates on the slider element and the slider element receiving means is possible. Therefore the fixing screws of the sliding plates are not subject to any forces such as to damage them, in particular tensile forces.
lo The prism guide means or the dovetail-like guide means provided between the slider element and the slider element receiving means can thus be used to equip small, medium and large-format wedge drives, thus affording a large range of uses. Embodiments by way of example will be described in greater detail hereinafter to describe the invention more fully, with reference to the drawings in which:
Figure 1 shows a vertical cross-sectional view through a first embodiment of a wedge drive according to the invention with dovetail-like guide means, 2o Figure 2 shows a perspective view of the slider element receiving means and the slider element of the wedge drive of Figure 1, Figure 3 shows a perspective exploded view of the slider element receiving means and the slider element of Figure 2, Figure 4 shows a perspective view of a second embodiment of a wedge drive according to the invention with dovetail-like guide means between the slider element and the slider element receiving means, Figure 5 shows a perspective view of the wedge drive of Figure 4 without a driver element, Figure 6 shows a perspective side view of the wedge drive of Figure 4, Figure 7 shows a lateral plan view of the wedge drive of Figure 4, Figure 8 shows a sectional side view of the wedge drive of Figure 4, Figure 9 shows a perspective view inclinedly from above of the wedge drive shown in Figure 4 with fitted receiving means for a processing tool, Figure 10 shows a perspective view of the wedge drive provided with a receiving means for a processing tool as shown in Figure 9 with the driver element removed, and Figure 11 shows a perspective view of the wedge drive of Figure 10 with the receiving means for a processing tool removed and with the driver element removed.
Figure 1 shows a sectional view of a wedge drive 1 or cotter key comprising a slider element receiving means 2, a slider element 3 and a receiving means 4 for receiving a processing tool. A driver element connected to the slider element 3 is not visible in Figure 1 but can be found in the perspective view in Figure 4.
The slider element and the slider element receiving means are connected together by way of a dovetail-like or prism guide means 6. In this case the slider element 3 has a portion 30 of a dovetail-like configuration. It includes two sliding surfaces 31, 32, 33, 34 which are respectively disposed at an angle to each other on both sides. In this arrangement the two sliding surfaces 31 and 33 are smaller than the two sliding surfaces 32 and 34. The reason for this is that, in a working stroke, the pressing forces exerted by a pressing tool in which the wedge drive is arranged are transmitted from the slider receiving means to the slider 1 o element by way of the sliding surfaces 32, 34. In a return motion or a rearward strake movement of the pressing tool the slider element is retracted by way of the two sliding surfaces 31, 33, in which case a very much lesser force is exerted on the slider element so that those smaller dimensions for the sliding surfaces are adequate.
The slider element receiving means 2 has a portion 20 which is of a correspondingly opposite and equal configuration and which includes corresponding sliding surfaces 21 through 24 which each bear in positively locking relationship against the sliding surfaces 31 through 34. In addition the portion 30 of a dovetail-like configuration engages with a protruding portion 35 into a corresponding recess 25 in positively locking relationship in the slider element receiving means 2. The protruding portion 35 can only extend over apart of the longitudinal extent of the slider element and the slider element receiving means respectively.
In principle it is also possible not to provide such a protruding portion, in which case however the hold of the slider element and the slider element receiving means to each other is markedly improved by such a protruding portion 35 which engages in positively locking relationship into a corresponding recess 25 of the slider element receiving means.
As can further be seen from Figure 1, sliding plates are provided on the slider element receiving means and the slider element to form the corresponding sliding surfaces 21 through 24, and 31 through 34 respectively. The sliding plates 26, 27 on the slider element receiving means 2 are of an L-shaped cross-section in cross-section, whereas individual flat sliding plates 36, 37, 38, 39 are attached to the corresponding surfaces of the slider element, as can be better seen from Figure 3. The L-shaped sliding plates 26, 27 are fixed to the slider element 4o receiving means by fixing screws 28, 29. The sliding plates 36 through 39 are also fixed to the slider element by corresponding fixing screws, although these are not shown in Figure 1.
The provision of such a releasable fixing for the sliding plates to the slider element receiving means and the slider element respectively permits the sliding plates to be replaced without any problem, when wear is involved. The fixing screws are arranged in sunk relationship in the sliding plates so that the sliding movement of the sliding surfaces against each other is not impeded by the provision of the fixing screws.
As can be clearly seen in particular from the cross-sectional view in Figure 1 the slider element receiving means protrudes outwardly in the region of the dovetail-like guide means to provide a sufficiently large sliding surface 22, 24 for support and sliding movement on the slider element 3.
As can be further seen from Figure 1 the receiving means 4, for 1o receiving a processing tool, is provided with a T-shaped protrusion 40 and the slider element 3 is provided with a corresponding T-shaped groove 41.
By virtue of that arrangement the receiving means far the processing tool can be easily pushed into the T-shaped groove 41, whereby simple fixing and a secure hold on the slider element is possible. Instead of a T-shaped groove and a T-shaped protrusion, it is also possible to provide a wedge shape with corresponding grooves and protrusions in that region so that in addition it is also possible to provide a centering action and to provide for carrying lateral thrust forces in that region. As however there is no provision for movement of the slider element with respect to the receiving means, in most cases it is sufficient to provide the T-shaped groove and the T-shaped protrusion.
Figure 2 shows a perspective view of the detail of the slider element receiving means and the slider element, viewed inclinedly from below. The two are shown separately so that it is possible to view the sliding plates 26, 27 of the slider element receiving means 2 and the dovetail-shaped portion 20 of the slider element receiving means. In addition it is also possible to clearly see the portion 30 of the slider element, which is of a dovetail-like configuration, and also the sliding plates secured thereto, the fixing thereof 3o by screws also being indicated. As can be even better seen from the perspective exploded view in Figure 3 the respective sliding plates are fixed to the slider element receiving means and the slider element respectively by three fixing screws. The sliding plates have corresponding bores for receiving the fixing screws.
Figures 2 and 3 also show a wedge-shaped receiving surface 300 for connection to the driver element 5 which is to be seen in Figure 4. The wedge-shaped receiving surface 300 is divided into two and has two sliding surfaces 301, 302, to which respective sliding plates are attached, although the sliding plates are not to be seen in Figures 2 and 3. The wedge-shaped receiving surface 300 is at an angle both to the dovetail-shaped portion 30 and also the side with the T-shaped groove 41 for receiving the receiving means for the processing tool, thus affording an extremely compact structural shape far the slider element, substantially without unused side surfaces. That can also be seen in particular from the perspective view of the assembled wedge drive 1 shown in Figure 4, in which the slider element receiving means, the slider element, the driver element and the receiving means for the processing tool are assembled. It can also be seen in that respect that the driver element and the slider element are connected together by positively acting return clamps 7. They serve for better entrainment of the slider element In the rearward strake movement of the pressing tool. The positively acting return clamps 7 engage both on the slider element and also the driver element, in openings, recesses or grooves provided there.
It can be clearly seen from Figure 5 that the positively acting return 1o clamps 7, for that purpose, have protruding portions 70 which can engage into corresponding grooves in the driver element. It can also be seen from Figure 5 that sliding plates 303, 304 are fixed on the sliding surfaces 301, 302 by way of fixing screws 305.
The perspective view of the wedge drive 1 in Figure 6, which is turned through 900 relative to the view in Figure 4, shows a view on to the receiving means 4 for receiving a processing tool. It will be seen in that respect that the receiving means 4 is provided with a corresponding wedge surface comprising two sliding surfaces 43, 44 which can slide on a corresponding wedge portion 50 of the driver element 5.
It can be even better seen from the side view of the wedge drive 1 shown in Figure 7 that the portion 30 of a dovetail-like configuration, the wedge-shaped receiving surface 300 and the third side with the T-shaped groove 41 for receiving the receiving means 4 for the processing tool of the slider element 3 are respectively arranged at an angle relative to each other. Each of the sides of the slider element is also at an angle relative to the vertical or the horizontal respectively which are indicated by broken lines 8, 9 in Figure 7. Here once again it is possible to clearly see the extremely compact structural form of the wedge drive.
The corresponding side view in section of the wedge drive 1 shown in Figure 8 additionally shows a spring element 10 in the form of a gas pressure spring. It serves to retract the slider element back into its starting position in the rearward stroke movement of the pressing tool. That facilitates the retraction movement of the slider element in the rearward stroke movement so that a working stroke can be more rapidly performed again. Depending on the respective configuration of the wedge drive however it would even be possible to omit such a spring element, in particular when positively acting return devices of a special design in the form of the positively acting return clamps 7, for example in the form of positively acting returning devices with rolling frictional elements, are provided.
It can also be clearly seen once again from the perspective view on to the wedge drive 1 of Figure 9 that the slider element is of an extremely compact configuration by virtue of a suitable arrangement of its three sides with a portion of a dovetail-like configuration for engagement into the slider element receiving means, the T-shaped groove for receiving the receiving means 4 for the processing tool and the wedge-shaped receiving surface for co-operation with the driver element 5.
The perspective view of the wedge drive 1 from below with the driver element 5 removed, as shown in Figure 10, shows that the sliding plates 303, 304 can be of such a length that they also engage under the sliding surfaces 43, 44 of the wedge surface 42 of the receiving means 4 for the 1 o processing tool, that is to say no further sliding plates are provided here, but only the sliding plates 303, 304, so that this arrangement provides a unitary surface for co-operation with the corresponding wedge portion 50 of the driver element 5.
The sliding plates 303, 304, with the receiving means for the processing tool removed, can be seen once again from the perspective view of the wedge drive 1 from above as shown in Figure 11. It is also evident in this respect that suitable fixing to the receiving means for the processing tool is afforded by the provision of a bore 305 in the sliding plates 303, 304 2o and a corresponding fixing screw which however is not shown in Figure 11.
By way thereof, fixing of the receiving means 4 far the processing tool to the slider element can be still further improved and an even more stable unit is afforded.
The above-mentioned sliding plates on the slider element and the driver element as well as the slider element receiving means preferably comprise bronze with a solid lubricant to permit particularly good sliding motion of the corresponding pairs of sliding components against each other. It will be appreciated that in principle it is also possible to use other materials far the sliding plates, wherein a low level of friction in the surfaces which slide against each other means that particularly optimum movement of the slider element within the wedge drive is possible in the working stroke and the rearward stroke of the pressing tool in which the wedge drive is disposed.
Besides the embodiments described hereinbefore and illustrated in the Figures for wedge drives having a dovetail-like or prism guide means, it is also possible to form numerous further embodiments in which dovetail shaped sliding surfaces are provided between the slider element receiving means and the slider element or prism guides are provided between the slider element and the driver element and the slider element receiving means and the slider element. That markedly improves the respective accuracy of movement of the slider element between the slider element receiving means and the driver element in comparison with the state of the art, lateral thrust forces are absorbed and manufacturing tolerances on the slider element receiving means, the slider element and the guide element are compensated. The provision of only one dovetail-like or prism guide means between the slider element receiving means and the slider element makes it possible to save on further components which assist with the guidance action, and thus manufacture of the wedge drive can be markedly less expensive than in the state of the art.
List of references 1 wedge drive 2 slider element receiving means 3 slider element 4 receiving means for processing tool 5 driver element 6 dovetail-like or prism guide means l0 7 positively acting return clamp 8 vertical line 9 horizontal line spring element (gas pressure spring) portion 15 21 sliding surface 22 sliding surface 23 sliding surface 24 sliding surface recess 20 26 L-shaped sliding plate 27 L-shaped sliding plate 28 fixing screw 29 fixing screw portion of dovetail-like configuration 25 31 sliding surface 32 sliding surface 33 sliding surface 34 sliding surface protruding portion 30 36 sliding plate 37 sliding plate 38 sliding plate 39 sliding plate T-shaped protrusion 35 41 T-shaped groove 42 wedge surface 43 sliding surface 44 sliding surface wedge portion 4o 70 protruding portion 300 wedge-shaped receiving surface 301 sliding surface 302 sliding surface 303 sliding surface 45 304 sliding plate 305 bore
Claims (21)
1. A wedge drive comprising a slider element receiving means a movable slider element and a driver element, wherein sliding surfaces are provided between the slider element and the driver element, wherein a dovetail-like or prism guide with sliding surfaces provided at the slider element and sliding surfaces provided at the slider element receiving means is arranged between the slider element and the slider element receiving means, wherein the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider element receiving means to the slider element in a working stroke during which the slider element is moved outwardly between the driver element and the slider element receiving means, are arranged at an angle relative to each other.
2. A wedge drive as set forth in claim 1, wherein the sliding surfaces, by way of which forces are transmitted in the working stroke are bigger than the sliding surfaces provided on the slider element by way of which forces are transmitted from the slider element receiving means to the slider element in a rearward stroke during which the slider element receiving means is moved away from the driver element.
3. A wedge drive according to claim 1 or 2, wherein the dovetail-like or prism guide includes at least two sliding plates arranged at an angle relative to each other.
4. A wedge drive as set forth in claim 3, wherein the sliding plates of the dovetail-like or prism guide are generally L-shaped in cross-section.
5. A wedge drive as set forth in claim 3 or claim 4, wherein each case sliding plates arranged at an angle to each other are provided.
6. A wedge drive as set forth in any one of claims 1 to 5, wherein the dovetail-like or prism guide includes a positively locking connection between the slider element and the slider element receiving means.
7. A wedge drive as set forth in claim 3, wherein the slider element receiving means is of a protruding configuration in the region of the sliding surfaces and/or the receiving portion of the sliding plates.
8. A wedge drive as set forth in claim 3, wherein the sliding plates are releasably fixed to the slider element receiving means and/or the slider element, in particular by fixing screws.
9. A wedge drive set forth in claim 1 or claim 2, wherein a wedge guide is provided between the slider element and the driver element.
10. A wedge drive as set forth in claim 9, wherein the wedge guide includes two sliding plates arranged at an angle relative to each other.
11. A wedge drive as set forth in claim 9 or claim 10, wherein the dovetail-like or prism guide and the wedge guide are provided at an angle relative to each other on the slider element.
12. A wedge drive as set forth in any one of claims 9 to 11, wherein the dovetail-like or prism guide and the wedge guide are provided at two mutually adjacent sides of the slider element.
13. A slider element for a wedge drive furthermore comprising a slider element receiving means and a driver element, the slider element being arranged between the slider element receiving means and the driver element, wherein the slider element has a dovetail-like or prismatically shaped side with sliding surfaces, wherein the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider element receiving means to the slider element in a working stroke during which the slider element is moved outwardly between the driver element and the slider element receiving means, are arranged at an angle relative to each other.
14. A slider element according to claim 13, wherein the sliding surfaces provided on the slider element, by way of which forces are transmitted in the working stroke are bigger than the sliding surfaces provided on the slider element, by way of which forces are transmitted from the slider element receiving means to the slider element in a rearward stroke during which the slider element receiving means is moved away from the driver element.
15. A slider element as set forth in claim 13 or 14, wherein the dovetail-like or prismatically shaped side has contact surfaces as sliding plates in particular for the attachment of sliding plates.
16. A slider element as set forth in claim 15, wherein there are provided two respective sliding plates arranged at an angle relative to each other.
17. A slider element as set forth in one of the claims 13 to 16, characterized in that provided in adjacent relationship with the first dovetail-like or prismatically shaped side is a second side having at least one wedge guide surface for connection to a driver element.
18. A slider element as set forth in claim 17, wherein there is provided at least one sliding plate for attachment to the at least one wedge guide surface.
19. A slider element as set forth in one of the claims 13 to 17, wherein the slider element has a third side adjacent to the other two sides, having a receiving portion for receiving a processing tool.
20. A slider element as set forth in claim 19, wherein the third side has at least two undercut configurations and/or grooves for the insertion of protruding elements of a receiving means for a processing tool.
21. A slider element as set forth in claim 19 or claim 20, wherein the third side is provided with at least one wedge surface.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102007045703A DE102007045703A1 (en) | 2007-09-24 | 2007-09-24 | Wedge drive with slide holder |
| DE102007045703.2 | 2007-09-24 | ||
| PCT/EP2008/000742 WO2009039895A1 (en) | 2007-09-24 | 2008-01-31 | Wedge drive with slide receptacle |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2700576A1 CA2700576A1 (en) | 2009-04-02 |
| CA2700576C true CA2700576C (en) | 2012-11-20 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA2700576A Expired - Fee Related CA2700576C (en) | 2007-09-24 | 2008-01-31 | Wedge drive with slider receiving means |
Country Status (13)
| Country | Link |
|---|---|
| EP (1) | EP2197660B1 (en) |
| JP (1) | JP5230743B2 (en) |
| KR (1) | KR101230185B1 (en) |
| CN (1) | CN101848805B (en) |
| BR (1) | BRPI0817324B1 (en) |
| CA (1) | CA2700576C (en) |
| DE (1) | DE102007045703A1 (en) |
| ES (1) | ES2553582T3 (en) |
| MX (1) | MX2010003031A (en) |
| PL (1) | PL2197660T3 (en) |
| RU (1) | RU2461463C2 (en) |
| UA (1) | UA97863C2 (en) |
| WO (1) | WO2009039895A1 (en) |
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| ES2517390T3 (en) * | 2011-05-26 | 2014-11-03 | Werkzeugmaschinen Gmbh + Co. Kg | Machine tool in the form of a press for the treatment of work pieces, especially metal sheets |
| EP2551097A1 (en) * | 2011-07-28 | 2013-01-30 | Osterwalder AG | Powder press |
| DE102012014546A1 (en) | 2012-07-21 | 2014-01-23 | Strack Norma Gmbh & Co. Kg | cotter |
| DE102015103112B4 (en) | 2014-03-06 | 2019-10-10 | voestalpine Gießerei Linz GmbH | tool pusher |
| DE102014102993B4 (en) | 2014-03-06 | 2016-05-12 | Voestalpine Giesserei Linz Gmbh | tool pusher |
| JP2017507036A (en) * | 2014-03-06 | 2017-03-16 | フェストアルピネ・ギーセライ・リンツ・ゲー・エム・ベー・ハー | Tool slide |
| JP2017507035A (en) | 2014-03-06 | 2017-03-16 | フェストアルピネ・ギーセライ・リンツ・ゲー・エム・ベー・ハー | Tool slide |
| DE102015100659B4 (en) * | 2015-01-19 | 2023-01-05 | Fft Produktionssysteme Gmbh & Co. Kg | Flanging system, flanging unit and flanging process for self-sufficient flanging |
| WO2017005875A1 (en) * | 2015-07-07 | 2017-01-12 | Voestalpine Giesserei Linz Gmbh | V-drive and slide element for the same |
| DE202015106966U1 (en) * | 2015-12-21 | 2016-01-28 | Harald Weigelt | cotter |
| CN106140993B (en) * | 2016-08-23 | 2018-01-05 | 优德精密工业（昆山）股份有限公司 | A kind of device for improving wedge service life |
| WO2018074051A1 (en) * | 2016-10-19 | 2018-04-26 | 三協オイルレス工業株式会社 | Cam device |
| DE202017100989U1 (en) | 2017-02-22 | 2017-04-21 | Fibro Gmbh | Wedge drive with optimized guidance |
| JP6321313B1 (en) * | 2018-01-05 | 2018-05-09 | 三協オイルレス工業株式会社 | Cam device |
| FR3076475B1 (en) * | 2018-01-09 | 2019-11-29 | Psa Automobiles Sa | SLIDING ASSEMBLY ON A CRUSHING PRESS STACK |
| DE102018111366B4 (en) * | 2018-05-14 | 2024-03-07 | F I B R O Gmbh | Wedge drive with adjustable guide device |
| DE102019100687B4 (en) | 2019-01-11 | 2021-05-20 | Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. | Wedge drive tool |
| JP7431434B2 (en) * | 2019-10-10 | 2024-02-15 | 株式会社キーレックス | Metal plate processing equipment |
| DE102022108067B3 (en) | 2022-04-05 | 2023-04-27 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Tool slide and method of assembly and/or disassembly |
| DE202022104415U1 (en) | 2022-07-12 | 2022-11-02 | F I B R O Gmbh | slider assembly |
| DE102022117325B3 (en) | 2022-07-12 | 2023-11-09 | F I B R O Gmbh | Slide arrangement |
| CN117282844B (en) * | 2023-11-23 | 2024-03-08 | 江苏常丰精密科技有限公司 | Stretching and trimming die for square shell of power battery |
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| KR960020727U (en) * | 1994-12-22 | 1996-07-18 | Cam guide block structure of press mold | |
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| DE19860178C1 (en) | 1998-12-24 | 2000-05-11 | Harald Weigelt | Wedge drives for finishing bodywork parts in car production lines includes slider returnable by gas compression spring and guided in slide faces arranged in prism formation to allow for manufacturing tolerances |
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| RU2282517C2 (en) * | 2004-05-31 | 2006-08-27 | Открытое акционерное общество "Чепецкий механический завод" (ОАО ЧМЗ) | Blank radial forging method and four-striker forging apparatus for performing the same |
| US7431502B2 (en) * | 2004-09-15 | 2008-10-07 | Anchor Lamina America, Inc. | Universal cam slide |
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2007
- 2007-09-24 DE DE102007045703A patent/DE102007045703A1/en active Pending
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2008
- 2008-01-31 MX MX2010003031A patent/MX2010003031A/en active IP Right Grant
- 2008-01-31 JP JP2010525212A patent/JP5230743B2/en active Active
- 2008-01-31 UA UAA201004864A patent/UA97863C2/en unknown
- 2008-01-31 PL PL08715674T patent/PL2197660T3/en unknown
- 2008-01-31 ES ES08715674.1T patent/ES2553582T3/en active Active
- 2008-01-31 WO PCT/EP2008/000742 patent/WO2009039895A1/en active Application Filing
- 2008-01-31 CA CA2700576A patent/CA2700576C/en not_active Expired - Fee Related
- 2008-01-31 EP EP08715674.1A patent/EP2197660B1/en active Active
- 2008-01-31 BR BRPI0817324-9A patent/BRPI0817324B1/en active IP Right Grant
- 2008-01-31 RU RU2010114863/02A patent/RU2461463C2/en not_active IP Right Cessation
- 2008-01-31 CN CN200880114991.9A patent/CN101848805B/en active Active
- 2008-01-31 KR KR1020107006463A patent/KR101230185B1/en active IP Right Grant
Also Published As
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| ES2553582T3 (en) | 2015-12-10 |
| PL2197660T3 (en) | 2016-04-29 |
| KR20100046062A (en) | 2010-05-04 |
| BRPI0817324A2 (en) | 2015-03-24 |
| WO2009039895A1 (en) | 2009-04-02 |
| JP2010540249A (en) | 2010-12-24 |
| BRPI0817324B1 (en) | 2019-11-12 |
| DE102007045703A1 (en) | 2009-04-09 |
| JP5230743B2 (en) | 2013-07-10 |
| CN101848805A (en) | 2010-09-29 |
| MX2010003031A (en) | 2012-01-20 |
| EP2197660B1 (en) | 2015-09-09 |
| EP2197660A1 (en) | 2010-06-23 |
| KR101230185B1 (en) | 2013-02-06 |
| RU2461463C2 (en) | 2012-09-20 |
| RU2010114863A (en) | 2011-11-10 |
| CN101848805B (en) | 2014-11-12 |
| CA2700576A1 (en) | 2009-04-02 |
| UA97863C2 (en) | 2012-03-26 |
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| EEER | Examination request | ||
| MKLA | Lapsed |
Effective date: 20220131 |