US3511350A - Braking roller - Google Patents

Braking roller Download PDF

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Publication number
US3511350A
US3511350A US764464A US3511350DA US3511350A US 3511350 A US3511350 A US 3511350A US 764464 A US764464 A US 764464A US 3511350D A US3511350D A US 3511350DA US 3511350 A US3511350 A US 3511350A
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Prior art keywords
braking
piston
roller
shell
shaft
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Expired - Lifetime
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US764464A
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English (en)
Inventor
Hans Vom Stein
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HANS VOM STEIN oHG
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HANS VOM STEIN oHG
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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
    • B65G13/00—Roller-ways
    • B65G13/075—Braking means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D57/00—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders
    • F16D57/06—Liquid-resistance brakes; Brakes using the internal friction of fluids or fluid-like media, e.g. powders comprising a pump circulating fluid, braking being effected by throttling of the circulation

Definitions

  • a braking roller for use in roller conveyor systems comprises a shaft which is fixedly mounted in the frame of the conveyor system, a liquid-filled housing having a cylindrical shell and two end walls which are rotatable on the shaft so that the shell can rotate in response to frictional engagement with an article which is caused to travel along the rollers of the conveyor system, a piston installed in the housing against rotation with reference to the shaft and dividing the interior of the housing into a pair of chambers which can communicate by way of one or more passages in the piston, cams provided on the piston and on the end walls of the housing to cause reciprocatory axial movements of the piston in response to rotation of the shell, and one or more automatic regulating valves provided in the passage or passages of the piston to offer to the flow of
  • the present invention relates to roller conveyors in general, and more particularly to improvements in braking rollers which are utilized in such conveyors to regulate the speed of goods.
  • braking rollers which serve to regulate the speed of goods.
  • Such braking rollers are installed at one or more points of the roller conveyor and may but need not be equidistant from each other. Their purpose is to insure that the speed of conveyed goods remains below a predetermined limit, for example, in order to prevent the goods from piling up on the roller conveyor and to thus insure that each article reaches the end of the conveyor ahead of and spaced from the next-following article.
  • Another purpose of braking rollers is to prevent the articles from being propelled with excessive force against stops which are normally provided at the discharge end of a roller conveyor.
  • a crate or a box could be deformed, damaged or destroyed in response to excessive impact against a fixed stop or against the preceding crate or box at the discharge end of the roller conveyor.
  • the braking rollers are usually installed in such a way that their peripheral surfaces extend into the path of and can be frictionally engaged by the undersides of conveyed articles.
  • Certain types of presently known braking rollers for use in roller conveyors are provided with braking devices which are operated in automatic response to rotation of the cylindrical shell of a braking roller, such rotation being caused by the article which travels along the conveyor and engages the external surface of the shell.
  • the braking device comprises a housing which is fixedly secured to the shaft of the braking roller.
  • the shaft is fixedly mounted in the frame of the roller conveyor and the housing is installed in the interior of the rotary shell.
  • This housing is formed with two axially parallel bores each of which accommodates a reciprocable piston and each piston has an end portion which extends from the respective bore and constitutes a follower tracking a cam provided on the adjoining end wall of the shell.
  • a drawback of the just described braking roller is that its braking action can be regulated by a screw which is accessible only in response to complete dismantling of the braking roller. Moreover, the braking action of the roller is not dependent on the speed at which the shell rotates but solely on the position of the aforementioned screw. Therefore, such braking rollers are unsatisfactory for use in roller conveyors which are intended for transport of goods at different speeds or whereon the speed of goods changes during transport. Such conventional braking rollers produce an excessive braking action upon a slowly moving article and an insufiicient braking action upon an article which is conveyed at a high speed. The construction of such rollers is complicated and the adjustment of braking action consumes too much time so that the conveyor is idle for extended periods of time whenever it is to be converted from transport of slowly moving goods to transport of rapidly advancing goods, or vice versa.
  • One of the objects of my present invention is to provide a braking roller whose braking action varies automatically in response to changes in speed of conveyed articles.
  • Another object of the invention is to provide a braking roller whose braking action can change during engagement with an article.
  • a further object of the invention is to provide a simple, relatively inexpensive and rugged braking roller which can be readily installed in presently known roller conveyors without necessitating substantial alterations in the design of such apparatus.
  • An additional object of the invention is to provide a braking roller which can be used in roller conveyors for transport of bulky, compact, heavy, lightweight, short and/or long goods and which need not be adjusted when the conveyor is converted from transport of one type of goods to transport of another type of goods.
  • a concomitant object of the invention is to provide a novel rotary housing for a braking roller of the above outlined character.
  • An ancillary object of the invention is to provide a ibraking roller which consists of a small number of relatively simple parts, whose parts can be mass-produced in known machinery, and which requires a minimum of maintenance.
  • Still another object of the invention is to provide a braking roller which can discriminate between heavy and lightweight goods as well as between rapidly moving and slowly advancing goods, and which automatically produces a braking force which is proportional to the bulk, speed and/ or kinetic energy of the goods.
  • a further object of the invention is to provide a braking roller which can be used to regulate the speed of smooth-surfaced or rough-surfaced goods.
  • the improved braking roller is utilized in roller conveyors or the like and comprises a shaft, means provided in the roller conveyor for holding the shaft against rotation, a hollow housing including a cylindrical shell and two end walls rotatably mounted on the shaft so that the housing can rotate in response to engagement between the external surface of the shell and an article which is caused to travel along the roller conveyor, a liquidfilled compartment defined by the housing and the shaft, a piston axially movably mounted on the shaft and dividing the compartment into a pair of chambers, cooperating cams provided on the housing and on the piston to move the latter back and forth in response to rotation of the housing so that the speed of axial movement of the piston is a function of rotational speed of the housing, at least one passage provided in the piston and extending between the two chambers of the compartment, and regulating valve means provided in the passage to throttle the flow of liquid between the chambers at a rate which increases in response to increasing rotational speed of the housing whereby the piston tends to decelerate the housing with a force which is a function of the rotational speed
  • the piston may be provided with one or more passages and the valve means may comprise a separate valve for each passage or groups of valves for groups of passages.
  • the cams are preferably face cams which are provided on the end walls of the housing and on the axial ends of the piston and operate in such a way that one cam of the piston engages the cam of the adjoining end wall when the piston moves in one direction whereby the other cam of the piston is moved along the cam on the other end wall, and vice versa.
  • the lead of all of the cams is preferably the same, and the cams of the two end walls are preferably angularly offset by 1-80 degrees with reference to each other.
  • FIG. 1 is an axial sectional view of a braking roller which embodies one form of the invention, the section being taken in the direction of arrows as seen from the line II of FIG. 2;
  • FIG. 2 is a transverse vertical sectional view as seen in the direction of arrows from the line IIII of FIG. 1;
  • FIG. 3 is an enlarged elevational view of a regulating valve in the braking roller of FIGS. 1 and 2;
  • FIG. 4 is a partly elevational and partly axial sectional view of a second braking roller, the section being taken in the direction of arrows as seen from the line IV-IV of FIG. 5;
  • FIG. 5 is a transverse vertical sectional view as seen in the direction of arrows from the line VV of FIG. 4.
  • the braking roller of FIGS. 1 to 3 comprises a shaft having externally threaded end portions 12 by means of which the shaft can be fixedly installed in a frame 75 of a roller conveyor.
  • the frame 75 constitutes a means for holding the shaft 10 against rotation.
  • the median portion of the shaft 10 is surrounded by a sleeve 11 of synthetic plastic material which is fixedly secured thereto and is provided with two axially parallel external ribs or splines 38 located diametrically opposite each other (see FIG. 2).
  • the braking roller further comprises a housing including a cylindrical shell 18 whose ends are aflixed to two end walls or caps 16 of the housing by radially extending screws 20 or analogous fasteners.
  • the caps 16 can be soldered, glued, welded or otherwise permanently secured to the end portions of the shell 18.
  • the caps 16 are coaxial with the shaft 10 and each thereof ac- 4 commodates an antifriction bearing 24 whose inner race 28 is aflixed to the shaft 10 and whose outer race 26 is mounted in the respective cap.
  • the peripheral surface of each cap 16 is formed with a circumferential groove for a sealing ring 22 and each cap is further provided with an internal recess for an annular sealing element 32 which surrounds the adjoining portion of the shaft 10.
  • the caps 16 define with the shell 18 and with the sleeve 11 of the shaft 10 an annular compartment 19 which is sealed by the elements 22 and 32.
  • Disk-shaped nuts 30 mate with the end portions 12 of the shaft 10 and overlie the outersides of the respective bearings 24.
  • the inner axial ends of the caps 16 are provided with helical face cams 34, 36 which are angularly offset by 180degrees.
  • the lead of the cam 34 is the same as that of the cam 36.
  • the compartment 19 accommodates an annular pumping member or piston 39 which is reciprocable along the sleeve 11 and comprises an outer cylindrical portion 40 which is adjacent to the internal surface of the shell 18, an inner cylindrical portion which is fluted to receive the splines 38 of the sleeve 11, and two axially spaced annular webs or flanges 46, 48 which extend radially between the cylindrical portions 40, 50.
  • the splines 38 of the sleeve 11 hold the piston 39 against angular movement with reference to the shaft 10 but permit the piston to move axially between the caps 16.
  • the end portions of the outer cylindrical portion 40 are provided with face cams 42, 44 whose lead is identical with that of the cams 34, 36.
  • the piston 39 comprises two halves which abut against each other in the plane of the line II-II of FIG. 1 and are permanently or separably secured to each other.
  • the flanges 46, 48 are provided with pairs of openings or bores which are parallel to the axis of the shaft 10 and are located diametrically opposite each other. Each opening 60 of the flange 46 registers with an opening 60 of the flange 48. These openings accommodate the end portions of two guide pins 56 forming part of two automatic fluid flow regulating valves each mounted in one of two passages 52 of the piston 39. One of these regulating valves is shown in detail in FIG. 3.
  • the median portion of each guide pin 56 is provided with a collar 54 which separates two helical valve springs 58. Each of these springs bears against one of the flanges 46, 48 and against the collar 54 so as to urge the guide pin 56 to a neutral position shown in the upper part of FIG. 1.
  • Each collar 54 is integral with a crosshead or carrier 51 which is rigid or integral with two cylindrical valve members 62 located diametrically opposite each other with reference to the axis of the corresponding guide pin 56.
  • the end portions of the valve members 62 are of conical shape and taper away from the central portions of such valve members.
  • Each opening 60 of the flange 46 or 48 is flanked by two ports 66, 68 which form part of the respective passages 52 and register with the valve members 62.
  • the inner annular edges of surfaces which surround the ports 66, 68 can serve as seats for the adjoining conical end portions 70 of the respective valve members 62.
  • the end portions 12 of the shaft 10 are fixedly mounted in the frame of the roller conveyor so that the shaft is held against rotation.
  • the braking roller of FIGS. 1 to 3 is installed between two idler rollers of the roller conveyor, between an idler roller and a second braking roller, or between two additional braking rollers.
  • an article When an article is caused to travel along the roller conveyor, its bottom surface engages the external surface of the shell 18 and causes the latter to rotate about the shaft 10.
  • the external diameter of the shell 18 may exceed slightly the external diameters of adjoining idler rollers in the roller conveyor.
  • the braking roller can be mounted on springs so that the shaft 10 can move up and down and is biased upwardly in order to maintain the top portion of the shell 18 in the path of movement of the underside of an article which travels along the roller conveyor.
  • the external surface of the shell 18 may be roughened by grooving, milling or in another suitable way to insure more satisfactory frictional engagement with travelling articles.
  • the shell preferably comprises an external liner or coating of rubber or other suitable elastomeric material.
  • the rotational speed of the shell 18 with reference to the shaft depends on the speed of the article which engages its external surface.
  • one of these cams engages the adjoining cam 42 or 44 of the piston 39 and causes the latter to move axially along the sleeve 11 of the shaft 10.
  • the other cam of the piston 39 then engages the adjoining cam of the revolving housing and causes the piston to move axially in the opposite direction.
  • the cams 34, 36 of the caps 16 cooperate with the earns 42, 44 to move the piston 39 axially back and forth between the caps of the braking roller.
  • the piston 39 increases the volume of the right-hand chamber 19b of the compartment 19 at the expense of the left-hand chamber 19a of this compartment, or vice versa, depending on the direction in which the piston moves in the shell 18.
  • the compartment 19 is filled with oil or another suitable liquid and such liquid is caused to flow through the passages 52 in response to axial displacement of the piston 39.
  • the springs 58 of the two regulating valves normally maintain the conical end portions 70 of the valve members '62 away from engagement with the adjoining seats in the flanges 46, 48.
  • the piston 39 changes its axial position at a low speed so that the liquid can flow between the end portions 70 and the adjoining seats without effecting any appreciable axial displacement of valve members 62 with reference to the piston.
  • the braking roller then produces a minimal braking action or no braking action at all.
  • the braking action is less pronounced or practically nonexistent when the articles are caused to travel at a lesser speed. Furthermore, and if the article which rotates the shell 18 is rather long, the braking action of the shell upon such article decreases gradually as the article continues to move therealong. This will be readily understood since, when the article is decelerated in response to initial engagement with the shell 18, the valve members 62 offer lesser resistance to the flow of liquid through the respective passages 52 and the braking action of the shell 18 decreases. This is due to the provision of springs 58 which always tend to maintain the valve members 62 in neutral positions in which the end portions 70 of such valve members offer a minimal resistance to the flow of liquid through the respective passages 52.
  • the braking action of the improved roller depends negligibly on the weight and/or bulk of conveyed goods, i.e., such braking action is dependent mainly on the speed of goods, and the shell 18 is capable of satisfactorily 6 braking a large, small, short, long, heavy or lightweight article with equal efficiency.
  • the shaft 10 of the braking roller preferably consists of steel or other suitable metallic material. All or nearly all other component parts of the braking roller can be made of synthetic plastic material and can be massproduced in accordance with any of several well known manufacturing processes. The use of plastic materials brings about a reduction in the weight and cost of the braking roller. Moreover, the maintenance cost of the braking roller is negligible and its useful life is surprisingly long.
  • FIGS. 4 and 5 illustrate a modified braking roller.
  • the median portion of the shaft is of polygonal (preferably hexagonal) cross-sectional outline and the shaft has two externally threaded end portions 82 by means of which it can be mounted in the frame of a roller conveyor in the same Way as described in connection with FIGS. 1 to 3.
  • the polygonal median portion of the shaft 80 is provided with a plastic sleeve 102 which has six equidistant axially parallel ribs or splines best shown in FIG. 5 and extending into complementary flutes provided in the internal surface of a cylindrical portion 106 forming part of an axially reciprocable pumping member or piston 139'.
  • the plastic shell of the housing of the braking roller is integral with two end walls or caps 84 which can rotate on the outer races of two antifriction bearings 98 and have their central openings sealed by nuts 96 which mesh with the respective end portions 82 of the shaft 80.
  • the shell 90 comprises two cupped sections 90a, 90b whose open ends abut against each other, as at 92.
  • a coupling member 94 of hardenable plastic material surrounds the abutting ends of the sections 90a, 90b to provide a fluidtight seal and to hold the sections against axial and/or angular movement relative to each other.
  • the coupling member 94 is formed subsequent to mounting of sections 90a, 90b on the shaft 80, Le, subsequent to insertion of the piston 139.
  • Each cap 84 has, a cylindrical portion 86 which is adjacent to the respective axial end of the shell 90 and is formed with a helical face cam 88.
  • the cams 88 are formed by the helical shoulders between the cylindrical portions 86 and the adjoining ends of the shell 90.
  • the two earns 88 are angularly offset by 180 degrees with reference to each other. Sealing elements are installed in the caps 84 inwardly of the respective antifriction bearings 98.
  • the piston 139 comprises an outer cylindrical portion 104 which slides along the internal surface of the shell 90, and two flanges which extend radially be tween the cylinders 104, 106.
  • the piston 139 has two face cams 108 each of which cooperates with one of the cams 88.
  • the lead of cams 108 is the same as that of the cams 8-8.
  • Each flange 110 has a port 112 and the port of one of the flanges is located diametrically opposite the port of the other flange.
  • the outer edge of the annular surface surrounding each port 112 constitutes a seat for a poppetlike valve member 116 forming part of one of two regulating valves which are installed in an internal chamber 111 of the piston 139.
  • the chamber 111 and the two ports 112 constitute a passage through which the braking liquid can flow between the chambers 180a, 1801; of the compartment 180 defined by the housing 89, 90, 89 and the sleeve 102 of the shaft 80.
  • the stems 114 of the valve members 116 are surrounded by prestressed helical valve springs 120 which are attached to disk-shaped retainers 118 at the inner ends of the respective stems 114 and to the adjoining flanges 110'. Each spring 114 tends to urge the respective valve member 116 away from the respective seat. In other words, when the piston 139 is at a standstill or when the piston moves slowly toward the one or the other of the caps 84, the chamber 111 is free to communicate with the chambers a, 1801) of the compartment 180 in the shell 90.
  • the operation of the just described braking roller is very similar to that of the braking roller shown in FIGS. 1 to 3.
  • liquid in the right-hand chamber 180b of the compartment 180 causes the lower valve member 116 to bear against the seat on the right-hand flange 110 and to thus oppose rotation of the shell 90 which latter thereby brakes the article travelling along the roller conveyor.
  • the piston 139 thereupon moves to the left, as viewed in FIG. 4, the upper valve member 116 is caused to move toward or to engage its seat and to thus again oppose rotation of the shell 90.
  • the braking action is again proportional to rotational speed of the shell.
  • the improved braking roller can be modified in a number of ways without departing from the spirit of my invention.
  • the braking roller can be equipped with other types of regulating valves, such as annular valves or the like.
  • the braking roller of FIGS. 1 to 3 could be provided with a single regulating valve and the roller of FIGS. 4-5 can be provided with two or more pairs of regulating valves.
  • a braking roller for use in roller conveyors or the like comprising a shaft; means for holding said shaft against rotation; a hollow housing including a cylindrical shell and two end walls rotatably mounted on said shaft so that the housing can rotate in response to engagement between the external surface of said shell and an article which travels along the conveyor, said housing defining with said shaft a liquid-filled compartment; a piston axially movably mounted on said shaft and dividing said compartment into a pair of chambers; cooperating cams provided on said piston and said housing and arranged to move the piston back and forth in response to rotation of said housing, said piston having at least one passage extending between said chambers; and regulating valve means provided in said passage to throttle the flow of liquid between said chambers at a rate which increases in response to increasing rotational speed of said housing.
  • said regulating valve means comprises a valve member which is movable in said passage to and from a neutral position in which said valve member offers a minimal resistance to the flow of liquid between said chambers, and means for yieldably urging said valve member to neutral position.
  • valve members are poppets.
  • valve members are of annular shape.
  • a braking roller as defined in claim 1, wherein said piston comprises an outer cylindrical portion in sliding engagement with the internal surface of said shell, an inner cylindrical portion surrounding said shaft, and at least one flange integral with and extending between said cylindrical portions.
  • a braking roller as defined in claim 1 wherein I said shell comprises two cylindrical sections arranged 3:399752 9/1968 Orwmend-to-end and further comprising coupling means sealingly securing said sections to each other. 5 FOREIGN PATENTS 19.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Braking Arrangements (AREA)
  • Rollers For Roller Conveyors For Transfer (AREA)
US764464A 1967-10-19 1968-10-02 Braking roller Expired - Lifetime US3511350A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DEST27484A DE1279539B (de) 1967-10-19 1967-10-19 Bremsrolle fuer Foerderbahnen

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US3511350A true US3511350A (en) 1970-05-12

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US764464A Expired - Lifetime US3511350A (en) 1967-10-19 1968-10-02 Braking roller

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US (1) US3511350A (fr)
DE (1) DE1279539B (fr)
FR (1) FR1601324A (fr)
GB (1) GB1198870A (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4215772A (en) * 1979-05-29 1980-08-05 F. Jos. Lamb Company Retarder for gravity conveyors
US5642804A (en) * 1996-07-23 1997-07-01 Continental Conveyor & Equipment Co., L.P. Pulley brake
US6354424B1 (en) * 2000-06-01 2002-03-12 Ancra International, Llc. Brake roller for use in roller tray assembly for loading and unloading cargo
US10392197B1 (en) * 2018-07-06 2019-08-27 Precision, Inc. Conveyor rollers that include a floating bearing

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012011485A1 (de) * 2012-06-09 2013-12-12 Volkswagen Aktiengesellschaft Bremsmodul für einen Schwerkraftförderer
DE102014018769B3 (de) * 2014-12-16 2016-03-03 Interroll Holding Ag Rolle mit Innenbaugruppe

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1189917B (de) * 1962-03-08 1965-03-25 Electrolux Ab Bremsrolle fuer einen aus hintereinanderliegenden Tragrollen gebildeten Rollgang
US3399752A (en) * 1967-03-07 1968-09-03 Fisholow Prod Ltd Gravity roller conveyors
DE1289779B (de) * 1967-05-10 1969-02-20 Schaefer H Kg Hydraulische Bremsrolle

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1183434B (de) * 1962-11-21 1964-12-10 Otto Peters Jr Fa Vorrichtung zur Regulierung der Laufgeschwindigkeit von auf einer geneigten Bahn gleitendem Gut

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1189917B (de) * 1962-03-08 1965-03-25 Electrolux Ab Bremsrolle fuer einen aus hintereinanderliegenden Tragrollen gebildeten Rollgang
US3399752A (en) * 1967-03-07 1968-09-03 Fisholow Prod Ltd Gravity roller conveyors
DE1289779B (de) * 1967-05-10 1969-02-20 Schaefer H Kg Hydraulische Bremsrolle

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4215772A (en) * 1979-05-29 1980-08-05 F. Jos. Lamb Company Retarder for gravity conveyors
US5642804A (en) * 1996-07-23 1997-07-01 Continental Conveyor & Equipment Co., L.P. Pulley brake
AU713897B2 (en) * 1996-07-23 1999-12-16 Continental Conveyor & Equipment Company, L.P. Pulley brake
US6354424B1 (en) * 2000-06-01 2002-03-12 Ancra International, Llc. Brake roller for use in roller tray assembly for loading and unloading cargo
US10392197B1 (en) * 2018-07-06 2019-08-27 Precision, Inc. Conveyor rollers that include a floating bearing

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Publication number Publication date
DE1279539B (de) 1968-10-03
FR1601324A (fr) 1970-08-17
GB1198870A (en) 1970-07-15

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