US3374684A - Carriage-reciprocating structure for a machine such as a drawing machine - Google Patents

Carriage-reciprocating structure for a machine such as a drawing machine Download PDF

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Publication number
US3374684A
US3374684A US502169A US50216965A US3374684A US 3374684 A US3374684 A US 3374684A US 502169 A US502169 A US 502169A US 50216965 A US50216965 A US 50216965A US 3374684 A US3374684 A US 3374684A
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United States
Prior art keywords
cam
carriage
rollers
movement
follower
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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US502169A
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English (en)
Inventor
Greven Johann
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Schumag Schumacher Metallwerke AG
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Schumag Schumacher Metallwerke AG
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Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C1/00—Manufacture of metal sheets, metal wire, metal rods, metal tubes by drawing
    • B21C1/16—Metal drawing by machines or apparatus in which the drawing action is effected by other means than drums, e.g. by a longitudinally-moved carriage pulling or pushing the work or stock for making metal sheets, bars, or tubes
    • B21C1/27—Carriages; Drives
    • B21C1/30—Drives, e.g. carriage-traversing mechanisms; Driving elements, e.g. drawing chains; Controlling the drive
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18296—Cam and slide
    • Y10T74/18304—Axial cam

Definitions

  • carriage means cyclically movable along a given path first forwardly from a given starting position to a given end position and then rearwardly from the end position back to the starting position, a pair of camfollower rollers displaced one with respect to the other along the path and defining a given space between themselves, a pair of support means carried by the carriage means and respectively supporting the rollers for rotary movement, and elongated cam means extending through the space between the cam-follower rollers and between the latter and movable in a direction generally transverse to the path, the cam means having a pair of opposed camming faces engaging the cam-follower rollers and respectively cooperating therewith to provide by cooperation of one of the camming faces with one of the rollers forward movement of the carriage means and by cooperation of the other of the ca
  • SPECIFICATION My invention relates to machines which have carriages which must be reciprocated.
  • my invention relates to machines of this type which are used in connection with drawing opera tions, according to which metal will be drawn through suitable drawing dies so as to reduce the cross section of the treated metal.
  • the camfollower rollers are arranged for this reason in such a way that they can be adjusted.
  • the rollers are of a tapered or frustoconical configuration and are mounted axially one above the other between a pair of camming surfaces on a suitable stub shaft which is fixedly mounted only at one of its ends so that this shaft projects freely from its one fixed end.
  • the pair of camming surfaces provided for forward and rearward movement, respectively are situated at different elevations so that one camming surface is capable of cooperating with one of the rollers on the stub shaft while the other camming surface is capable of cooperating with the other of the cam-follower rolls on the same stub shaft.
  • the stability of the drawing carriage and of the bearings for the cam-follower rollers are of extremely great importance so as to provide a reliable and faultless operation, particularly in those cases where the machine has a plurality of carriages and where the drawing operations are carried out at high speed.
  • the abovediscussed conventional arrangement of tapered rollers on a stub shaft is only of limited utility in connection with the forward movement of the drawing carriage. Where large drawing forces greater than 10 tons, or even greater than 20 tons are present, the above conventional arrangement is no longer adequate.
  • the machine will include a carriage means movable from a given starting position forwardly along a given path to an end position and then rearwardly along this same path back to the starting position.
  • a pair of cam-follower rollers 3 are provided with their axes of rotation spacedfrom each other .along the path of movement of the carriage means, and the pair of cam-follower rollers define between themselves a predetermined space.
  • a support means is carried by the carriage means and supports the pair of cam-follower rollers for rotary movement.
  • a single cam means extends through the space between the pair of cam-follower rollers and is movable in a direction generally transverse to the path along which the carriage means moves, and the single cam means which extends through the space between the pair of cam-follower rollers has forwardly and rearwardly directed camming faces respectively engaging the rollers to cooperate therewith for providing the forward and rearward movement of the carriage means.
  • the pair of cam-follower rollers are located in a common plane and the cam means is in the form of an elongated endless cam which is supported for rotary movement.
  • FIG. 1 is a bottom plan view of a carriage means of my invention, FIG. 1 illustrating in phantom lines how the cam means cooperates with the structure carried by the carriage means;
  • FIG. 2 is a side elevation of the structure of FIG. 1 showing the cam means partly in a section taken along line 11-11 of FIG.'l in the direction of the arrows;
  • FIG. 3 is a developed view of the cam of FIGS. 1 and 2;
  • FIG. 4 is a schematic side elevation showing how a pair of carriages of a drawing machine are controlled with the structure of my invention.
  • the carriage means 1 shown in the drawings is slideable along any suitable ways in a Well known manner so as to carry out a forward movement from a given starting position to a given end position and a rearward movement from this end position back to its starting position, during each operating cycle, and this cyclically repeating reciprocation of the carriage means 1 is represented by the double-headed arrow 10 in FIG. 1.
  • Situated beneath the carriage means 1 are a pair of cam-follower roller-s 2 and 3.
  • the carriage means 1 reciprocates in a given plane and the axes of the rollers 2 and 3 are parallel to each other and normal to the plane of the carriage means 1.
  • the cam-follower roller 2 is the forward roller which participates in the forward movement of the carriage means 1, and it is supported for rotary movement by a support means 4 which is fixedly carried by the carriage means 1 and which provides a fixed mounting for the axis of rotation of the cam-follower roller 2.
  • the support means 4 extends around the right peripheral portion of the roller 2, as viewed in FIG. 2, so that the support means 4 is situated both above and below the cam-follower roller 2 at both sides thereof, so that a very secure mounting of the cam-follower roller 2 at both of its sides is provided with the support means 4 of my invention.
  • This support means 4 is fixedly connected directly with a bottom plate of the carriage means 1.
  • the support means which supports the rear cam-follower roller 3 for rotation mounts the latter roller for yieldable resilient movement.
  • this latter support means includes an elongated lever 5 supported for pivotal movement by pivot pin 6 fixedly carried by the carriage means 1 and extending through a suitable bore in one end of the lever 5.
  • the other end of the lever 5 is engaged by a spring assembly 7 made up of a stack or series of cup-shaped spring plates pressing one against the other and capable of having their force of compression adjusted by an adjusting screw 8, so that in this way the spring assembly 7 urges the lever 5 to turn in a counter-clockwise direction about the pivot 6, as viewed in FIG. 1.
  • the lever 5 carries intermediate its ends the pivot 9 for the roller 3, and thus the roller 3 is urged toward the forward roller 2 by the spring means 7.
  • axis of the pivot 9, which coincides with the axis of the roller 3, is thus capable of yielding rearwardly in response to a force sufficient to compress the spring assembly 7 so as to be capable of increasing the space between the rollers 2 and 3 when and if required.
  • cam-follower rollers 2 and 3 are situated in a common plane which is parallel to the plane in which the carriage means 1 moves and moreover these rollers 2 and 3 are mounted with their axes displaced from each other along the path of movement of the carriage means 1 to an extent sufficient to provide a predetermined space between the rollers 2 .and 3. It is through this latter space that the cam means of my invention extends in a direction generally transverse to the path of movement of the carriage means 1, so that in this way a single cam can be provided with opposed camming faces respectively engaging the rollers 2 and 3.
  • the cam means of my invention includes a cam portion 11 which provides rearward movement of the carriage and a cam portion 11 which provides the forward movement of the carriage, and this cam is shown in one example most clearly in the developed view of FIG. 3.
  • the cam portions 11 and 11' respectively have forward camming surfaces 12 and 12' which cooperate with the forward cam-follower roller 2 and rear camming faces 13 and 13 which cooperate with the rear cam-follower roller 3.
  • the cam- -ming face 12 produces the forward movement of the carriage means 1, while the rear camming face 13 provides the return movement of the carriage means 1.
  • the camming face 13 approaches the path of movement of the carriage means 1 to a far greater extent than the camming face 12' so that this camming face 13 is considerably steeper than the camming face 12' and thus will provide a return stroke for the carriage which requires less time than the forward stroke thereof.
  • the thickness of the cam portion 11' because of its reduced steepness according to which it more closely approaches a direction precisely transverse to the path of movement of the carriage means 1, is greater than the thickness of the steeper cam portion 11 while also providing a substantially constant distance between the follower rollers 2 and 3.
  • a rotary cam drum 14 forms part of the camming means and has its axis extending in the direction of movement of the carriage means 1 perpendicularly across the pair of parallel axes of the rollers 2 and 3 and parallel to the plane in which the carriage means 1 moves.
  • the cam 11, 11' is integral with the hollow drum 14 and projects from the exterior surface thereof into the space between the follower rollers 2 and 3 so that the forward and rearward camming faces can respectively cooperate with these rollers 2 and 3.
  • the follower rollers 2 3 engage the camming faces with completely different parts of their outer peripheries according to the angular position of the cam 11, 11'. This geometric factor must be taken into consideration in determining the curvature of the cam.
  • the prestressing of the spring assembly 7 is so chosen that when the machine operates at maximum drawing speed, which is to say when the carriage means 1 executes the largest number of operating cycles in a given period of time, the cam-follower roller 2 does not become separated from the cam at the crest or reversing point 19 where the camming faces 12 and 12' meet.
  • the spring assembly 7 it should not be possible for the spring assembly 7 to be compressed to such an extent that the cam moves rearwardly out of contact with the forward cam-follower roller 2. Any inaccuracies in the camming faces 12, 12 and 13, 13' are compensated for by the elasticity of the spring assembly 7.
  • FIG. 4 in addition to the drawing carirage 1 with its cam-follower rollers 2 and 3, cam drum 14, and cam means 11, 11', there is a second drawing carriage 15 with its cam-follower rollers 16 and 17 which respectively correspond to the rollers 2 and 3 as well as with its cooperating cam drum 18 and cam 20 which corresponds to the cam drum 14 and cam 11, 11, respectively.
  • FIG. 4 in addition to the drawing carirage 1 with its cam-follower rollers 2 and 3, cam drum 14, and cam means 11, 11', there is a second drawing carriage 15 with its cam-follower rollers 16 and 17 which respectively correspond to the rollers 2 and 3 as well as with its cooperating cam drum 18 and cam 20 which corresponds to the cam drum 14 and cam 11, 11, respectively.
  • the pair of cams illustrated therein are angularly displaced with respect to each other in such a way that the pair of carriages 1 and 15 are out of phase in their cyclical movements, the cam drums 14 and 18 actually being shown at 180 out of phase relationship so that in this way the work can be continuously drawn-by being suceessively engaged in a known way with structure carried by the carriages 1 and 15.
  • the other carriage takes over and continues the forward drawing of the work without any interruption.
  • This latter phase of the drawing operations are conventional and form no part of my invention.
  • cam-follower rollers of my invention can take the form of simple rollers of cylindrical configuration, and any transmission of axial force components to the carriage itself is reliably avoided.
  • the structure of my invention can be operated with very great precision. Therefore, the structure of my invention is particularly suited for drawing machines where the work material is continuously drawn through the drawing dies and where at least a pair of drawing carriages are provided to operate in a given phase relationship as pointed out above in connection with FIG. 4.
  • the rotary drum support for the cam structure is preferred because of the advantages it provides in connection with the saving of space and the ease of mounting of the cam assembly.
  • each follower roller at both of its sides is relatively simple to carry out with the particular arrangement of my invention and provides the advantage of avoiding the necessity of structures which are too large and heavy, even when dealing with drawing forces on the .order 10 or 20 tons.
  • the cam-follower rollers are mounted on a common stub shaft which is fixed at only one of its ends, the size of the parts is necessarily far too great to be of any practical value when dealing with relatively large drawing forces.
  • the forward roller 2 a fixed mounting for its axis of rotation, since it is this forward roller which receives the greater force.
  • a fixed mounting of the axis of rotation of the forward cam-follower roller is preferred and makes the structure particularly suitable for drawing machines where relatively large forces are absorbed by these forward rollers of the drawing carriages.
  • the cam-follower rollers 2 and 3 will be maintained at a constant distance from each other at all times.
  • the cam is relatively steep, so that it approaches to a greater extent the direction of movement of the carriage, the distance between the pair of camming faces must be reduced and thus the thickness of the cam must be correspondingly reduced.
  • cam thickness By a proper choice of cam thickness it is possible to provide the structure of my invention according to which at all angular positions of the cam drum the cam will maintain the rollers at the same distance from each other. In this way any possible play between the cam-follower rollers and the camming faces is eliminated.
  • the required variation in the thickness of the cam along its length can easily be calculated or. determined from drawings or from suitable tests.
  • the diameters of the rollers 2 and 3 as well as the distance therebetween are so chosen that the pair of opposed camming faces at the steepest part of the cam will still be spaced from each other by a distance great enough to provide a cam at its steepest portion with a thickness sufficiently great toabsorb the forces which are encountered.
  • carriage means cyclically movable along a given path first forwardly from a given starting position to a given end position and then rearwardly from said end position back to said starting position, a pair of cam-follower rollers displaced one with respect to the other along said path and defining a given space between themselves, a pair of support means carried by said carriage means and respectively supporting said .rollers for rotary movement, and elongated cam means extending through said space between said cam-follower rollers and between the latter and movable in a direction generally transverse to said path, said cam means having a pair of opposed camming faces engaging said cam-follower rollers and respectively cooperating therewith to provide by cooperation of one of said camming faces with one of said rollers forward movement of said carriage means and by cooperation of the other of said camming faces with the other of said rollers rearward movement of said carriage means, one of said support means which supports the cam-follower roller-which cooperates with said cam means to provide rearward movement of said carriage means supporting the latter roller
  • said one'support means including a lever turnable carrying said latter roller intermediate the ends of said lever, a pivot carried by said carriage means and supporting said leverfor turning movement adjacent one of said ends thereof and an adjustable spring assembly mounted on said carriage means and engaging the other of said ends of said lever for urging the cam follower roller carried thereby toward said cam means.
  • carriage means movable back and forth in a given plane from a given starting position forwardly to'a given end position and from said end position rearwardly back to said starting position, a rotary cam drum having an axis of rotation parallel to said plane in which said carriage means moves, said axis extending generally in the direction of movement of said carriage means and said rotary cam drum carrying at its exterior surface an endless cam of predetermined curvature which projects from the surface of said cam drum and which has a pair of opposed camming faces one of which is a forward camming face and is directed forwardly while the other camming face is a rear camming face and is directed rearwardly, a pair of cam-follower rollers respectively having axes parallel to each other and normal to the axis of said drum and said plane in which said carriage means moves, said cam-follower rollers being situated in a common plane parallel to the plane in which said car riage means moves and respectively engaging saidopposed camming faces with one of said rollers being a forward roller and
  • the endless cam which projects from said periphery of said drum having a curvature and a distance between said camming faces which maintains said rollers at a substantially constant distance from each other at all angular positions of said drum.

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  • Mechanical Engineering (AREA)
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US502169A 1965-04-17 1965-10-22 Carriage-reciprocating structure for a machine such as a drawing machine Expired - Lifetime US3374684A (en)

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DESC036904 1965-04-17

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FR (1) FR1462081A (fr)
GB (1) GB1134066A (fr)
SE (1) SE306916B (fr)

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3699291A (en) * 1971-04-01 1972-10-17 Millipore Corp Apparatus for converting rotational displacement into linear displacement
US3807242A (en) * 1973-04-18 1974-04-30 Stoneco Inc Power tool adapter
US4101153A (en) * 1974-10-24 1978-07-18 Dozier Donald P Quick opening lock assembly for doors and method
US4187762A (en) * 1977-02-14 1980-02-12 Buzby Nicholas L Drive and motion synchronizing apparatus for a hydraulic system
EP0112805A1 (fr) * 1982-12-23 1984-07-04 DANIELI & C. OFFICINE MECCANICHE S.p.A. Dispositif pour actionner le mouvement d'un chariot d'étirage
US4532820A (en) * 1978-06-27 1985-08-06 M. S. Willett, Inc. Motion multiplier apparatus
US4631827A (en) * 1985-01-09 1986-12-30 Black & Decker, Inc. Electric knife drive mechanism
US4756239A (en) * 1986-11-28 1988-07-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Anti-rolling structure for double headed piston of disc cam type reciprocative compressor
EP0371165A1 (fr) * 1988-11-30 1990-06-06 Schumag Aktiengesellschaft Commande de mouvement
US5452647A (en) * 1993-06-08 1995-09-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave plate type compressor
WO1996027459A1 (fr) * 1995-03-08 1996-09-12 Delaware Capital Formation, Inc. Ensemble a coulisseau et contre-came taree
US5603245A (en) * 1993-02-02 1997-02-18 Schumag Aktiengesellschaft Method for a translatory motion of components
US20090266128A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. Apparatus for rotating a container body
US20090266129A1 (en) * 2008-04-24 2009-10-29 Daniel Egerton Container manufacturing process having front-end winder assembly
US20090266131A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. High Speed Necking Configuration
US20090266126A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. Systems and methods for monitoring and controlling a can necking process
US8245551B2 (en) 2008-04-24 2012-08-21 Crown Packaging Technology, Inc. Adjustable transfer assembly for container manufacturing process
US8464567B2 (en) 2008-04-24 2013-06-18 Crown Packaging Technology, Inc. Distributed drives for a multi-stage can necking machine
WO2016071276A1 (fr) * 2014-11-03 2016-05-12 Continental Automotive Gmbh Actionneur linéaire
US20170059027A1 (en) * 2015-08-31 2017-03-02 Hcc, Inc. Cam follower design for a pickup reel

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE388046C (de) * 1924-01-08 Franz Ulmer Dr Ing Schraegringgetriebe
US1808083A (en) * 1929-05-31 1931-06-02 Packard Motor Car Co Nternal combustion engine
US2323375A (en) * 1941-12-26 1943-07-06 Kenly C Bugg Tool

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE388046C (de) * 1924-01-08 Franz Ulmer Dr Ing Schraegringgetriebe
US1808083A (en) * 1929-05-31 1931-06-02 Packard Motor Car Co Nternal combustion engine
US2323375A (en) * 1941-12-26 1943-07-06 Kenly C Bugg Tool

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3699291A (en) * 1971-04-01 1972-10-17 Millipore Corp Apparatus for converting rotational displacement into linear displacement
US3807242A (en) * 1973-04-18 1974-04-30 Stoneco Inc Power tool adapter
US4101153A (en) * 1974-10-24 1978-07-18 Dozier Donald P Quick opening lock assembly for doors and method
US4187762A (en) * 1977-02-14 1980-02-12 Buzby Nicholas L Drive and motion synchronizing apparatus for a hydraulic system
US4532820A (en) * 1978-06-27 1985-08-06 M. S. Willett, Inc. Motion multiplier apparatus
EP0112805A1 (fr) * 1982-12-23 1984-07-04 DANIELI & C. OFFICINE MECCANICHE S.p.A. Dispositif pour actionner le mouvement d'un chariot d'étirage
US4631827A (en) * 1985-01-09 1986-12-30 Black & Decker, Inc. Electric knife drive mechanism
US4756239A (en) * 1986-11-28 1988-07-12 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Anti-rolling structure for double headed piston of disc cam type reciprocative compressor
EP0371165A1 (fr) * 1988-11-30 1990-06-06 Schumag Aktiengesellschaft Commande de mouvement
US5040426A (en) * 1988-11-30 1991-08-20 Schumag Ag Drive mechanism for moving a member along a defined path
US5603245A (en) * 1993-02-02 1997-02-18 Schumag Aktiengesellschaft Method for a translatory motion of components
US5452647A (en) * 1993-06-08 1995-09-26 Kabushiki Kaisha Toyoda Jidoshokki Seisakusho Wave plate type compressor
WO1996027459A1 (fr) * 1995-03-08 1996-09-12 Delaware Capital Formation, Inc. Ensemble a coulisseau et contre-came taree
US5676006A (en) * 1995-03-08 1997-10-14 Delaware Capital Formation, Inc. Preloaded-cam follower ram assembly for reshaping containers
US20090266131A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. High Speed Necking Configuration
US8601843B2 (en) 2008-04-24 2013-12-10 Crown Packaging Technology, Inc. High speed necking configuration
US20090266128A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. Apparatus for rotating a container body
US20090266126A1 (en) * 2008-04-24 2009-10-29 Crown Packaging Technology, Inc. Systems and methods for monitoring and controlling a can necking process
US7770425B2 (en) 2008-04-24 2010-08-10 Crown, Packaging Technology, Inc. Container manufacturing process having front-end winder assembly
US7784319B2 (en) 2008-04-24 2010-08-31 Crown, Packaging Technology, Inc Systems and methods for monitoring and controlling a can necking process
US7997111B2 (en) 2008-04-24 2011-08-16 Crown, Packaging Technology, Inc. Apparatus for rotating a container body
US8245551B2 (en) 2008-04-24 2012-08-21 Crown Packaging Technology, Inc. Adjustable transfer assembly for container manufacturing process
US8464567B2 (en) 2008-04-24 2013-06-18 Crown Packaging Technology, Inc. Distributed drives for a multi-stage can necking machine
US20090266129A1 (en) * 2008-04-24 2009-10-29 Daniel Egerton Container manufacturing process having front-end winder assembly
US9290329B2 (en) 2008-04-24 2016-03-22 Crown Packaging Technology, Inc. Adjustable transfer assembly for container manufacturing process
US9308570B2 (en) 2008-04-24 2016-04-12 Crown Packaging Technology, Inc. High speed necking configuration
US10751784B2 (en) 2008-04-24 2020-08-25 Crown Packaging Technology, Inc. High speed necking configuration
US9968982B2 (en) 2008-04-24 2018-05-15 Crown Packaging Technology, Inc. High speed necking configuration
CN107110395A (zh) * 2014-11-03 2017-08-29 大陆汽车有限责任公司 直线致动器
JP2018502257A (ja) * 2014-11-03 2018-01-25 コンチネンタル オートモーティヴ ゲゼルシャフト ミット ベシュレンクテル ハフツングＣｏｎｔｉｎｅｎｔａｌ Ａｕｔｏｍｏｔｉｖｅ ＧｍｂＨ リニアアクチュエータ
US10619604B2 (en) 2014-11-03 2020-04-14 Continental Automotive Gmbh Linear actuator
WO2016071276A1 (fr) * 2014-11-03 2016-05-12 Continental Automotive Gmbh Actionneur linéaire
US20170059027A1 (en) * 2015-08-31 2017-03-02 Hcc, Inc. Cam follower design for a pickup reel

Also Published As

Publication number Publication date
GB1134066A (en) 1968-11-20
SE306916B (fr) 1968-12-16
FR1462081A (fr) 1966-12-09

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