CA1064849A - Article transfer mechanism - Google Patents
Article transfer mechanismInfo
- Publication number
- CA1064849A CA1064849A CA288,381A CA288381A CA1064849A CA 1064849 A CA1064849 A CA 1064849A CA 288381 A CA288381 A CA 288381A CA 1064849 A CA1064849 A CA 1064849A
- Authority
- CA
- Canada
- Prior art keywords
- cam
- support members
- transfer mechanism
- feed bars
- opposite ends
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- 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
- B21D43/00—Feeding, positioning or storing devices combined with, or arranged in, or specially adapted for use in connection with, apparatus for working or processing sheet metal, metal tubes or metal profiles; Associations therewith of cutting devices
- B21D43/02—Advancing work in relation to the stroke of the die or tool
- B21D43/04—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work
- B21D43/05—Advancing work in relation to the stroke of the die or tool by means in mechanical engagement with the work specially adapted for multi-stage presses
- B21D43/055—Devices comprising a pair of longitudinally and laterally movable parallel transfer bars
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G25/00—Conveyors comprising a cyclically-moving, e.g. reciprocating, carrier or impeller which is disengaged from the load during the return part of its movement
- B65G25/02—Conveyors comprising a cyclically-moving, e.g. reciprocating, carrier or impeller which is disengaged from the load during the return part of its movement the carrier or impeller having different forward and return paths of movement, e.g. walking beam conveyors
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Press Drives And Press Lines (AREA)
- Automobile Manufacture Line, Endless Track Vehicle, Trailer (AREA)
- Transmission Devices (AREA)
- Special Conveying (AREA)
Abstract
ARTICLE TRANSFER MECHANISM
Abstract of the Disclosure An article transfer mechanism is disclosed comprising a pair of longitudinally and laterally reciprocable feed bars having opposed cooperable article engaging feed fingers there-between. The feed bars are supported at opposite ends for longitudinal sliding movement relative to feed bar support members which in turn are supported for linear lateral move-ment toward and away from one another. An oscillatory drive arrangement is provided at one end of the feed bars for recipro-cating the bars longitudinally, and a rotatable cam and follower lever arrangement is provided at each end of the feed bars for reciprocating the support members and thus the feed bars laterally toward and away from one another.
Abstract of the Disclosure An article transfer mechanism is disclosed comprising a pair of longitudinally and laterally reciprocable feed bars having opposed cooperable article engaging feed fingers there-between. The feed bars are supported at opposite ends for longitudinal sliding movement relative to feed bar support members which in turn are supported for linear lateral move-ment toward and away from one another. An oscillatory drive arrangement is provided at one end of the feed bars for recipro-cating the bars longitudinally, and a rotatable cam and follower lever arrangement is provided at each end of the feed bars for reciprocating the support members and thus the feed bars laterally toward and away from one another.
Description
Dlsclosllre Thi, i~erl'ion rel~te.s ~o the art o:E m~t--.ial handli.
an~l, more particll.larly, to ~ reciproc~tin~ artic.le _ransfer mec'.lanism for a~vancing ~rticles ste~ ~ step alon3 ~ linea.r feed path.
The present invention fi.~s particular uLility in connection ~Jith the step by step a~vance~ent oE a ~;or'~piece relative to a plur~lity o~ ~.7ork st~tions in a metalworki~g press. Accordin~ly, the invention will be describ~d with ~. .`
regard to such use; however, it will be appreciated that t~e invention has utility in connection with transferrin3 articles othen than press ~;or~pieces and in conjunction with a~paratus other than presses.
Transfer feed mechanisms have been provided heretofore ~ ,.
... .,, .. ., ,,,. .;, - ... ~, . ... ; .. . ~ : ~ ... ... . .
~064~349 fox advancing workpie~es step by step through a metalworking press such that a workpiece is picked up at one station, advanced to the next station and then released for the performance of work thereon by the press. Among such trans~er mechanisms are those including a pair of longi tudinally and laterally reciprocable ~eed bars having opp~sed pairs of cooperable feed fingers therebetween. The feed bars are adapted to be displaced laterally away from one another to release the fingers from engagement with an article, displaced longitudinally in one direction to-position-another set of fingers in aligmnent with the article, displaced laterally toward one another for the article to be received between the new pair of fingers, and then advanced longi-tudinally in the opposite direction to move the article to lS the next work station. Such movement is of course coordinated with the stroke of the press slide such that the engagement, transfer and release func-tions of the feed mechanism take place during the non-working portion of the total stroke of the press.
A variety of axrangements have been provided hereto-fore for imparting the longitudinal and lateral reciprocating motions to the ~eed bhrs and thus the ~eed fingexs associated therewith~ Such previous efforts have included cam and linkage ;~
assemblies including rotating cams and long linkage trains involving a number o~ p}votally interrelated component parts.
Other arrangements have included oscillating levers and linkage trains, again involving a considerable num~er or pivotally interconnected component parts. In view of th longitudinal and lateral reciprocating motions imparted to the feed bars it is necessary to have separate drive mechanisms therefore - :. . .
which genexally are driven Erom a cor~non drive source such as the crankshaft of the press so as to coordinate the operation. ~ven though the mechanisms are dr.iven by the press, a princip~l disadvantage of the mech~nisms heretofore provided S has been the inabllity to time the separate longitudinal arld lateral displacements with sufficient precision Eor high speed press operation. In this respect, links, levers, bell cranks and the like, lntroduce e.rrors through long chains o~ action which effect the ability to achieve and maintain desired timing relationships between the longitudinal and lateral displace-ments. Further, operation of a feed transfer mechanism is continuous and accordingly requires a continuous and repeated change o~ direction with respect to the feed bars~ In con- :
nection with this rec~uirement, the drive arrangements hereto- .
fore provided consume a considerable clmount o~ energy as a -~
result of heav~ links, levers, bell cranks and the like, wh~re-by high ~rictional losses are encountered which hinder high speed operation~ Thus, the inability to obtain close coord-inated action of the longitudinal and lateral drives for the ~eed bars heretofore has impeded the use of such feed mechanisms - in high speed presses~
The foregoing and other diff:iculties and disadvantages encountered in connection with previous transfer feed mech~nisms are overcome ox minimized in accordan~e with the present in~
ventlon by an improved arrangement or achieving late.ral displacement of the feed bars which minimi~e ener~y loss and :~
enables improved timing capabillties and thus higher speed press operation than heretofore possible. More particularly .:.
in accordance with the present invention, a continuou61y rotating cam is associated with the feed bars for achieving relative lateral displacement therebetween. This continu~us rotating drive arrangement enables optimizing timing of s~ch lateral reciprocation and thus coordination thereo~ ~
with longitudinal reciprocation of the reed bars. Moreover, - -by maximizimg rotary motion to achieve lateral displacement of the feed bars, energy losses her~et~fore encountered through long linkage trains is minimized. Further, by use o~ a cam in accordance with the preferred emhodiment o~ the invention, - two in and out motions of the feed bars are realized for each - 10 revolution of the cam, thus ~urther reducing eneryy losses hereto~ore encou~ltered and reducing inertia loads on the cam, thus enabling higher speed press operation. Still further, r~ciproca-ing movement of the feed bars is prefera~ly achieved through use of rotary-to-oscillatory drive mechanism, whereb~
the input to the separate drlve mechanisms ~or achieving lateral and longitudinal recipr,ocation are both rotary.
This~énables optimizing the timing between the lateral and -~
longitudinal reciprocating m~vement of the ~eed bars.
In a further aspect o~ the present invention therë~ -is provided an article transfer mechanism comprising, a~ ~ ~
`-~ palr~of horizontal feed bars laterally space~d part and hnvlng ~:
coopera~lè fèed fingers therebetween, feed bar support members ;
each supporting one of said feed bars for longitudinal recipro- ;
cation relative thereto~ means supporting said feed bar support members for linear reciprocation laterally toward and - , - . ~
away fr~m one another, means to reciprocate said feed bars .
longitudinally relative to said support members, and means to reciproeate said support members and feed bars laterally toward and away` from one another including cam means between said support members and rotatable about a vertical~axis, and laterally displaeeable fnllower means between said eam . means-and each of said ~upport members, each said ollo~er B - 4~ -;
, 34~
means interengaging said cam means and the corresponding support member for~ said follower means to displace said support members laterally in response to rotation of said cam means.
In a still further aspect of the present invention there is provided an article transfer mecha:nism comprisiny a pair of feed bars having opposite ends and opposed pairs of feed ¦
fingers between said opposite e,nds, support means at each of ¦ .
said opposite ends~ a pair of feed bar support members supporte by each sup~ort means for linear reciprocation laterally toward I
an~ away from one another, each.support member receiving and .
supporting the corresponding end o~ one of said ~eed bars ~or ¦ .
longitudinal sliding movement relative thereto, means for reciprocating said feed bars longitudinally, a pair o~
pivotal levers at each said opp~site ends, each lever of sai~
pair having o~posite ends one pivotally interconne~cted with the corresponaing support means and the other slidably engaging `~
one of the support me~bers at the corresponding one of said ~:
opposite ends, a rotatable cam between.each pair of levers, -m ans biasing each sai~ pair of ~evers toward engag~ment ¦
with-the~corresponding c~m, and means tct rotate said cams ~ ; - ~
~ .~
It is accordingl~ an-outstanding object o~ the ~ .... t :;
presént~.invention to provide an improved drive arrangement : . ..
. . . .
for a transfer feed mechanism involving longituainal and -12teral--reciprocating movements of feea-bars. . ~-: .3 Another object is the provision of an improved drive arrangement of the ~oregoing character in which the use of `:
rotary-motion is optimized t~ achieve longitudinal ana - . ~ :
lateral reciprocation of the feed bars. ~.
Yet another object is the provision of a drive 30 arrangement of the f~regoing character which minimizes energy losses and inertia on the compcnent parts, thus to ena~tle higher speed operation o* the transfer feed m~chani~m - 4a -B , I
. . . ~ ~ . ,......................... ~.
.
~0t;9~84~3 than heretofo.re possible.
Still anothel- object is the provision of a d.rive arrangement of the ~oregoing ch~racter which enables more accurate timing and close coordinati.on with respect to th~ :
longitudinal and lateral reciprocating movements imparted to the feed bars.
Still another object is the provision of a drive arrangement of the foregoing character in.which lateral reciprocation of the feed bars is achieved ~y a cam dr.i~e arrangement which enables reducing the num~er of moving parts required to achieve the desired lateral movements oE the ~eed bars and thus decreases frictional losses and inertial fQrces on the component parts to improve accuracy with respect to coordinating drives for the lateral and longitudinal move-ments and to enable higher speed operation than heretoforepossible.
The foregoing objects, and others, will in part be : ~
obvious and in part pointed out more fully hereinafter in ~ -conjunction with the written description of a preferred embodiment o~ the invention illustrated in the accompanying - drawings in which: . .
. FIGU~E 1 .is a plan view of a transfer fead mechanism in accordance with the present invention;
FIGU~E 2 is a side elevation view of the mechanis~
looXing in the direction of line 2 2 in FIGURE l;
FIGURE 3 is an end elevation view of the mechanism as seen along-line 3-3 in FIGUnE 2;
FIGURE 4 is a p-an view, partially in section, ..
o~ the drive arran~ement by ~hich the feed bars are laterally reciprocated as se~n along line 4-4 in FIGURE 3;
. - .
: :
.
8~9 FIGURE 4A is a view similar to FIGVRE 4 but sho-Ying the component parts in different positions;
FIGURE 5 is a sectional elevation view taken along line 5-5 in FIGURE 4; and, FIGURE 6 is a sectional elevation view taken alon~
line 6-6 in FIGURE 4.
~eferring now in greater detail to the drawings where-in the showings are for the purpose of illustrating a pre-ferred embodiment of the invention only and not for the purpose of limiting the same, FIGURES 1~3 illustrate a trans;Eer feed 1.5 mechanism for use with a press in which a workpiece is to be transferred step by step to ~a plurality of successive work stations between opposite sides of the press. As i5 ;well known in the art, workpieces are conveyed to the input end of the transfer mechanism and are mvved step by step across the press bed or a bolster plate thereon to the exit :.:
end of the transfer mechanism at which point the workpieces are picked up by a suitable discharge conveying mechanism~
Accordingly, it will be appreciated w.ith regard to FIGURES 1-3 that the transfex feed mechanism designated generally by the numeral 10 is mounted on the press frame to span the press bed such that workpieces W are transferred across the press bed from input end 12 to discharge end 14 of the transfer mechanism. Basically, the transfer feed mechanism includes a pair of parallel feed baxs 16 carrying a plurality of opposed pairs of feed fingers 1~ along the lengths thereof. Typically, .
. ~ - , , : ~ :
48~5~
hars 16 are re~iprocated lon~itudlnally and laterally :in ~
pattern which provides for ingers 18 to move late.rally apart to release a workpiece therebetw~en, to move longitudinally in the direction of input end 12 of the mechanism, to move laterally inwardly to grip a new workpiece therebetween, and then to move longitudinally in the direction o~ output end 14 o~ the mechan-ism to transfer the workpiece to the next work station~
In the embodiment illustrated, feed bars 16 are longi-tudinally reciprocated by means of a drive unit 20 at the input end o~ the feed mechanism and are laterally reciprocated by means of a drive unit 22 at the input end of the m~chanism and a similar drive unit 24 at the discharge end of the drive unit and which is driven in synchronism with drive unit 22 through a cross shaft 23 therebetween. ~s will be described in greater lS detail hereina~ter, the opposite e~ds of feed bars 16 are supported for longikudinal and,lateral reciprocation relative ~ ~`
to the press bed by components of drive units 22 and 24.
Drive~uni~ 20 is a mechanism adapted to translate rotary motion in~o oscillating motion and, in the preferred embodiment, is a well known and commercially available Ferguson Cam Box. As is well known in the art, suc~ a.unit has a rotatable input shaft 26 and an output shart 28 which oscillates in response to rotation of shaft 26. In connection with the transfer ~eed mechanism of the present invention, one end of input shaft 26 is connected to the press crankshaft, not shown., through a timing belt 30 so that oscillation of output sha~t 28 is timed with respect to the press drive. Xnput shaft 26 extends through the cam box and the other end o~
the shaft is connected with an input shaft 32 of drive unit 22 through a timing belt 34O The timing belt provides fox the .~- .
1~6~89~9 operation of drive units 22 and 2~ to be synchronized with the osclllatin~ movements of outpu-t sha~t 28 of drive unit 20.
It w.ill be appreciated of course khat drive unit 20 is suitabl~
mounted on the press frame such as by a bracket assembly 36 and that drive units 22 and 24 are like~ise suitably mounted on the press ~rame such as by corresponding bracket assemblies 38. Output shaft 28 o~ drive unit ~0 is coupled to a member 40 provided with a pair o~ laterally spaced apart arms 42, and feed bars 16 are reciprocated together longi-tudinally by means of corresponding wobble links ~4 coupledto arms 4~ by universal couplings 46 and to feed bars 16 by universal couplings 48.
In accordance with the present invention, feed bars 16 are laterally reciprocated xelative to one another and to the press bed by means o~ drive units 22 and 24. The latter drive units are substantially identical in structure and :.
operation and the differences therebetween will be apparent and will be pointed out hereinafter in conjunction with the description of drive unit 22 illustrated in FIGURES 4-6 of the drawing. With regard to the latter Figures, drive unit 22 includes a housing 5~ provided with a cover 52~
The end of housing 50 ~acing the press is open to receive the corresponding ends of ~eed bars 16, and the latter ends of the feed bars are longitudinally slidably received in ~5 corresponding feed bar suppor-t members 54. More particularly, each member 54 is provided with a recess 55 sli.dably re~eivin~
the corresponding feed bar and which recess is covered by a plate 56 to retain the feed bar against upward displacement relative to the support membersO Each support member 54 is provided with a pair of parallel laterally extending openings 58 . . ; , . . .
:~. . . - . . : .
~0~41~
receiving correspondlng laterally extenc1ing guide rods 60 having opposite ends fastened in place with respect to housincJ
50 such as by corresponding brackets 62. Preferably, bearing sleeves 64 are interposed betwe2n openinys 58 and rods 60 to ; 5 enhance lateral sliding of support me~bers $4 along the guide rods.
Housing S0 is urther provided with a circular posk 66 which is fixed relative to the housing and which supports a driven gear 68 for rotation about the vertical axis of pos~
0 66. Gear 68 has a hub portion 70 providing a shoulder 72, and an apertured cam member 74 receives hub 70 and rests -on shoulder 72. cam 74 is suitably a~tached to gear 68, such as by a shrink fit therebetween, so that the cam is rotatable with the gear. Cam 74 is a double cam having a maior axis 76 and a minor axis 78 and a peripheral cam sur-face 80 which is identical in ~ach o the rour quadrants defined by the major and minor axes.
A pair of follower levers 82 are disposed between cam 74 and a corresponding one o the feed bar support me~bers 54O Each iever 82 has one end 84 pivotally int rconnectad with housing S0 and its other end 86 interconnected with the corresponding support member 54 for sliding engagement therewith. Further, each lever is provided intermediate its opposite ends with depending follower rollers 88, which rollers engage diametrically opposite sides oE cam surface 80 o~ cam 74~ Follower rollers 88 are biased toward cam surface 80 by means of a pair o~ tension springs 90 each having their opposite ends connected to one of the feed bar support memb2rs - 54 such as by means of pins 92, It will be appreciated from the description thus far-1~4l~4~
of drive unit 22 Lhat rotation of gear 68 rotates cam 74 about the axis of post G6 and that such rotation of the carn imparts reciprocating movement to ~eed bar support members 54 laterally toward and away from one anokher. It will be appreciated too that when the cam cornponent is in the position illustrated in E'IGURE 4 support members 54 are in the positions of maximum lateral spacing therebetween, and when the cam component is in the position illustrated in FIGURh 4A support members 54 are in the positions o~ rninimum lateral spacing therebetween. It will be further appreciated that double cam 74 provides for lateral outward and inward movement of members 54 twice for each revolutlon of the cam, that the cam drives support members 54 outwardly against the bias of springs 90, and that the sprin~s return the support me~bers inwardly as the cam rotates from the position of E'IGU~E 4 to that of FIGURE 4A.
Gear 68 is adapted to be rotated constantly through a gear train driven in response to rotation o~ input shaft 32 - and including, in sequence from input shaft 32, gears 94, 96, 98 and 100. As mentioned hereinabove, drive units 22 and 2 are adapted to be driven in synchronism through cross shaft 23. Input shaft 32 of drive unit 22 extends throu~h housing 50, and it will be seen from FIGURE 4 that input shaft 32 is coupled with cross shaft 23 by means of a suitable coupling 1~2.
Drive unit 22 further includes an au~iliary cam 104 havin~ cam lobes 106 normall~ positioned as shown in FIGURE 4. Cam 104 is mounted on post 66 fox rotation relative thereto and relative to cam 74, and lobes 10~ are coplanar with levers 82. When feed bar support members 54 are in 1(~64~
the laterally inward positions sho~n in FIGU~E 4~, c~m 104 is adapted to be pivoted to displace lobes 106 into engaye-ment with the sides of levers 82. This displaces the levers 82 and thus support members 54 laterall~ out~ardly independent o~ cam 74. This provides for an emergency release of the feed fingers oE feed bars 16 relative to workpieces there-between in the event a mal~unction o~ other emergency condition.
In the embodiment shown, cam 104 is adapted to be pivoted clockwis as viewed in FIGURE 4 to achieve such spreading of the feèd bars by means of a pneumatic piston and cylinder unit 108. More particulaxly, unit 108 inc~udes a cylinder 110 mounted on housing 50 and supportin~ a recipro-cable piston 112 having a piston rod 114 extendin~ through an opening in the housing. The inner end of piston rod 114 is connected with cam 104 by me,ans of a connectiny link 116 having its opposite ends pivotally interconnected one with the piston rod and the other with cam 104. Return movement o~ c~m 104 to the position shown in FIGU~E 4 is achieved through a tension spring 118 having its opposite ends connected to cam 104 and housing 50. It will be appreciated of course that cylinder 110 is connected to a suitable source of air under pressure, not shown.
As mentioned hexeinabove, drive units 22 and 24 are substantially identical in structurer In ~act, the only difference i5 a reversal of the positions of the component parts to provide :Eor unit 24 to be driven from the same side as the input to unit 22, and to position auxiliary cam actuatox 108 ~or unit 24 on the same side as that of unit 22. It will appreciated thak cross shaEt 23 is connected throu~h a .
L8~
coupliny 120 ~ith an input sha~t o:E drive unit 2~ equivalent to input shaEt 3~ of unit 22. Accordingly, rotation oE input shaEt 32 of unit 22 imparts identical rotation to the .input shaft of unit 24, whereby the two units are driven in synchxonism to achieve simultaneous lateral reciprocation of feed bars 16 outwardly and inwardly relative to one another. It will be appreciated too that piston cylinder units 108 of drive unit~ 2~
and 24 can be connected to a common source of air under presisure and can be operated toyether.
It will be understood from the foregoing description that the transfer feed mechanism is operated through the press and in timed coordination therewith through timing belt 30.
Further, it will be appreciated that the operation of drive.
unit 20 is coordinated with the operation of drive units 22 and 24 through timing belt 2~ between units 20 and 22.
Thus, xotation of timiny belt 3~0 through operation of the press imparts oscillating movement to output shaft 28 to reciprocate feed bars 16 longitudinally relative to th~
press and rotation of input shaft 32 of drive unit 22 throuyh timing belt 34 causes reciprocation of the feed bars laterally .relative to one another in timed coordination with such longi~
tudinal reciprocation. Therefore, during a cycle or operation feed bars 16 are displaced longitudinally in one direction while in their laterally inward posltions, are displaced laterali~
outwardly relative to one anOther, are displaced longitudinally in the opposite direction, and are displaced laterally inwardly - toward one another to complete the cycle. Duriny each cycle o~ movement double cam 74 rotates one-half revolution~ It will be appreciated, therefore, that the press will perform two work-ing operations for each full revolution oE cam 74, thus ;: .- . . . ~ ~
1~64~4~3 minimizing the inerti.a of workin~ parts of drive units 2 and 24 relative to that which would be encountered with mechanisms re~uiring a complete cycle o:E operation oE these parts with each cycle vf press operation. Additionally, it will be appreciated that a continuous rotational drive for units 22 and 24 with minimum use of linkage arrangements between the various component parts thereof minimizes energy losses and inaccuracies in timing ~Jith regard to coordinating movements of the feed bars in the longitudinal.and lateral directions.
While considerable emphasis has been placed herein on the specific st.ructure and structuYal interrelationships between the con~onent parts of drive units 22 and 24, it will be appreciated that many modi~ications can be made in the structures shown and described without depa.rting ~rom the principles o~ the present ~nvention. Accordingly, it is to be distinctly unaerstood that the foregoing descriptive matter is to be intexpreted merely as illustrative of the - present invention and not as d limitation.
. .
- 13 ~
.
an~l, more particll.larly, to ~ reciproc~tin~ artic.le _ransfer mec'.lanism for a~vancing ~rticles ste~ ~ step alon3 ~ linea.r feed path.
The present invention fi.~s particular uLility in connection ~Jith the step by step a~vance~ent oE a ~;or'~piece relative to a plur~lity o~ ~.7ork st~tions in a metalworki~g press. Accordin~ly, the invention will be describ~d with ~. .`
regard to such use; however, it will be appreciated that t~e invention has utility in connection with transferrin3 articles othen than press ~;or~pieces and in conjunction with a~paratus other than presses.
Transfer feed mechanisms have been provided heretofore ~ ,.
... .,, .. ., ,,,. .;, - ... ~, . ... ; .. . ~ : ~ ... ... . .
~064~349 fox advancing workpie~es step by step through a metalworking press such that a workpiece is picked up at one station, advanced to the next station and then released for the performance of work thereon by the press. Among such trans~er mechanisms are those including a pair of longi tudinally and laterally reciprocable ~eed bars having opp~sed pairs of cooperable feed fingers therebetween. The feed bars are adapted to be displaced laterally away from one another to release the fingers from engagement with an article, displaced longitudinally in one direction to-position-another set of fingers in aligmnent with the article, displaced laterally toward one another for the article to be received between the new pair of fingers, and then advanced longi-tudinally in the opposite direction to move the article to lS the next work station. Such movement is of course coordinated with the stroke of the press slide such that the engagement, transfer and release func-tions of the feed mechanism take place during the non-working portion of the total stroke of the press.
A variety of axrangements have been provided hereto-fore for imparting the longitudinal and lateral reciprocating motions to the ~eed bhrs and thus the ~eed fingexs associated therewith~ Such previous efforts have included cam and linkage ;~
assemblies including rotating cams and long linkage trains involving a number o~ p}votally interrelated component parts.
Other arrangements have included oscillating levers and linkage trains, again involving a considerable num~er or pivotally interconnected component parts. In view of th longitudinal and lateral reciprocating motions imparted to the feed bars it is necessary to have separate drive mechanisms therefore - :. . .
which genexally are driven Erom a cor~non drive source such as the crankshaft of the press so as to coordinate the operation. ~ven though the mechanisms are dr.iven by the press, a princip~l disadvantage of the mech~nisms heretofore provided S has been the inabllity to time the separate longitudinal arld lateral displacements with sufficient precision Eor high speed press operation. In this respect, links, levers, bell cranks and the like, lntroduce e.rrors through long chains o~ action which effect the ability to achieve and maintain desired timing relationships between the longitudinal and lateral displace-ments. Further, operation of a feed transfer mechanism is continuous and accordingly requires a continuous and repeated change o~ direction with respect to the feed bars~ In con- :
nection with this rec~uirement, the drive arrangements hereto- .
fore provided consume a considerable clmount o~ energy as a -~
result of heav~ links, levers, bell cranks and the like, wh~re-by high ~rictional losses are encountered which hinder high speed operation~ Thus, the inability to obtain close coord-inated action of the longitudinal and lateral drives for the ~eed bars heretofore has impeded the use of such feed mechanisms - in high speed presses~
The foregoing and other diff:iculties and disadvantages encountered in connection with previous transfer feed mech~nisms are overcome ox minimized in accordan~e with the present in~
ventlon by an improved arrangement or achieving late.ral displacement of the feed bars which minimi~e ener~y loss and :~
enables improved timing capabillties and thus higher speed press operation than heretofore possible. More particularly .:.
in accordance with the present invention, a continuou61y rotating cam is associated with the feed bars for achieving relative lateral displacement therebetween. This continu~us rotating drive arrangement enables optimizing timing of s~ch lateral reciprocation and thus coordination thereo~ ~
with longitudinal reciprocation of the reed bars. Moreover, - -by maximizimg rotary motion to achieve lateral displacement of the feed bars, energy losses her~et~fore encountered through long linkage trains is minimized. Further, by use o~ a cam in accordance with the preferred emhodiment o~ the invention, - two in and out motions of the feed bars are realized for each - 10 revolution of the cam, thus ~urther reducing eneryy losses hereto~ore encou~ltered and reducing inertia loads on the cam, thus enabling higher speed press operation. Still further, r~ciproca-ing movement of the feed bars is prefera~ly achieved through use of rotary-to-oscillatory drive mechanism, whereb~
the input to the separate drlve mechanisms ~or achieving lateral and longitudinal recipr,ocation are both rotary.
This~énables optimizing the timing between the lateral and -~
longitudinal reciprocating m~vement of the ~eed bars.
In a further aspect o~ the present invention therë~ -is provided an article transfer mechanism comprising, a~ ~ ~
`-~ palr~of horizontal feed bars laterally space~d part and hnvlng ~:
coopera~lè fèed fingers therebetween, feed bar support members ;
each supporting one of said feed bars for longitudinal recipro- ;
cation relative thereto~ means supporting said feed bar support members for linear reciprocation laterally toward and - , - . ~
away fr~m one another, means to reciprocate said feed bars .
longitudinally relative to said support members, and means to reciproeate said support members and feed bars laterally toward and away` from one another including cam means between said support members and rotatable about a vertical~axis, and laterally displaeeable fnllower means between said eam . means-and each of said ~upport members, each said ollo~er B - 4~ -;
, 34~
means interengaging said cam means and the corresponding support member for~ said follower means to displace said support members laterally in response to rotation of said cam means.
In a still further aspect of the present invention there is provided an article transfer mecha:nism comprisiny a pair of feed bars having opposite ends and opposed pairs of feed ¦
fingers between said opposite e,nds, support means at each of ¦ .
said opposite ends~ a pair of feed bar support members supporte by each sup~ort means for linear reciprocation laterally toward I
an~ away from one another, each.support member receiving and .
supporting the corresponding end o~ one of said ~eed bars ~or ¦ .
longitudinal sliding movement relative thereto, means for reciprocating said feed bars longitudinally, a pair o~
pivotal levers at each said opp~site ends, each lever of sai~
pair having o~posite ends one pivotally interconne~cted with the corresponaing support means and the other slidably engaging `~
one of the support me~bers at the corresponding one of said ~:
opposite ends, a rotatable cam between.each pair of levers, -m ans biasing each sai~ pair of ~evers toward engag~ment ¦
with-the~corresponding c~m, and means tct rotate said cams ~ ; - ~
~ .~
It is accordingl~ an-outstanding object o~ the ~ .... t :;
presént~.invention to provide an improved drive arrangement : . ..
. . . .
for a transfer feed mechanism involving longituainal and -12teral--reciprocating movements of feea-bars. . ~-: .3 Another object is the provision of an improved drive arrangement of the ~oregoing character in which the use of `:
rotary-motion is optimized t~ achieve longitudinal ana - . ~ :
lateral reciprocation of the feed bars. ~.
Yet another object is the provision of a drive 30 arrangement of the f~regoing character which minimizes energy losses and inertia on the compcnent parts, thus to ena~tle higher speed operation o* the transfer feed m~chani~m - 4a -B , I
. . . ~ ~ . ,......................... ~.
.
~0t;9~84~3 than heretofo.re possible.
Still anothel- object is the provision of a d.rive arrangement of the ~oregoing ch~racter which enables more accurate timing and close coordinati.on with respect to th~ :
longitudinal and lateral reciprocating movements imparted to the feed bars.
Still another object is the provision of a drive arrangement of the foregoing character in.which lateral reciprocation of the feed bars is achieved ~y a cam dr.i~e arrangement which enables reducing the num~er of moving parts required to achieve the desired lateral movements oE the ~eed bars and thus decreases frictional losses and inertial fQrces on the component parts to improve accuracy with respect to coordinating drives for the lateral and longitudinal move-ments and to enable higher speed operation than heretoforepossible.
The foregoing objects, and others, will in part be : ~
obvious and in part pointed out more fully hereinafter in ~ -conjunction with the written description of a preferred embodiment o~ the invention illustrated in the accompanying - drawings in which: . .
. FIGU~E 1 .is a plan view of a transfer fead mechanism in accordance with the present invention;
FIGU~E 2 is a side elevation view of the mechanis~
looXing in the direction of line 2 2 in FIGURE l;
FIGURE 3 is an end elevation view of the mechanism as seen along-line 3-3 in FIGUnE 2;
FIGURE 4 is a p-an view, partially in section, ..
o~ the drive arran~ement by ~hich the feed bars are laterally reciprocated as se~n along line 4-4 in FIGURE 3;
. - .
: :
.
8~9 FIGURE 4A is a view similar to FIGVRE 4 but sho-Ying the component parts in different positions;
FIGURE 5 is a sectional elevation view taken along line 5-5 in FIGURE 4; and, FIGURE 6 is a sectional elevation view taken alon~
line 6-6 in FIGURE 4.
~eferring now in greater detail to the drawings where-in the showings are for the purpose of illustrating a pre-ferred embodiment of the invention only and not for the purpose of limiting the same, FIGURES 1~3 illustrate a trans;Eer feed 1.5 mechanism for use with a press in which a workpiece is to be transferred step by step to ~a plurality of successive work stations between opposite sides of the press. As i5 ;well known in the art, workpieces are conveyed to the input end of the transfer mechanism and are mvved step by step across the press bed or a bolster plate thereon to the exit :.:
end of the transfer mechanism at which point the workpieces are picked up by a suitable discharge conveying mechanism~
Accordingly, it will be appreciated w.ith regard to FIGURES 1-3 that the transfex feed mechanism designated generally by the numeral 10 is mounted on the press frame to span the press bed such that workpieces W are transferred across the press bed from input end 12 to discharge end 14 of the transfer mechanism. Basically, the transfer feed mechanism includes a pair of parallel feed baxs 16 carrying a plurality of opposed pairs of feed fingers 1~ along the lengths thereof. Typically, .
. ~ - , , : ~ :
48~5~
hars 16 are re~iprocated lon~itudlnally and laterally :in ~
pattern which provides for ingers 18 to move late.rally apart to release a workpiece therebetw~en, to move longitudinally in the direction of input end 12 of the mechanism, to move laterally inwardly to grip a new workpiece therebetween, and then to move longitudinally in the direction o~ output end 14 o~ the mechan-ism to transfer the workpiece to the next work station~
In the embodiment illustrated, feed bars 16 are longi-tudinally reciprocated by means of a drive unit 20 at the input end o~ the feed mechanism and are laterally reciprocated by means of a drive unit 22 at the input end of the m~chanism and a similar drive unit 24 at the discharge end of the drive unit and which is driven in synchronism with drive unit 22 through a cross shaft 23 therebetween. ~s will be described in greater lS detail hereina~ter, the opposite e~ds of feed bars 16 are supported for longikudinal and,lateral reciprocation relative ~ ~`
to the press bed by components of drive units 22 and 24.
Drive~uni~ 20 is a mechanism adapted to translate rotary motion in~o oscillating motion and, in the preferred embodiment, is a well known and commercially available Ferguson Cam Box. As is well known in the art, suc~ a.unit has a rotatable input shaft 26 and an output shart 28 which oscillates in response to rotation of shaft 26. In connection with the transfer ~eed mechanism of the present invention, one end of input shaft 26 is connected to the press crankshaft, not shown., through a timing belt 30 so that oscillation of output sha~t 28 is timed with respect to the press drive. Xnput shaft 26 extends through the cam box and the other end o~
the shaft is connected with an input shaft 32 of drive unit 22 through a timing belt 34O The timing belt provides fox the .~- .
1~6~89~9 operation of drive units 22 and 2~ to be synchronized with the osclllatin~ movements of outpu-t sha~t 28 of drive unit 20.
It w.ill be appreciated of course khat drive unit 20 is suitabl~
mounted on the press frame such as by a bracket assembly 36 and that drive units 22 and 24 are like~ise suitably mounted on the press ~rame such as by corresponding bracket assemblies 38. Output shaft 28 o~ drive unit ~0 is coupled to a member 40 provided with a pair o~ laterally spaced apart arms 42, and feed bars 16 are reciprocated together longi-tudinally by means of corresponding wobble links ~4 coupledto arms 4~ by universal couplings 46 and to feed bars 16 by universal couplings 48.
In accordance with the present invention, feed bars 16 are laterally reciprocated xelative to one another and to the press bed by means o~ drive units 22 and 24. The latter drive units are substantially identical in structure and :.
operation and the differences therebetween will be apparent and will be pointed out hereinafter in conjunction with the description of drive unit 22 illustrated in FIGURES 4-6 of the drawing. With regard to the latter Figures, drive unit 22 includes a housing 5~ provided with a cover 52~
The end of housing 50 ~acing the press is open to receive the corresponding ends of ~eed bars 16, and the latter ends of the feed bars are longitudinally slidably received in ~5 corresponding feed bar suppor-t members 54. More particularly, each member 54 is provided with a recess 55 sli.dably re~eivin~
the corresponding feed bar and which recess is covered by a plate 56 to retain the feed bar against upward displacement relative to the support membersO Each support member 54 is provided with a pair of parallel laterally extending openings 58 . . ; , . . .
:~. . . - . . : .
~0~41~
receiving correspondlng laterally extenc1ing guide rods 60 having opposite ends fastened in place with respect to housincJ
50 such as by corresponding brackets 62. Preferably, bearing sleeves 64 are interposed betwe2n openinys 58 and rods 60 to ; 5 enhance lateral sliding of support me~bers $4 along the guide rods.
Housing S0 is urther provided with a circular posk 66 which is fixed relative to the housing and which supports a driven gear 68 for rotation about the vertical axis of pos~
0 66. Gear 68 has a hub portion 70 providing a shoulder 72, and an apertured cam member 74 receives hub 70 and rests -on shoulder 72. cam 74 is suitably a~tached to gear 68, such as by a shrink fit therebetween, so that the cam is rotatable with the gear. Cam 74 is a double cam having a maior axis 76 and a minor axis 78 and a peripheral cam sur-face 80 which is identical in ~ach o the rour quadrants defined by the major and minor axes.
A pair of follower levers 82 are disposed between cam 74 and a corresponding one o the feed bar support me~bers 54O Each iever 82 has one end 84 pivotally int rconnectad with housing S0 and its other end 86 interconnected with the corresponding support member 54 for sliding engagement therewith. Further, each lever is provided intermediate its opposite ends with depending follower rollers 88, which rollers engage diametrically opposite sides oE cam surface 80 o~ cam 74~ Follower rollers 88 are biased toward cam surface 80 by means of a pair o~ tension springs 90 each having their opposite ends connected to one of the feed bar support memb2rs - 54 such as by means of pins 92, It will be appreciated from the description thus far-1~4l~4~
of drive unit 22 Lhat rotation of gear 68 rotates cam 74 about the axis of post G6 and that such rotation of the carn imparts reciprocating movement to ~eed bar support members 54 laterally toward and away from one anokher. It will be appreciated too that when the cam cornponent is in the position illustrated in E'IGURE 4 support members 54 are in the positions of maximum lateral spacing therebetween, and when the cam component is in the position illustrated in FIGURh 4A support members 54 are in the positions o~ rninimum lateral spacing therebetween. It will be further appreciated that double cam 74 provides for lateral outward and inward movement of members 54 twice for each revolutlon of the cam, that the cam drives support members 54 outwardly against the bias of springs 90, and that the sprin~s return the support me~bers inwardly as the cam rotates from the position of E'IGU~E 4 to that of FIGURE 4A.
Gear 68 is adapted to be rotated constantly through a gear train driven in response to rotation o~ input shaft 32 - and including, in sequence from input shaft 32, gears 94, 96, 98 and 100. As mentioned hereinabove, drive units 22 and 2 are adapted to be driven in synchronism through cross shaft 23. Input shaft 32 of drive unit 22 extends throu~h housing 50, and it will be seen from FIGURE 4 that input shaft 32 is coupled with cross shaft 23 by means of a suitable coupling 1~2.
Drive unit 22 further includes an au~iliary cam 104 havin~ cam lobes 106 normall~ positioned as shown in FIGURE 4. Cam 104 is mounted on post 66 fox rotation relative thereto and relative to cam 74, and lobes 10~ are coplanar with levers 82. When feed bar support members 54 are in 1(~64~
the laterally inward positions sho~n in FIGU~E 4~, c~m 104 is adapted to be pivoted to displace lobes 106 into engaye-ment with the sides of levers 82. This displaces the levers 82 and thus support members 54 laterall~ out~ardly independent o~ cam 74. This provides for an emergency release of the feed fingers oE feed bars 16 relative to workpieces there-between in the event a mal~unction o~ other emergency condition.
In the embodiment shown, cam 104 is adapted to be pivoted clockwis as viewed in FIGURE 4 to achieve such spreading of the feèd bars by means of a pneumatic piston and cylinder unit 108. More particulaxly, unit 108 inc~udes a cylinder 110 mounted on housing 50 and supportin~ a recipro-cable piston 112 having a piston rod 114 extendin~ through an opening in the housing. The inner end of piston rod 114 is connected with cam 104 by me,ans of a connectiny link 116 having its opposite ends pivotally interconnected one with the piston rod and the other with cam 104. Return movement o~ c~m 104 to the position shown in FIGU~E 4 is achieved through a tension spring 118 having its opposite ends connected to cam 104 and housing 50. It will be appreciated of course that cylinder 110 is connected to a suitable source of air under pressure, not shown.
As mentioned hexeinabove, drive units 22 and 24 are substantially identical in structurer In ~act, the only difference i5 a reversal of the positions of the component parts to provide :Eor unit 24 to be driven from the same side as the input to unit 22, and to position auxiliary cam actuatox 108 ~or unit 24 on the same side as that of unit 22. It will appreciated thak cross shaEt 23 is connected throu~h a .
L8~
coupliny 120 ~ith an input sha~t o:E drive unit 2~ equivalent to input shaEt 3~ of unit 22. Accordingly, rotation oE input shaEt 32 of unit 22 imparts identical rotation to the .input shaft of unit 24, whereby the two units are driven in synchxonism to achieve simultaneous lateral reciprocation of feed bars 16 outwardly and inwardly relative to one another. It will be appreciated too that piston cylinder units 108 of drive unit~ 2~
and 24 can be connected to a common source of air under presisure and can be operated toyether.
It will be understood from the foregoing description that the transfer feed mechanism is operated through the press and in timed coordination therewith through timing belt 30.
Further, it will be appreciated that the operation of drive.
unit 20 is coordinated with the operation of drive units 22 and 24 through timing belt 2~ between units 20 and 22.
Thus, xotation of timiny belt 3~0 through operation of the press imparts oscillating movement to output shaft 28 to reciprocate feed bars 16 longitudinally relative to th~
press and rotation of input shaft 32 of drive unit 22 throuyh timing belt 34 causes reciprocation of the feed bars laterally .relative to one another in timed coordination with such longi~
tudinal reciprocation. Therefore, during a cycle or operation feed bars 16 are displaced longitudinally in one direction while in their laterally inward posltions, are displaced laterali~
outwardly relative to one anOther, are displaced longitudinally in the opposite direction, and are displaced laterally inwardly - toward one another to complete the cycle. Duriny each cycle o~ movement double cam 74 rotates one-half revolution~ It will be appreciated, therefore, that the press will perform two work-ing operations for each full revolution oE cam 74, thus ;: .- . . . ~ ~
1~64~4~3 minimizing the inerti.a of workin~ parts of drive units 2 and 24 relative to that which would be encountered with mechanisms re~uiring a complete cycle o:E operation oE these parts with each cycle vf press operation. Additionally, it will be appreciated that a continuous rotational drive for units 22 and 24 with minimum use of linkage arrangements between the various component parts thereof minimizes energy losses and inaccuracies in timing ~Jith regard to coordinating movements of the feed bars in the longitudinal.and lateral directions.
While considerable emphasis has been placed herein on the specific st.ructure and structuYal interrelationships between the con~onent parts of drive units 22 and 24, it will be appreciated that many modi~ications can be made in the structures shown and described without depa.rting ~rom the principles o~ the present ~nvention. Accordingly, it is to be distinctly unaerstood that the foregoing descriptive matter is to be intexpreted merely as illustrative of the - present invention and not as d limitation.
. .
- 13 ~
.
Claims (20)
1. In article transfer mechanism comprising, a pair of horizontal feed bars laterally spaced apart and having cooperable fingers therebetween, feed bar support members each supporting one of said feed bars for longitudinal recipro-cation relative thereto, means supporting said feed bar support members for linear reciprocation laterally toward and away from one another, means to reciprocate said feed bars longitudinally relative to said support members, and means to reciprocate said support members and feed bars laterally toward and away from one another including cam means between said support members and rotatable about a vertical axis, and laterally displaceable follower means between said cam means and each of said support members, each said follower means interengaging said cam means-and the corresponding.
support member for said follower means to displace said support members laterally in response to rotation of said cam means.
support member for said follower means to displace said support members laterally in response to rotation of said cam means.
2. The transfer mechanism according to claim 1, wherein said feed bars have opposite ends, said support members, cam means and follower means being provided at each of said opposite ends, and means interconnecting said cam means at said opposite ends for synchronous rotation.
3. The transfer mechanism according to claim 1, wherein said follower means includes means biasing said support members laterally toward one another, said cam means displacing said support members laterally away from one another against said bias.
4. The transfer mechanism according to claim 3, and pivotal cam means between said feed bars selectively operable independent of said rotatable cam means to displace said feed bars and support members laterally away from one another against said bias, and means to pivot said pivotal cam means.
5. The transfer mechanism according to claim 1, wherein said means supporting said support members includes housing means and wherein said follower means includes a follower lever laterally between and interengaging said cam means and each said support member, each said follower lever having opposite ends, one of said ends being pivotally interconnected with said housing means and the other of said ends slidably engaging the corres-ponding support member, said cam means being positioned between said opposite ends of said follower levers.
6. The transfer mechanism according to claim 5, wherein said follower means includes means biasing said follower levers laterally toward one another into engagement with said cam means.
7. The transfer mechanism according to claim 6, wherein said biasing means is spring means interconnecting and biasing said support members toward one another and into engagement with said other ends of the corresponding support member.
8. The transfer mechanism according to claim 7, wherein said feed bars have opposite ends, said housing means, support members, follower levers and cam means being provided at each of said opposite ends, and means interconnecting said cam means at said opposite ends for synchronous rotation.
9. The transfer mechanism according to claim 8, and pivotal cam means between said feed bars at each of said opposite ends and operable independent of said rotatable cam means to displace the corresponding ends of said feed bars laterally away from one another against the bias of said spring means, and means to pivot said pivotal cam means.
10. An article transfer mechanism comprising a pair of feed bars having opposite ends and opposed pairs of feed fingers between said opposite ends, support means at each of said opposite ends, a pair of feed bar support members supported by each support means for linear reciprocation laterally toward and away from one another, each support member receiving and supporting the corresponding end of one of said feed bars for longitudinal sliding movement relative thereto, means for reciprocating said feed bars longitudinally, a pair of pivotal levers at each said opposite ends, each lever of said pair having opposite ends one pivotally interconnected with the corresponding support means and the other slidably engaging one of the support members at the corresponding one of said opposite ends, a rotatable cam between each pair of levers, means biasing each said pair of levers toward engagement with the corresponding cam, and means to rotate said cams for said cam levers and biasing means to laterally reciprocate said support members and feed bars laterally toward and away from one another.
11. The transfer mechanism according to claim 10, wherein said biasing means is spring means between each said pair of support members.
12. The transfer mechanism according to claim 10, wherein said means to rotate said cams includes common drive means for rotating said cams in synchronism.
13. The transfer mechanism according to claim 10, and a pivotal cam between each said pair of levers at each said opposite ends of said feed bars, said pivotal cam being operable independent of the rotatable cam at the corresponding end of said feed bars to engage said levers and displace said feed bars and support members at the corresponding end laterally away from one another, and means to pivot said pivotal cams.
14. The transfer mechanism according to claim 13, wherein said rotatable and pivotal cams at each of said opposite ends are coaxial with one another.
15. The transfer mechanism according to claim 14, wherein said means for pivoting said pivotal cams includes corresponding pneumatic motor means and spring means, said motor means pivoting said pivotal cams in one direction and said spring means biasing said pivotal cams in the opposite direction.
16. The transfer mechanism according to claim 10, wherein each said rotatable cam is rotatable about an axis perpendicular to the plane of lateral movement of said feed bars.
17. The transfer mechanism according to claim 16, wherein the levers of each said pairs of levers are pivotal about axes parallel to and spaced from said cam axis.
18. The transfer mechanism according to claim 17, wherein said biasing means is spring means between each said pair of support members.
19. The transfer mechanism according to claim 18, wherein said means to rotate said cams includes common drive means for rotating said cams in'synchronism.
20. The transfer mechanism according to claim 19, and a pivotal cam between each said pair of levers at each said opposite ends of said feed bars, said pivotal cams being coaxial with the corresponding rotatable cam and operable independent thereof to engage the corresponding pair of levers and displace said feed bars and support members at the corresponding end laterally away from one another, and means to simultaneously pivot said pivotal cams.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US75408276A | 1976-12-23 | 1976-12-23 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1064849A true CA1064849A (en) | 1979-10-23 |
Family
ID=25033410
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA288,381A Expired CA1064849A (en) | 1976-12-23 | 1977-10-07 | Article transfer mechanism |
Country Status (7)
| Country | Link |
|---|---|
| JP (1) | JPS53104481A (en) |
| AU (1) | AU510543B2 (en) |
| CA (1) | CA1064849A (en) |
| DE (2) | DE2756096C2 (en) |
| FR (1) | FR2375117B1 (en) |
| GB (1) | GB1584576A (en) |
| IT (1) | IT1090924B (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3227476A1 (en) * | 1982-07-22 | 1984-01-26 | Iosif Isaakovič Kramatorsk Donezkaja oblast' Kaganovskij | Transport unit for coils wound onto reels |
| GB8311035D0 (en) * | 1983-04-22 | 1983-05-25 | Mead Corp | Spacing and conveying articles in packaging machine |
| US4691819A (en) * | 1984-04-09 | 1987-09-08 | Hallstrom Jr Olof A | Reciprocating conveyor |
| DE3627866A1 (en) * | 1986-08-16 | 1988-02-18 | Adolf Wuensch | TRANSPORTATION DEVICE |
| CN113182806B (en) * | 2021-06-04 | 2024-07-19 | 合肥正进自动化设备有限公司 | Step-by-step type lock clamping machine |
Family Cites Families (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE270636C (en) * | ||||
| CH297635A (en) * | 1951-12-19 | 1954-03-31 | Hans Dr Lanz | Device for placing bottles in crates. |
| GB928719A (en) * | 1959-08-24 | 1963-06-12 | Hordern Mason & Edwards Ltd | Improvements in or relating to transfer feed mechanism |
| DE1272687B (en) * | 1963-01-30 | 1968-07-11 | Textron Ind Inc | Cross conveyor on multi-stage presses for producing bolts, nuts or the like. |
| US3187883A (en) * | 1963-03-04 | 1965-06-08 | Ajem Lab Inc | Article transfer mechanism |
| NL6706657A (en) * | 1967-05-12 | 1968-11-13 | ||
| US3620381A (en) * | 1970-04-06 | 1971-11-16 | Stuart H Mccaughey | Horizontal high-speed transfer |
| DE2206407C3 (en) * | 1972-02-11 | 1979-11-15 | Gesellschaft Fuer Pressen-Automation Mbh, 7500 Karlsruhe | Feed device in presses |
| IT975795B (en) * | 1972-11-21 | 1974-08-10 | Colubra Lamsat Spa | CONTROL DEVICE FOR A SPORTER OF PIECES OF A PROCESSING LINE |
| DE2349126C2 (en) * | 1973-09-29 | 1982-07-29 | Günter 7500 Karlsruhe Zierpka | Feed device for step-by-step material and / or workpiece transport |
-
1977
- 1977-10-07 CA CA288,381A patent/CA1064849A/en not_active Expired
- 1977-10-18 AU AU29817/77A patent/AU510543B2/en not_active Expired
- 1977-11-07 IT IT5172077A patent/IT1090924B/en active
- 1977-11-21 FR FR7734953A patent/FR2375117B1/fr not_active Expired
- 1977-11-25 GB GB4925077A patent/GB1584576A/en not_active Expired
- 1977-12-16 DE DE19772756096 patent/DE2756096C2/en not_active Expired
- 1977-12-16 DE DE19777738370 patent/DE7738370U1/en not_active Expired
- 1977-12-20 JP JP15350677A patent/JPS53104481A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE2756096A1 (en) | 1978-06-29 |
| JPS53104481A (en) | 1978-09-11 |
| DE2756096C2 (en) | 1983-05-26 |
| AU2981777A (en) | 1979-04-26 |
| FR2375117A1 (en) | 1978-07-21 |
| AU510543B2 (en) | 1980-07-03 |
| GB1584576A (en) | 1981-02-11 |
| DE7738370U1 (en) | 1978-03-30 |
| FR2375117B1 (en) | 1984-12-14 |
| IT1090924B (en) | 1985-06-26 |
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