Title:
SWAGING MACHINE FOR A CONTINUOUS SWAGING OF ROD-SHAPED WORKPIECES
United States Patent 3690142
Abstract:
The hammers of a swaging machine, which extend radially to the axis of the feeding path of a workpiece, are driven by eccentric shafts parallel to this path. Each hammer is slidably guided in the longitudinal direction thereof, and elliptic chucks transform the rotation of the shafts into a radial swaging motion of the hammers to and from the feeding path and into an oscillating rocking motion in a plane defined by the axes of the feeding path and the associated shaft. Each chuck comprises a spider rigid with the associated hammer, a cylindrical link surrounding the eccentric of the associated shaft, a first guiding element carried by the spider, a second guiding element carried by the link, meshing helical teeth on the guiding elements, and the second guiding elements being held against displacement parallel to the shafts.
US Patent References:
Stretch-forging machine
Kralowetz - September 1959 - 2903923
Forging machine
Kralowetz - June 1965 - 3165012
Swaging machine
Kralowetz - December 1965 - 3224244
APPARATUS FOR SWAGING CONTINUOUS STOCK
Kralowetz - August 1969 - 3460370
APPARATUS FOR A CONTINUOUS SWAGING OF ROD-SHAPED WORKPIECES
Kralowetz - March 1971 - 3572077
Stretch-forging machine
Kralowetz - September 1959 - 2903923
Forging machine
Kralowetz - June 1965 - 3165012
Swaging machine
Kralowetz - December 1965 - 3224244
APPARATUS FOR SWAGING CONTINUOUS STOCK
Kralowetz - August 1969 - 3460370
APPARATUS FOR A CONTINUOUS SWAGING OF ROD-SHAPED WORKPIECES
Kralowetz - March 1971 - 3572077
Application Number:
05/088946
Publication Date:
09/12/1972
Filing Date:
11/12/1970
View Patent Images:
Export Citation:
Assignee:
Gfm, Gesellschaft Fur Fertigungstechnik Und Maschinenbau (Steyr, OE)
Primary Class:
Other Classes:
74/402, 72/406
International Classes:
B21J7/14; B21J7/00; B21J9/06
Field of Search:
72/402,404,429,189,399,452,406
US Patent References:
| 3596497 | APPARATUS FOR THE CONTINUOUS SWAGING OF CONTINUOUS WORKPIECES | August 1971 | Kralowetz |
Primary Examiner:
Lanham, Charles W.
Assistant Examiner:
Crosby, Gene P.
Claims:
What is claimed is
1. A swaging machine for a continuous swaging of rod-shaped workpieces, which comprises
2. A swaging machine as set forth in claim 1, in which
1. A swaging machine for a continuous swaging of rod-shaped workpieces, which comprises
2. A swaging machine as set forth in claim 1, in which
Description:
This invention relates to a swaging machine for a continuous swaging of rod-shaped workpieces, which machine comprises connecting rod-like hammers, which extend radially to the axis of the workpiece and are driven by eccentric shafts that are parallel to said axis, each of said hammers comprising the spider of an elliptic chuck which includes a cylindrical link, which surrounds the eccentric and is slidably guided in the spider transversely to the axis of the hammer, each hammer also comprising a rotatable sliding guide, which is disposed between the eccentric shaft and the workpiece, and each hammer performing both a radial swaging movement to and from the workpiece and a rocking movement in the plane which extends through the axes of the workpiece and of the eccentric shaft.
Swaging machines are known in which the eccentric shafts for driving the connecting rod-like hammers extend transversely to the axis of the workpiece and in which the axis of rotation of the sliding guide for each hammer is parallel to the associated eccentric shaft. In this arrangement, the hammers constitute true connecting rods, which perform a motion that is composed of a thrust movement toward the workpiece and a rocking or oscillating motion about the axis of rotation of the sliding guide so that the hammers do not only shape the workpiece so as to reduce the cross-section thereof but also advance the workpiece. The orientation of the eccentric shafts transversely to the axis of the workpiece necessitates the provision of bevel or angle gear drives for driving the eccentric shafts. Particularly in machines which comprise more than two hammers, these bevel or angle gear drives involve a relatively complicated and expensive design. The common drive of two or more similar swaging machines arranged one behind the other is also rendered difficult.
A swaging machine has been disclosed in which this disadvantage is eliminated in that the axes of the eccentric shafts are parallel to the axis of the workpiece and the axes of rotation of the sliding guides are transverse to the axis of the workpiece and an oscillating rocking motion about the axis of rotation of the sliding guide is superimposed on the radial thrust motion of the hammers. To superimpose the motions, each hammer comprises a spider of an elliptic chuck which comprises a link that embraces the eccentric and is displaceable transversely to the axis of the hammer. On that side of the spider which is remote from the sliding guide, the hammers engage a coupling pin, which is parallel to the eccentric shaft and is adapted to reciprocate to an extent which is determined by the rotation of the eccentric shaft. For this reason, these hammers do not perform a rocking motion in a plane which is normal to the axis of the workpiece and to the axes of the eccentric shafts because these hammers comprise spiders of elliptic chucks in which only the link performs the transverse movement which is required. The reciprocation of the coupling pin imparts to each hammer an oscillating motion in the plane that includes the axis of the eccentric shaft and the axis of the workpiece so that the workpiece is advanced as desired as it is shaped by the hammers although the axes of the eccentric shafts extend parallel to the axis of the workpiece so that simple spur gears may be used for driving the eccentric shafts. A reciprocating axial motion is imparted to the coupling pin which causes the hammers to oscillate because the coupling pin is held against rotation by the hammer but is provided with screw threads which engage a nut, which by a crank arm and a coupling link is linked to a pivoted spider of an elliptic chuck, which comprises a link that embraces another eccentric mounted on the eccentric shaft so that the crank arm, the coupling link and the spider chuck form a four-bar linkage. The additional eccentric on the eccentric shaft imparts an oscillating rocking motion to the associated spider which forms one link of the four-bar linkage so that the crank arm oscillates in unison therewith and the nut performs an oscillating angular motion so as to impart the desired reciprocating axial motion to the coupling pin and the desired oscillation to the hammer in the desired dependence on the rotation of the eccentric shaft. In that known swaging machine, the eccentric shafts can be driven by a fairly simple mechanism which includes simple spur gears but the oscillation of the hammers in the plane which includes the axes of the eccentric shafts and the axis of the workpiece, which oscillation is superimposed on the axial motion of the hammers, still requires a considerable structural expenditure. For this reason, that solution is not fully satisfactory.
It is an object of the invention to eliminate these disadvantages and so to improve the swaging machine which has been described hereinbefore that the oscillating motion of the hammers which is superimposed on the radial swaging motion to and from the workpiece is accomplished by means which are very simple in structure so that the structural expenditure is much reduced.
This object is accomplished according to the invention in that the cooperating guiding elements on one side of the spider and on the link of the elliptic chuck comprise meshing helical teeth and the guiding element of the link is held against a displacement parallel to the eccentric shaft. During the rotation of the eccentric shaft, the link performs in the spider formed by the hammer an axial motion which is transverse to the axis of the hammer whereas the hammer initially follows only that movement of the link which is in the direction of the axis of the hammer. Because the link and spider of the elliptic chuck comprise meshing helical teeth, a displacement of the link transversely to the axis of the hammer will necessarily result in an additional motion of one of the two meshing parts in the plane which includes the axis of the eccentric shaft. Because the guiding element of the link is held against a displacement that is parallel to the eccentric shaft, only the hammer itself can perform said additional motion so that the hammer will oscillate as desired. This oscillation of the hammer is enabled because the link is cylindrical and the hammer is guided in the rotatable sliding guide. This results in a comparatively simple design, which hardly adds to the structural expenditure which is anyway required because it is sufficient to provide helical teeth on the guiding elements on one side of the spider and the link of the elliptic chuck.
To enable an oscillating rocking motion of the connecting rod-like hammer relative to the link about the axis of rotation of the sliding guide for the hammer, the axes of the cylindrical surfaces of the link and of the spider of the elliptic chuck must coincide with the axis of rotation of the sliding guide. The axial motion of the hammer to and from the workpiece results necessarily in a displacement of the axis of the cylinder relative to the axis of rotation of the sliding guide. Such displacement is also due to the fact that the location of the axis of rotation of the eccentric shaft is changed when the hammer engages the workpiece or the depth of penetration of the hammer into the workpiece is changed. To take these changes into account, the link of the elliptic chuck is provided on its side which is opposite to the helical teeth with a cylindrical guiding surface, which is coaxial with the helical teeth, the common cylinder axis coincides approximately with the axis of rotation of the sliding guide for the hammer, and the link of the elliptic chuck consists of two parts, one of which has no helical teeth and is displaceable in the direction of the eccentric shaft. Owing to the division of the link of the elliptic chuck into two parts, which are movable relative to each other parallel to the axis of the eccentric shaft, the hammer can perform a pivotal movement relative to the link of the elliptic chuck even when the axis of the cylindrical guiding elements of said link does not exactly agree with the axis of rotation of the sliding guide.
An embodiment of the invention is shown by way of example on the accompanying drawing, in which
FIGS. 1 and 2 are fragmentary sectional views taken on line I--I in FIG. 2 and on line II--II in FIG. 1, respectively, and showing a part of a swaging machine.
A machine housing 1 comprises four connecting rod-like hammers 3, which are angularly spaced 90° 0 apart and extend radially to the axis 2 of the workpiece. Each hammer 3 cooperates with a rotatable sliding guide 4 and is driven by an eccentric shaft 5, which is parallel to the axis 2 of the workpiece. The eccentric shafts 5 are eccentrically mounted in rotatable adjusting housings 6, which are rotatable to change the distance from the axes of the eccentric shafts to the axis 2 of the workpiece so that the stroke position of the hammers will be changed too. Each eccentric shaft is driven by a clutch, which is only diagrammatically indicated and permits of a displacement of the eccentric shaft relative to the driving spur gear. Such clutches are known in the art.
Each hammer 3 comprises a spider 7 of an elliptic chuck. Guiding elements 8, 9 having a cylindrical inside surface are anchored in said spider. The eccentric 10 of each eccentric shaft 5 is surrounded by a two-part link 11, 12, which is slidable in the spider transversely to the axis of the hammer. The part 12 of the link has a cylindrical outside surface, which conforms to the cylindrical inside surface of the guiding element 9 of the spider. The guiding element 8 of the spider and the guiding element 11 of the link of the elliptic chuck carry meshing helical teeth 13. The cylindrical guiding surfaces of the elements 9 and 12 and the helical teeth 13 have a common axis, which approximately coincides with the axis of rotation of the sliding guide 4. As is apparent from FIG. 1, the guiding element 11 of the link of the elliptic chuck is held against a displacement parallel to the eccentric shaft 5. On the other hand, the element 12 can move in this direction relative to the part 11. The two elements 11, 12 of the link of the elliptic chuck are rigidly coupled to move in unison in a direction which is transverse to the eccentric shaft. On that side of the spider 7 of the elliptic chuck which is remote from the sliding guide 4, the hammers 3 are provided with two bifurcated guide extensions 14, which straddle a stationary slide rail 15. As a result, the hammers can oscillate only in the planes which are defined by the axes of the eccentric shaft and the axis 2 of the workpiece whereas a movement transverse to the axis of the workpiece and of the eccentric shaft is precluded.
During a rotation of the eccentric shaft 5, the two-part link 11, 12 reciprocates in the spider 7 in the direction of the arrow 16 in FIG. 2 and the hammer is moved radially to and from the workpiece at the same time. Owing to the meshing helical teeth 13, the reciprocating relative axial movement of the link 11, 12 also results in a reciprocating rocking motion of the hammer 3 in the direction of the arrow 17 in FIG. 1 because the guiding element 11 of the link is supported at its end in the adjusting housing 6 and is thus held against a movement parallel to the eccentric shaft. When the axis of the cylindrical guiding surfaces does not coincide with the axis of rotation of the sliding guide 4, the division of the link into two parts enables a very slight movement of the element 12 of the link in a direction which is parallel to the eccentric shaft.
Swaging machines are known in which the eccentric shafts for driving the connecting rod-like hammers extend transversely to the axis of the workpiece and in which the axis of rotation of the sliding guide for each hammer is parallel to the associated eccentric shaft. In this arrangement, the hammers constitute true connecting rods, which perform a motion that is composed of a thrust movement toward the workpiece and a rocking or oscillating motion about the axis of rotation of the sliding guide so that the hammers do not only shape the workpiece so as to reduce the cross-section thereof but also advance the workpiece. The orientation of the eccentric shafts transversely to the axis of the workpiece necessitates the provision of bevel or angle gear drives for driving the eccentric shafts. Particularly in machines which comprise more than two hammers, these bevel or angle gear drives involve a relatively complicated and expensive design. The common drive of two or more similar swaging machines arranged one behind the other is also rendered difficult.
A swaging machine has been disclosed in which this disadvantage is eliminated in that the axes of the eccentric shafts are parallel to the axis of the workpiece and the axes of rotation of the sliding guides are transverse to the axis of the workpiece and an oscillating rocking motion about the axis of rotation of the sliding guide is superimposed on the radial thrust motion of the hammers. To superimpose the motions, each hammer comprises a spider of an elliptic chuck which comprises a link that embraces the eccentric and is displaceable transversely to the axis of the hammer. On that side of the spider which is remote from the sliding guide, the hammers engage a coupling pin, which is parallel to the eccentric shaft and is adapted to reciprocate to an extent which is determined by the rotation of the eccentric shaft. For this reason, these hammers do not perform a rocking motion in a plane which is normal to the axis of the workpiece and to the axes of the eccentric shafts because these hammers comprise spiders of elliptic chucks in which only the link performs the transverse movement which is required. The reciprocation of the coupling pin imparts to each hammer an oscillating motion in the plane that includes the axis of the eccentric shaft and the axis of the workpiece so that the workpiece is advanced as desired as it is shaped by the hammers although the axes of the eccentric shafts extend parallel to the axis of the workpiece so that simple spur gears may be used for driving the eccentric shafts. A reciprocating axial motion is imparted to the coupling pin which causes the hammers to oscillate because the coupling pin is held against rotation by the hammer but is provided with screw threads which engage a nut, which by a crank arm and a coupling link is linked to a pivoted spider of an elliptic chuck, which comprises a link that embraces another eccentric mounted on the eccentric shaft so that the crank arm, the coupling link and the spider chuck form a four-bar linkage. The additional eccentric on the eccentric shaft imparts an oscillating rocking motion to the associated spider which forms one link of the four-bar linkage so that the crank arm oscillates in unison therewith and the nut performs an oscillating angular motion so as to impart the desired reciprocating axial motion to the coupling pin and the desired oscillation to the hammer in the desired dependence on the rotation of the eccentric shaft. In that known swaging machine, the eccentric shafts can be driven by a fairly simple mechanism which includes simple spur gears but the oscillation of the hammers in the plane which includes the axes of the eccentric shafts and the axis of the workpiece, which oscillation is superimposed on the axial motion of the hammers, still requires a considerable structural expenditure. For this reason, that solution is not fully satisfactory.
It is an object of the invention to eliminate these disadvantages and so to improve the swaging machine which has been described hereinbefore that the oscillating motion of the hammers which is superimposed on the radial swaging motion to and from the workpiece is accomplished by means which are very simple in structure so that the structural expenditure is much reduced.
This object is accomplished according to the invention in that the cooperating guiding elements on one side of the spider and on the link of the elliptic chuck comprise meshing helical teeth and the guiding element of the link is held against a displacement parallel to the eccentric shaft. During the rotation of the eccentric shaft, the link performs in the spider formed by the hammer an axial motion which is transverse to the axis of the hammer whereas the hammer initially follows only that movement of the link which is in the direction of the axis of the hammer. Because the link and spider of the elliptic chuck comprise meshing helical teeth, a displacement of the link transversely to the axis of the hammer will necessarily result in an additional motion of one of the two meshing parts in the plane which includes the axis of the eccentric shaft. Because the guiding element of the link is held against a displacement that is parallel to the eccentric shaft, only the hammer itself can perform said additional motion so that the hammer will oscillate as desired. This oscillation of the hammer is enabled because the link is cylindrical and the hammer is guided in the rotatable sliding guide. This results in a comparatively simple design, which hardly adds to the structural expenditure which is anyway required because it is sufficient to provide helical teeth on the guiding elements on one side of the spider and the link of the elliptic chuck.
To enable an oscillating rocking motion of the connecting rod-like hammer relative to the link about the axis of rotation of the sliding guide for the hammer, the axes of the cylindrical surfaces of the link and of the spider of the elliptic chuck must coincide with the axis of rotation of the sliding guide. The axial motion of the hammer to and from the workpiece results necessarily in a displacement of the axis of the cylinder relative to the axis of rotation of the sliding guide. Such displacement is also due to the fact that the location of the axis of rotation of the eccentric shaft is changed when the hammer engages the workpiece or the depth of penetration of the hammer into the workpiece is changed. To take these changes into account, the link of the elliptic chuck is provided on its side which is opposite to the helical teeth with a cylindrical guiding surface, which is coaxial with the helical teeth, the common cylinder axis coincides approximately with the axis of rotation of the sliding guide for the hammer, and the link of the elliptic chuck consists of two parts, one of which has no helical teeth and is displaceable in the direction of the eccentric shaft. Owing to the division of the link of the elliptic chuck into two parts, which are movable relative to each other parallel to the axis of the eccentric shaft, the hammer can perform a pivotal movement relative to the link of the elliptic chuck even when the axis of the cylindrical guiding elements of said link does not exactly agree with the axis of rotation of the sliding guide.
An embodiment of the invention is shown by way of example on the accompanying drawing, in which
FIGS. 1 and 2 are fragmentary sectional views taken on line I--I in FIG. 2 and on line II--II in FIG. 1, respectively, and showing a part of a swaging machine.
A machine housing 1 comprises four connecting rod-like hammers 3, which are angularly spaced 90° 0 apart and extend radially to the axis 2 of the workpiece. Each hammer 3 cooperates with a rotatable sliding guide 4 and is driven by an eccentric shaft 5, which is parallel to the axis 2 of the workpiece. The eccentric shafts 5 are eccentrically mounted in rotatable adjusting housings 6, which are rotatable to change the distance from the axes of the eccentric shafts to the axis 2 of the workpiece so that the stroke position of the hammers will be changed too. Each eccentric shaft is driven by a clutch, which is only diagrammatically indicated and permits of a displacement of the eccentric shaft relative to the driving spur gear. Such clutches are known in the art.
Each hammer 3 comprises a spider 7 of an elliptic chuck. Guiding elements 8, 9 having a cylindrical inside surface are anchored in said spider. The eccentric 10 of each eccentric shaft 5 is surrounded by a two-part link 11, 12, which is slidable in the spider transversely to the axis of the hammer. The part 12 of the link has a cylindrical outside surface, which conforms to the cylindrical inside surface of the guiding element 9 of the spider. The guiding element 8 of the spider and the guiding element 11 of the link of the elliptic chuck carry meshing helical teeth 13. The cylindrical guiding surfaces of the elements 9 and 12 and the helical teeth 13 have a common axis, which approximately coincides with the axis of rotation of the sliding guide 4. As is apparent from FIG. 1, the guiding element 11 of the link of the elliptic chuck is held against a displacement parallel to the eccentric shaft 5. On the other hand, the element 12 can move in this direction relative to the part 11. The two elements 11, 12 of the link of the elliptic chuck are rigidly coupled to move in unison in a direction which is transverse to the eccentric shaft. On that side of the spider 7 of the elliptic chuck which is remote from the sliding guide 4, the hammers 3 are provided with two bifurcated guide extensions 14, which straddle a stationary slide rail 15. As a result, the hammers can oscillate only in the planes which are defined by the axes of the eccentric shaft and the axis 2 of the workpiece whereas a movement transverse to the axis of the workpiece and of the eccentric shaft is precluded.
During a rotation of the eccentric shaft 5, the two-part link 11, 12 reciprocates in the spider 7 in the direction of the arrow 16 in FIG. 2 and the hammer is moved radially to and from the workpiece at the same time. Owing to the meshing helical teeth 13, the reciprocating relative axial movement of the link 11, 12 also results in a reciprocating rocking motion of the hammer 3 in the direction of the arrow 17 in FIG. 1 because the guiding element 11 of the link is supported at its end in the adjusting housing 6 and is thus held against a movement parallel to the eccentric shaft. When the axis of the cylindrical guiding surfaces does not coincide with the axis of rotation of the sliding guide 4, the division of the link into two parts enables a very slight movement of the element 12 of the link in a direction which is parallel to the eccentric shaft.