US3854576A - Eccentric wheel accumulators - Google Patents

Eccentric wheel accumulators Download PDF

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Publication number
US3854576A
US3854576A US00373928A US37392873A US3854576A US 3854576 A US3854576 A US 3854576A US 00373928 A US00373928 A US 00373928A US 37392873 A US37392873 A US 37392873A US 3854576 A US3854576 A US 3854576A
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United States
Prior art keywords
roller
rollers
radius
roller means
means according
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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
Application number
US00373928A
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English (en)
Inventor
Clyde L Bowman
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.)
Rapistan Inc
Original Assignee
Rapistan Inc
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Rapistan Inc filed Critical Rapistan Inc
Priority to US00373928A priority Critical patent/US3854576A/en
Priority to CA200,432A priority patent/CA1004175A/en
Priority to DE2426073A priority patent/DE2426073C3/de
Priority to IT23377/74A priority patent/IT1012975B/it
Priority to HURA618A priority patent/HU170738B/hu
Priority to FR7419762A priority patent/FR2235069B1/fr
Priority to BE145386A priority patent/BE816290A/xx
Priority to NLAANVRAGE7408251,A priority patent/NL173622C/xx
Priority to JP7244174A priority patent/JPS538437B2/ja
Priority to ES427678A priority patent/ES427678A1/es
Priority to SU7402045183A priority patent/SU575017A3/ru
Priority to BR5302/74A priority patent/BR7405302D0/pt
Priority to GB2866274A priority patent/GB1429453A/en
Application granted granted Critical
Publication of US3854576A publication Critical patent/US3854576A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • B65G47/00—Article or material-handling devices associated with conveyors; Methods employing such devices
    • B65G47/22—Devices influencing the relative position or the attitude of articles during transit by conveyors
    • B65G47/26—Devices influencing the relative position or the attitude of articles during transit by conveyors arranging the articles, e.g. varying spacing between individual articles
    • B65G47/261—Accumulating articles
    • B65G47/268—Accumulating articles by means of belt or chain conveyor
    • 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
    • B65G47/00—Article or material-handling devices associated with conveyors; Methods employing such devices
    • B65G47/22—Devices influencing the relative position or the attitude of articles during transit by conveyors
    • B65G47/26—Devices influencing the relative position or the attitude of articles during transit by conveyors arranging the articles, e.g. varying spacing between individual articles
    • B65G47/261—Accumulating articles
    • 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
    • B65G2203/00—Indexing code relating to control or detection of the articles or the load carriers during conveying
    • B65G2203/04—Detection means
    • B65G2203/042—Sensors

Definitions

  • This invention relates to powered conveyors of the wheel, roller and, belt variety wherein a propelling member is raised or lowered into a drive or dwell position. More particularly, this invention relates to a novel eccentric cam roller means utilized to raise and lower the propelling member.
  • a principal drawback to known types of eccentric cams of the prior art is that the eccentric rollers produce a constant vertical reciprocation of the propelling member resulting in rapid, alternate drive and release of each drive roller or the articles to lower the propelling member.
  • the driving force is delivered to the articles in pulses.
  • the pulsing is especially critical when the propelling member makes direct contact with the articles.
  • the pulsing is directly translated to the articles or cartons being conveyed.
  • advanced deterioation or breakage of the packages or articles therein can occur as a result of this vibratory or pulse form of propulsion.
  • a novel cam roller means for supporting a continuous propelling member in both raised (drive) and lowered (accumulation) positions.
  • the cam roller of this invention includes a pair of coaxially adjacent rollers, each eccentric in cross section and having restricted rotatability relative each other.
  • the portions of least radius of both rollers are held stationary in phase with each other and in the drive phase or position the portions of least radius rotate out of phase with each other.
  • the rollers in the drive position or phase rotate together and jointly form a circular roller supporting the propelling member at a constant height.
  • the portions of least radius are in phase and upwardly facing so that the propelling member is lowered.
  • a keeper is movable into engagement with a stop on each cam roller'means to hold the roller means in the dwell position. Subsequent release permits the rollers, under the influ ence of the propelling member, to shift into drive position, out of phase.
  • the preferred propelling member is a belt, the upper surface of which can be utilized to drive appropriate rollers or wheels on which the articles or cartons are supported or in the alternative, the articles can be engaged directly on the belt.
  • a significant advantage of the present invention is a roller which is circular in drive phase and lifts the belt into a constant drive position. Supporting the propelling member at a constant height eliminates fluctuation of propelling member height; eliminates pulsation in conveyor operation and significantly reduces associated noise levels. While the cam roller means is primar ily utilized for accumulation conveyors, its use is envisioned in other types of environments.
  • FIG. 1 is a front elevation view of the split-cam roller of the invention illustrated in the dwell or accumulation phase;
  • FIG. 2 is a side elevation view taken in cross section along the plane 22 in FIG. 1;
  • FIG. 3 is a cross-sectional view of the split-cam roller taken along the plane 33 in FIG. 1;
  • FIG. 4 is a front elevation view of the splitcam roller of the invention illustrated in the raised or drive positron; 7
  • FIG. 5 is a side elevation view taken in cross section along plane 5-5 of FIG. 4;
  • FIG. 6 is a cross section view taken along plane 6-6 of FIG. 4;
  • FIG. 7 is a fragmentary schematic plan view of a roller conveyor incorporating this invention.
  • FIG. 8 is a fragmentary elevation view in cross section taken along the plane VIII--VIII of FIG. 7;
  • FIG. 9 is a fragmentary sectional view taken along the plane IX--IX of FIG. 8;
  • FIG. 10 is a perspective view of an alternative conveyor arrangement incorporating this invention.
  • FIG. 11 is a fragmentary elevation view in cross section illustrating the invention in the conveyor of FIG. 10.
  • FIG. 12 is a sectional view taken along plane XII- XII of FIG. 11.
  • each split-cam roller 10 is comprised of an inner roller 12 and a pair of outer rollers 14 and 16 rotatably mounted on a conveyor axle 18.
  • the inner roller has a pair of spaced roller units 12a and 12b joined together by a tubular hub 120.
  • the rollers are metal and each roller includes a roller bearing assembly (not shown).
  • rollers are eccentric as will be described hereinafter and outer rollers 14 and 16 are rotatable relative to and jointly with roller 12 between a first position defined as the dwell or accumulating phase illustrated in FIGS. 1-3 and a raised drive position illustrated in FIGS. 4-6.
  • the flattened portions or portions of least radius 44, 46a and 4612 are held stationary in phase or alignment so that a propelling member such as a belt 50 drawn over the rollers (FIGS. 1-3 is in a lowered position out of engagement with the article or article supporting rollers.
  • a propelling member such as a belt 50 drawn over the rollers
  • the portions of least radius 44 of the outer rollers are rotated and held approximately 180 out of phase with the portions of least radius 46a, 46b of roller 12 so that the belt or propelling member 50 is raised a constant vertical distance causing article movement.
  • the rollers 12, 14 and 16 in this position rotate jointly as a circular roller.
  • each outer roller 14 includes a circumferential rim or flange 20 and web 22, the latter interconnecting flange 20 to the pulley hub 24.
  • the roller is also strengthened and braced by a plurality of ribs 26 integrally connected with the flange, web and hub.
  • Roller 16 is identical to roller 14 and is similarly constructed,'the details not being illustrated.
  • Roller unit 12a of split roller 12 likewise has a circumferential flange or rim portion 26a (FIGS. 1, 3 and 6) interconnected to a hub 28a by web 30a. Radially extending ribs 32a strengthen and support the integral elements of roller unit 12a. Roller unit 12b is identical to 12a and thus not described in detail. The suffix b is utilized to illustrate corresponding elements as shown in the drawings.
  • Outer rollers 14 and 16 are rotatable relative to each other and inner roller 12. Their relative rotation, however, is restricted through a revolution slightly less than 180.
  • a stop pin 36 is anchored longitudinally through inner roller 12 parallel to the axis of axle 18 and spaced radially approximately midway between hub 12c and outer raceways 26a and 26b. The significance of the spacing will be described subsequently hereinafter.
  • the length of stop pin 36 exceeds the longitudinal thickness of roller 12 such that one end 38 extends through web portion 22 of roller 14 while the other end 40 extends through the web portion of roller 16.
  • the means permitting extension through the appropriate web portions of rollers 14 and 16 is provided by a lost motion catch in the form of a circumferential slot 42 (FIGS. 2 and Slot 42 extends approximately 180 thus preventing rotation of outer rollers 14 and 16 relative each other and inner roller 12 by the same degree of revolution.
  • rollers 12, 14 and 16 are circular except that each is eccentric having a flattened portion of least radius. Rollers 14 and 16 have a portion of least radius 44 while roller units 12a, 12b have portions of least radius 46a, 46b. Rollers 14 and 16 are identical to each other such that when stop pin 36 is in abutment with either respective end of slot 42 of each roller, they are in complete alignment and their portions of least radius (FIGS. l-3) which is generally in the form of a belt continuously moved across the flange or rim surfaces of each roller, more specifically, flanged surfaces of rollers 14 and 16 and flanged surfaces 26a, 26b of roller units 12a, 12b.
  • the belt 50 preferably includes a depending central portion 52 which fits loosely within the circumferential slot or groove 54 formed by spaced roller units 12a, 12b and hub 120 as illustrated in FIG. 1.
  • each split-cam roller 10 is positioned in either a raised-drive position or lowered-accumulating (dwell) position which positions are illustrated in FIGS. l-6.
  • split-cam roller 10 is illustrated in what would be referred to as the accumulating position wherein if the propelling member 50 were being pulled across the upper surface from left to right in FIG. 2 (See arrow C), rotation of the rollers would be urged in the clockwise direction. If a physical stop (such as 114) were positioned in front of stop pin 36 in the position illustrated in FIGS.
  • roller 12 further rotation of roller 12 would be prevented and, depending on the relative position of rollers 14 and 16, they would cease rotating within approximately one-half a revolution when stop pin 36 reached one end of slots 42.
  • the portions of least radius 44 and 46a, 46b are all positioned upwardly in phase so that the propelling belt 50 being pulled there across is in effect lowered.
  • the rollers in the dwell position are brought into a stationary state and will remain so until the stop is removed from interference with stop pin 36.
  • FIGS. 4-6 The alternative position of operation of split-cam roller 10 is illustrated in FIGS. 4-6.
  • the physical stop (not shown) is removed from interference with stop pin 36, the particular propelling member being moved across the portions of least radius of the rollers will cause immediate rotation of the inner split roller 12.
  • the reason for this is the greater magnitude of the portions of least radius 46a, 46b relative to portions 44 of the outer rollers as illustrated in FIGS. 1 and 2.
  • the belt such as belt 50 will actually become disengaged from the portions of least radius 44 so that when the physical stop is removed, inner roller 12 will begin rotating immediately.
  • Inner roller 12 in fact will rotate through the complete circumferential length of slot 42 since as it begins to rotate, its radius increases as the portion of least radius rotates out of contact with the propelling member.
  • pin 36 Upon reaching the opposite limit of slot 42 however, pin 36 will engage the end of each slot in rollers 14 and 16 causing them to rotate jointly with roller 12 approximately out of phase. In this out of phase position, the portions of least radius 44 and 46a, 46b are out of phase with each other thereby combining to form an effective roller having a circular cross section (FIGS. 5 and 6) when the outer rollers and inner roller are out of phase with each other.
  • This out of phase operation will lift the propelling member moving across the outer surfaces of the rollers and rollers 12 and 14, 16, in combination, will provide a belt supporting roller of uniform radius, the belt being positioned for propelling articles along the conveyor causing a drive function as will be described shortly hereinafter.
  • outer rollers 14 and 16 8 preferably include a counterweight 60 which urges the portion of least radius 44 into an upper orientation when the roller is not under the influence of an outside force, such as engagement with belt 50.
  • an outside force such as engagement with belt 50.
  • the frictional effect of the propelling member pulled across the outer surface of each roller will overcome the counterweight bias.
  • the bias weight will tend to rotate the outer rollers slightly towards the upstream transition portion 52 (FIG. 2) of each outer roller which will come into contact with the propelling member 50 so that constant reciprocating pulses are not being effected. This greatly reduces the clatter around the conveyor unit itself.
  • counterweights 60 will bias roller 14 and 16 out of engagement with belt 50 until pin 36 drives it around.
  • inner roller 12 and its roller units 12a, 12b likewise include a counterweight 64 positioned so that the portion of least radius 46a and 46b is rotated away from the upper dwell position in a direction opposite the urgency of rotation of outer rollers 14 and 16. This will ensure contact between the flanged surface 46a, 46b of inner roller 12 at all times with the propelling member being moved there across. This is of significance during startup also since it could be that the belt might under certain circumstances be spaced from the portions of least radius of each roller when the belt is stopped. However, the urgency of counterweight 64 will ensure that the inner roller 12 will always engage the propelling member so that during startup, positive engagement exists between the actuating portion (inner roller 12) of each split-cam roller.
  • weights 64 urge roller 12 out of phase with rollers 14 and 16 in the same fashion as described above in regard to rollers 14 and 16.
  • the numeral 100 indicates a roller conveyor having conventional side frame members 102 and 104 between which extend a plurality of driven or propelling rollers 106.
  • the rollers 106 are arranged in spaced relationship along the conveyor and in a common plane to form a conveying surface. Beneath the rollers 106 is a driven propelling member 50a moved by any suitable power means in the direction of the arrow A of FIG. 8, thus rotating the rollers 106 to move articles in the direction of the arrow B.
  • the side frame members 102 and 104 are connected by rigid cross braces 108.
  • the upper run of propelling member 50 is supported on the split-cam rollers 10. These rollers are placed at equal intervals along the length of the conveyor, only one of which is shown in phantom in FIG. 7. Where the propelling member is a belt having a depending central tracking ridge 52a (FIG. 9), these rollers are of sufficient width to support a substantial lateral portion of the propelling member and are equipped with a central circumferential channel 54 formed by the spaced inner roller units 12a, 12b as described previously.
  • stop pin 36 is anchored within inner rollers 12a, 12b and rotates therewith within channel 54.
  • a stop means or looking slide 112 (FIG. 8) is slidably seated beneath split-cam rollers and includes upstanding stop portions 114 which are positioned in alignment with and for cooperative association with channel 54 and stop pin 36.
  • a plurality of slides 112, 112a, etc., are arranged longitudinally endto-end the length of the conveyor.
  • Each locking slide 112 is common to several of the cam rollers 10, the number being determined by the size of the articles to be conveyed. Thus, it might in clude three, four or even fifteen or twenty of the cam rollers 10. In the particular construction illustrated, each slide cooperates with four of the cam rollers 10 defined in zones I, II and III (FIG. 8). The length of the slide will be determined by the length of the zone which is determined to be suitable for change in belt attitude for each article as it passes along the conveyor.
  • Each locking slide 112 has an upstanding stop, 114 for each of the cam rollers 10. These stops cooperate with stop pins 36 so that when the locking slide is in a active or interfering position (FIG. 9), the stops are so located as to interfere with stop pin 36 to prevent free rotation of the particular associated split-cam roller 10. When the slide is shifted longitudinally (slides 112 and 112b, FIG. 8) out of interference, the associated stops are removed from interference with the associated stop pins 36 and the associated split-cam rollers 10 are free to rotate.
  • Each locking slide 112 is secured to a pair of rocker arms 116 (FIG. 8) extending downwardly from each side of a sensing roller 118.
  • a rod 120 interconnects the lower ends of each rocker arm 116, slide 112 being anchored to the center portion of each rod 120 (FIG. 8).
  • the rocker arms are pivotal about a shaft 122 while the lower ends of the arms are attached to springs 124 which bias the sensing roller 118 upwardly and the associated locking slide 112 forwardly so that stops 114 are in a non-engaging position.
  • sensing rollers 118 in normal position, are raised slightly above the plane of the conveying surface of the conveyor. Thus, as an article D passes over them, they are depressed as indicated by the roller 1 18. This pivots the assembly to shift stop slide 112a rearwardly for interference with stop pins 36 of the four split-cam rollers 10 associated with the particular stop slide. Articles supported by the associated conveyor rollers 106 will thus stop since belt a is lowered out of. engagement therewith.
  • the sensor of one zone actuates the slide of the adjacent upstream zone.
  • sensor 118 in zone I actuates slide 112a in zone II, the operation of which is well-known to one skilled in the art.
  • FIG. 9 clearly illustrates one of the stops 114 in interference with stop pin 36 causing the split-cam roller 10 to be held in a stationary position as illustrated and described in detail with regard to FIGS. 13. In this position, belt 50a is lowered out of engagement with the roller 106 immediately thereabove causing the articles under the influence of the particular group of rollers 106 being stopped to come to rest.
  • FIGS. 10-12 illustrate an alternative conveyor embodiment in which the application of this invention is directed to a conveyor 130 in which the belt or propelling member 50b is mounted substantially at the conveyor surface.
  • Belt 50b makes direct physical contact with the articles E, rather than contacting driving rollers which, in turn, transport the articles as illustrated in FIGS. 7-9.
  • the belt 50b thus moves in the direction of arrow F in this embodiment which is opposite that of belt 500 in the embodiment of FIGS. 79.
  • the construction of this conveyor is quite similar to that of the conveyor illustrated in FIGS.
  • rollers 106 extending the entire width of the conveyor track, two outer tracks of rollers of diminished length, namely rollers 106a and 1061; are provided, each group of rollers 106a and 1061; being arranged in spaced relationship along the conveyor and in a common plane to form a conveying surface.
  • the sets of rollers 106a and 10Gb are spaced transversely forming a medial lane 131 in which the continuously driven belts 50b is positioned.
  • belt 501) in cooperation with split-cam rollers 10 of the invention is positionable between a raised article contacting and propelling position as illustrated in the left fragmentized portion of FIG. 11 when the split-cam rollers 10b are rotating to raise propelling member 50b and a lowered position out of contact with the articles supported on the conveyor rollers 106a and 10Gb when a stop mechanism has been inserted in front of the associated stop pins 36 of each split-cam roller 10b so that the portions of least radius of rollers 12a, 12b 14 and 16 are up so that propelling member 50b is lowered.
  • the operation of cam rollers 10b is identical to that of rollers 10 described previously except that the position of slot 42 and pin 36 is reversed since the direction of rotation is reversed.
  • the cam roller 10 is arranged for counterclockwise rotation while roller 10b is arranged for clockwise rotation.
  • a stop slide 132 is mounted beneath rollers 10 having a plurality of raised stops 134 movable longitudinally in similar fashion to stop slides 112, 112a, 112b, etc., described in the embodiment in FIGS. 79.
  • Stop slides 132 are connected to one or more rocker arms 136 which are pivotal about their lower ends 138 about shaft 140 (FIG. 11).
  • the rocker arm is attached at its upper end to sensor roller 142 and intermediate each end to slide 133 by a pin 14.
  • a cam roller means for supporting a propelling member in both a raised and lowered position comprising first and second eccentric rollers mounted coaxially, and rotatable relative to each other between a lowered position wherein the portions of least radius of said rollers are in phase with each other and supporting said propelling member in its lowered position and a raised position wherein the portions of least radius of said rollers are out of phase with each other forming a circular roller means supporting said propelling memher in its raised position.
  • roller means according to claim 1 wherein said rollers are stationary in said lowered position and rotating jointly in said raised position.
  • roller means further includes a stop actuated by a keeper movable into and out of engagement with said stop to select the positioning of said rollers in one of said raised or lowered positions.
  • roller means according to claim 3 wherein said propelling member is a continuously driven belt engaged with at least one of said rollers urging said rollers to move between said raised and lowered positions.
  • roller means according to claim 4 wherein said first roller has an annular slot, said belt has 21 depending ridge movable in said slot for guiding said belt over said first roller.
  • roller means according to claim 6 wherein said keeper has a finger moveable radially relative to said first roller, said finger being movable into said slot for interference with said pin to stop in sequence said first and second rollers.
  • roller means according to claim 3 wherein a plurality of roller means are positioned beneath said propelling means, said propelling means causing article movement along a conveyor, said keeper being movable into stopping interference with a discrete number of adjacent roller means to cause article accumulation at selected locations along said conveyor.
  • roller means according to claim 9 wherein said keeper is actuated by a sensor responsive to article movement along said conveyor.
  • An eccentric split-cam roller means for supporting a propelling member in both raised and lowered positions comprising: a pair of coaxially adjacent rollers eccentric in cross section and rotatable relative each other into a first position wherein the portions of least radius are in phase with each other and a second position wherein the portions of least radius are out of phase with each other; and a stop on said cam means for selective engagement with a keeper movable into and out of engagement with said stop, said stop when engaged with said keeper preventing further rotation of said rollers causing said rollers to dwell in said first position with said portions of least radius engaging said propelling member thereby lowering said propelling member, said stop when not engaged with said keeper allowing said rollers to be rotated by said propelling member relative to each other into said second position, whereupon said rollers rotate jointly together forming a circular roller means lifting said propeller member.
  • one of said rollers includes a stop pin positioned laterally and extending beyond said one roller, the other of said rollers including a circumferential slot through which said pin extends, the length of said circumferential slot being less than 360 whereby said pin engages one or the other ends of said circumferential slot to lock said rollers into one of said two positions.
  • roller means according to claim 15 wherein the radial magnitude of the eccentric portion of said one roller is greater than the radial magnitude of the eccentric portion of the other of said rollers so that said propelling member is disengaged from the other of said rollers when said roller means is in said first position.
  • roller means according to claim 14 wherein one of said rollers include a bias weight which urges said one roller toward said first position and the other of said rollers includes a bias weight which urges said one roller toward said second position when said roller means are free of influence from said propelling member.
  • roller means according to claim 14 wherein a plurality of roller means are positioned beneath said propelling means, said propelling means causing article movement along a conveyor, said keeper being movable into stopping interference with a discrete number of adjacent roller means to cause article accumulation at selected locations along said conveyor.
  • roller means according to claim 20 wherein said keeper is actuated by a sensor to article movement along said conveyor.
  • Means for supporting and controlling the position of a conveyor propelling member said means having a first eccentric roller provided with a flattened portion of least radius, said means characterized by a second eccentric roller provided with a flattened portion of least radius, an element coaxially mounting said first and second rollers for rotation independently of each other, said rollers, with their flattened portions are in phase forming an eccentric support for said propelling member holding it constantly in one position and when said portions are out of phase forming circular support for said propelling member holding it constantly in a second position spaced from said first position.
  • roller means according to claim 1 wherein a third roller is coaxially mounted with said first and second rollers, said third roller corresponding dimensionally to said second roller and rotating jointly therewith, said first roller being positioned intermediate said second and third rollers.
  • belts should be, belt ;

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rollers For Roller Conveyors For Transfer (AREA)
  • Attitude Control For Articles On Conveyors (AREA)
  • Silver Salt Photography Or Processing Solution Therefor (AREA)
  • Structure Of Belt Conveyors (AREA)
US00373928A 1973-06-27 1973-06-27 Eccentric wheel accumulators Expired - Lifetime US3854576A (en)

Priority Applications (13)

Application Number Priority Date Filing Date Title
US00373928A US3854576A (en) 1973-06-27 1973-06-27 Eccentric wheel accumulators
CA200,432A CA1004175A (en) 1973-06-27 1974-05-21 Eccentric wheel accumulators
DE2426073A DE2426073C3 (de) 1973-06-27 1974-05-30 Kurvenrollenvorrichtung für einen Sammelförderer
IT23377/74A IT1012975B (it) 1973-06-27 1974-05-30 Perfezionamenti nei dispositivi di accumulazione a ruote eccen triche
HURA618A HU170738B (de) 1973-06-27 1974-06-04
FR7419762A FR2235069B1 (de) 1973-06-27 1974-06-07
BE145386A BE816290A (fr) 1973-06-27 1974-06-13 Transporteur d'accumulation a rouleaux excentriques
NLAANVRAGE7408251,A NL173622C (nl) 1973-06-27 1974-06-20 Verzameltransporteur.
JP7244174A JPS538437B2 (de) 1973-06-27 1974-06-26
ES427678A ES427678A1 (es) 1973-06-27 1974-06-26 Perfeccionamientos introducidos en medios de leva para so- portar un miembro propulsor tanto en posicion elevada como en posicion bajada.
SU7402045183A SU575017A3 (ru) 1973-06-27 1974-06-27 Эксцентриковый ролик кулачкового механизма дл пуска и останова накопительного конвейера
BR5302/74A BR7405302D0 (pt) 1973-06-27 1974-06-27 Um mecanismo de rolos excentricos aperfeicoado
GB2866274A GB1429453A (en) 1973-06-27 1974-06-27 Roller means and conveyors incorporating such roller means

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US00373928A US3854576A (en) 1973-06-27 1973-06-27 Eccentric wheel accumulators

Publications (1)

Publication Number Publication Date
US3854576A true US3854576A (en) 1974-12-17

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Application Number Title Priority Date Filing Date
US00373928A Expired - Lifetime US3854576A (en) 1973-06-27 1973-06-27 Eccentric wheel accumulators

Country Status (13)

Country Link
US (1) US3854576A (de)
JP (1) JPS538437B2 (de)
BE (1) BE816290A (de)
BR (1) BR7405302D0 (de)
CA (1) CA1004175A (de)
DE (1) DE2426073C3 (de)
ES (1) ES427678A1 (de)
FR (1) FR2235069B1 (de)
GB (1) GB1429453A (de)
HU (1) HU170738B (de)
IT (1) IT1012975B (de)
NL (1) NL173622C (de)
SU (1) SU575017A3 (de)

Cited By (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0040949A1 (de) * 1980-05-19 1981-12-02 Lear Siegler, Inc. Sammelförderer
EP0109732A1 (de) * 1982-09-17 1984-05-30 Lear Siegler, Inc. Fühleinrichtung zur Betriebssteuerung eines Stauförderers
US4502593A (en) * 1981-08-26 1985-03-05 Lear Siegler, Inc. Conveyor facility
US4878578A (en) * 1988-06-10 1989-11-07 Rapistan Corp. Split-cam conveyor rollers
US5125497A (en) * 1989-12-28 1992-06-30 Bleichert Forderanlagen Gmbh Lifting system for lifting goods over a limited distance while maintaining an aligned orientation of the goods with respect to a reference
US5540323A (en) * 1993-10-04 1996-07-30 Rapistan Demag Corporation Modular pneumatic accumulation conveyor
US6065588A (en) * 1998-07-02 2000-05-23 Mannesmann Dematic Rapistan Corp. Contact assembly for accumulation conveyors
US6478142B2 (en) 1998-12-09 2002-11-12 Rapistan Systems Advertising Corp. Contact assembly for accumulation conveyors
US20030192774A1 (en) * 2002-04-12 2003-10-16 Cotter David H. Tape drive conveyor
US6763930B2 (en) 2002-03-14 2004-07-20 Rapistan Systems Advertising Corp. Accumulation conveyor assembly
US20090065330A1 (en) * 2007-09-07 2009-03-12 Dematic Corp. Conveyor systems
ES2605426A1 (es) * 2016-09-09 2017-03-14 Mecalux, S.A. Sistema transportador de cargas, estructura modular y una instalación de transporte de cargas
US10214357B2 (en) * 2017-06-13 2019-02-26 Goodrich Corporation Lift roller for power drive unit
CN109516117A (zh) * 2018-11-07 2019-03-26 宋海燕 一种进出口使用的传输带机构
CN110203627A (zh) * 2019-07-20 2019-09-06 湖南信芯电子技术有限公司 吸塑盘排版***
US11130639B2 (en) * 2019-12-20 2021-09-28 Abb Schweiz Ag Modular pulley for continuous belt conveyor system
US11319156B2 (en) * 2019-01-20 2022-05-03 Suzhou Suxiang Robot Intelligent Equipment Co., Ltd Sorting module and conveyer appartus composed thereof
US20220281692A1 (en) * 2021-03-04 2022-09-08 Crown Plastics Co. Roller Assembly For Singulator

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EP0002106A1 (de) * 1977-10-14 1979-05-30 Hydraroll Limited Einrichtung zum Handhaben von Lasten mit anhebbaren Rollen und damit versehener Speicherboden
EP0005920B1 (de) * 1978-05-31 1982-06-30 J.H. Fenner & Co. Limited Antriebseinrichtung für Rollenbahnen
JPS5823982Y2 (ja) * 1978-06-24 1983-05-23 澤藤電機株式会社 エンジン始動装置
FR2462365A1 (fr) * 1979-07-30 1981-02-13 Mecanique Gle Decolletage Tour Transporteur accumulateur
GB2195112B (en) * 1986-09-23 1990-05-23 Ian David Marshall Powered roller conveyor

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Cited By (24)

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US4361224A (en) * 1980-05-19 1982-11-30 Lear Siegler, Inc. Roller motion sensing accumulator
EP0040949A1 (de) * 1980-05-19 1981-12-02 Lear Siegler, Inc. Sammelförderer
US4502593A (en) * 1981-08-26 1985-03-05 Lear Siegler, Inc. Conveyor facility
EP0109732A1 (de) * 1982-09-17 1984-05-30 Lear Siegler, Inc. Fühleinrichtung zur Betriebssteuerung eines Stauförderers
US4473148A (en) * 1982-09-17 1984-09-25 Lear Siegler, Inc. Motion sensor for motion sensing accumulator
US4878578A (en) * 1988-06-10 1989-11-07 Rapistan Corp. Split-cam conveyor rollers
US5125497A (en) * 1989-12-28 1992-06-30 Bleichert Forderanlagen Gmbh Lifting system for lifting goods over a limited distance while maintaining an aligned orientation of the goods with respect to a reference
US5540323A (en) * 1993-10-04 1996-07-30 Rapistan Demag Corporation Modular pneumatic accumulation conveyor
US6065588A (en) * 1998-07-02 2000-05-23 Mannesmann Dematic Rapistan Corp. Contact assembly for accumulation conveyors
US6478142B2 (en) 1998-12-09 2002-11-12 Rapistan Systems Advertising Corp. Contact assembly for accumulation conveyors
US6763930B2 (en) 2002-03-14 2004-07-20 Rapistan Systems Advertising Corp. Accumulation conveyor assembly
US6899219B2 (en) 2002-04-12 2005-05-31 Rapistan Systems Advertising Corp. Tape drive conveyor
US20030192774A1 (en) * 2002-04-12 2003-10-16 Cotter David H. Tape drive conveyor
US20090065330A1 (en) * 2007-09-07 2009-03-12 Dematic Corp. Conveyor systems
US7909155B2 (en) 2007-09-07 2011-03-22 Dematic Corp. Conveyor systems
ES2605426A1 (es) * 2016-09-09 2017-03-14 Mecalux, S.A. Sistema transportador de cargas, estructura modular y una instalación de transporte de cargas
US10214357B2 (en) * 2017-06-13 2019-02-26 Goodrich Corporation Lift roller for power drive unit
CN109516117A (zh) * 2018-11-07 2019-03-26 宋海燕 一种进出口使用的传输带机构
CN109516117B (zh) * 2018-11-07 2020-08-14 杭州银湖机械弹簧有限公司 一种进出口使用的传输带机构
US11319156B2 (en) * 2019-01-20 2022-05-03 Suzhou Suxiang Robot Intelligent Equipment Co., Ltd Sorting module and conveyer appartus composed thereof
CN110203627A (zh) * 2019-07-20 2019-09-06 湖南信芯电子技术有限公司 吸塑盘排版***
US11130639B2 (en) * 2019-12-20 2021-09-28 Abb Schweiz Ag Modular pulley for continuous belt conveyor system
US20220281692A1 (en) * 2021-03-04 2022-09-08 Crown Plastics Co. Roller Assembly For Singulator
US11780682B2 (en) * 2021-03-04 2023-10-10 Crown Plastics Co. Roller assembly for singulator

Also Published As

Publication number Publication date
DE2426073B2 (de) 1980-01-03
BR7405302D0 (pt) 1975-09-30
HU170738B (de) 1977-08-28
NL7408251A (de) 1974-12-31
DE2426073A1 (de) 1975-01-16
NL173622C (nl) 1984-02-16
DE2426073C3 (de) 1980-09-04
BE816290A (fr) 1974-09-30
FR2235069B1 (de) 1978-01-13
JPS538437B2 (de) 1978-03-28
SU575017A3 (ru) 1977-09-30
CA1004175A (en) 1977-01-25
IT1012975B (it) 1977-03-10
FR2235069A1 (de) 1975-01-24
GB1429453A (en) 1976-03-24
ES427678A1 (es) 1976-09-01
JPS5037169A (de) 1975-04-07

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