CA1075183A - Slip friction roller drive - Google Patents
Slip friction roller driveInfo
- Publication number
- CA1075183A CA1075183A CA306,414A CA306414A CA1075183A CA 1075183 A CA1075183 A CA 1075183A CA 306414 A CA306414 A CA 306414A CA 1075183 A CA1075183 A CA 1075183A
- Authority
- CA
- Canada
- Prior art keywords
- disc
- flange
- roller
- axle
- sprocket
- 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
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- Rollers For Roller Conveyors For Transfer (AREA)
Abstract
TITLE OF THE INVENTION: Slip Friction Roller Drive INVENTOR: George Rae ASSIGNEE: Rexnord Inc., a Wisconsin corporation ABSTRACT OF THE DISCLOSURE:
A slip friction drive for powered roller conveyor apparatus which minimizes coupling of forces between the driving engagement and the bearing surfaces and additionally provides an adjusting means for compensating for the varying frictional forces caused by changing loads.
A slip friction drive for powered roller conveyor apparatus which minimizes coupling of forces between the driving engagement and the bearing surfaces and additionally provides an adjusting means for compensating for the varying frictional forces caused by changing loads.
Description
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B~CKG~OUND OF THE INVENTION:
This invention relates to conve~ing apparatus of the powered roller type in which the rollercl are individually driven.
The use of slip drive devices in roller conveyor apparatus are well known in the industry. Examples are ~ound in U.~. Patents Nos. 2,976,981 and 4,006,815. For example, the former discloses a ~procket driven roller in which the sprocket drives the roller by virtue of the frictional forces between the hub of the sprocket and the roller. As the line pressure of the loads increase on the sur~ace of the rollers and provide a counter-torque ~orce, the sprocket being constantly driven begins to slide within the sleeve and accumulation occurs.
The advantages of a slip drive become very ~mportant in environments requiring or exposing the surfaces of the rollers to objects which may become lodged between rollers.
Damage to the object or rollers could result when the roller is positively driven by the driving means. Having the slip function designed into the apparatus minimizes the damage since the counter-torque imposed by the jamming articles overcomes the torque due to the frictional force and the roller becomes stationary.
The present inventio~ provides additional advantages to a slip frictional drive as will be understood by reading the ensuing description. The simplicity of the invention will al90 be evident.
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SUMMARY OF TElE INVENTION:
Each roller of the improved apparatus is supported at one end in a manner similar to conventional rollers of the prior art. That is, conventional rollers are in the form of a cylindrical sleeve. A hub bearing assembly is housed within the sleeve and caps one end thereoE, providing rotational support at that point to the sleeve about a stationary axle. The bearing assembly at the other end o~
the roller is o the slip friction type and comprises a plurality of elements. ~irst, an outer bearing element having an outer diameter dimensioned closely with respect to the inner diameter of the roller is press-fitted within the roller. ~hus, the outer bearing member is keyed to and rotates with the sleeve. A flange of the outer bearing element has an outer diameter equal to or slightly greater than the outer diameter of the roIler sleeve and fits snugly against the sleeve mouth and around its circumference. A
driven element which has a disc-like portion and annular cylindxical extension abuts the flange of the sleeve bearing element and fits within the inner diameter of the slee~e, respectively. An inner bearing elem~nt is keyed to the stationary axle and is positioned between the cylindrical extension of the driven element and axle~
In ordinary situations, the element being driven by a chain or belt or the like rotates about the inner bearing element and, by virtue of friction between the driven element and outer bearing elementl causes the roller _3_ .. . .
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~0~5~3 sleeve to also rotate. When a force opposing rotation of one of the rollers occurs, thereby providin~ a torque counter to the frictional force torque about the axis of rotation , the roller sleeve will become stationary i the counter torque becomes greater than the frictional torque.
Such a situation may occur due to line forces generated by accumulating loads or a force caus~d by the ja~ming of the roller, e.g., due to a foreign article. The driven member, however, continues to rotate.
; 10 To provide uni~orm rotation and wear of the bearing surfaces and ultimate better control o~ rictional forces, it is desireable that coupling o~ torques acting ; upon the apparatus be minimize~. The present invention accomplishes this by ~tructurally de~igning the driven element such that torque created by the driving mean3 acts in a plane juxtaposed to the flange bearing surface of the outer bearing element. In the ca~e of ~ sp~ocket- type driven element, the arc of the sprocket teeth defines a plane sllbstantially coplanar with the plane of the flange surface.
To further improve the frictional force control of the present invention, a means is pro~ided to selectively move or press the driven member against the flange of the outer bearing element. Several alternate means may be employed to accompliqh this result, but a preferred means is to provide a yieldable resilient means positioned against the driven member. The yielda~le re~ilient means may increasingly bear against the driven member which in turn causes an increase in frictional foxce between the driven member and flange. This function may be desireable when light loads are being carried by the rollers.
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1~75183 i i DESCRIPTION OF TEIE DRAWINGS:
Figure 1 is a perspective view of the roller apparatus employing a slip drive in accordance with the present invention.
Figure 2 is a side view of a slip drive and roller in accordance with the present invention.
Figure 3 is a side section view of a slip drive in accordance with the present invention.
Figure 4 i~ arl exploded perspective view of a slip drive in accordance with the present inventiorl.
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~75~ 33 DETAILED DESCRIPTION OF THE P~EFERRED EMBODXMENT:
The roller conveyor apparaltus o~ Figure 1 i~
comprised of three major parts: a frame ~tructure consisting of two parallel rails 10, 12; a plurality of rollers 14 mounted on axles 16 supported ~y rai.ls 10, 12 and a roller drive which is here illustrated as sprocket~ 20 and chain 18. The power ma~ be supplied by any motor (not shown) typically used to drive chain.
Rollers 14 and axles 16 are generally positioned horizon~ally between rails 10, 12 with xollers 14 providing a conveying surface to articles placed on the roller~. To prevent material~ from contacting spxockets 20 and chain 18, both are positioned within a safety enclosure 22. Enclosure 22 serves both as a safety guard and lateral guide for articles being moved along the conveyor. :~-Bach roller 14 i~ an elongated cylinder, usually made of metal sheet material. As ~een in Figure 2, one end of roller 14 houses a typical bearing assembly 24 mounted on axle 16. The innex race of the assembly i~ typically ~ecured or keyed to axle 16 while the outer race i5 keyed to roller 14, thereby providing the roller 14 the ability to rotate about a stationary axle 16.
Figure 3 depicts in side section the slip type functional bearing assembly in accordance with the present invention. As ~hown, there are three major elements: an outer bearing element or sleeve 26; an inner bearing element or bushing 30; and a driven ele~ent which is sprocket 20.
Sleeve 26 fits tightly within roller 14 and has a flange 28 which ~buts the mouth edge of roller 14. Inner bushing 30 ~.
'.i ~ J~,r~ 3 fits over and is ke~ed to stationary axle 16. The key mechanism may be either ~hrough known slot arrangemen~s in the event axle 16 is cylindrical or via geometry of bushing cros~ection if ~he axle 16 is oE the hexagonal type.
Sprocket 20 has a lateral and annular cylindrical extension 21 which ~its between beariny sleeve 26 and bushing 30, Juxtaposed to the wall of sprocket 20 faciny roller 14 is flange 32 o~ bushing 30. Flange 32 fAcilitates insertion a~d removal of bushing 30 and may serve still another important function as descrihed below.
Axle3 16 which are stationary may be keyed by any conventional 810t and torque arrangement with rails 10/ 12 or retained motionless by virtue of geometry in ~as~s where the axles have a hexagonal cross-sectlon and are p~sitioned within hexag~nal rail slots. Cotter pins 17 seen ln Figure
B~CKG~OUND OF THE INVENTION:
This invention relates to conve~ing apparatus of the powered roller type in which the rollercl are individually driven.
The use of slip drive devices in roller conveyor apparatus are well known in the industry. Examples are ~ound in U.~. Patents Nos. 2,976,981 and 4,006,815. For example, the former discloses a ~procket driven roller in which the sprocket drives the roller by virtue of the frictional forces between the hub of the sprocket and the roller. As the line pressure of the loads increase on the sur~ace of the rollers and provide a counter-torque ~orce, the sprocket being constantly driven begins to slide within the sleeve and accumulation occurs.
The advantages of a slip drive become very ~mportant in environments requiring or exposing the surfaces of the rollers to objects which may become lodged between rollers.
Damage to the object or rollers could result when the roller is positively driven by the driving means. Having the slip function designed into the apparatus minimizes the damage since the counter-torque imposed by the jamming articles overcomes the torque due to the frictional force and the roller becomes stationary.
The present inventio~ provides additional advantages to a slip frictional drive as will be understood by reading the ensuing description. The simplicity of the invention will al90 be evident.
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, ~'75~
SUMMARY OF TElE INVENTION:
Each roller of the improved apparatus is supported at one end in a manner similar to conventional rollers of the prior art. That is, conventional rollers are in the form of a cylindrical sleeve. A hub bearing assembly is housed within the sleeve and caps one end thereoE, providing rotational support at that point to the sleeve about a stationary axle. The bearing assembly at the other end o~
the roller is o the slip friction type and comprises a plurality of elements. ~irst, an outer bearing element having an outer diameter dimensioned closely with respect to the inner diameter of the roller is press-fitted within the roller. ~hus, the outer bearing member is keyed to and rotates with the sleeve. A flange of the outer bearing element has an outer diameter equal to or slightly greater than the outer diameter of the roIler sleeve and fits snugly against the sleeve mouth and around its circumference. A
driven element which has a disc-like portion and annular cylindxical extension abuts the flange of the sleeve bearing element and fits within the inner diameter of the slee~e, respectively. An inner bearing elem~nt is keyed to the stationary axle and is positioned between the cylindrical extension of the driven element and axle~
In ordinary situations, the element being driven by a chain or belt or the like rotates about the inner bearing element and, by virtue of friction between the driven element and outer bearing elementl causes the roller _3_ .. . .
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~0~5~3 sleeve to also rotate. When a force opposing rotation of one of the rollers occurs, thereby providin~ a torque counter to the frictional force torque about the axis of rotation , the roller sleeve will become stationary i the counter torque becomes greater than the frictional torque.
Such a situation may occur due to line forces generated by accumulating loads or a force caus~d by the ja~ming of the roller, e.g., due to a foreign article. The driven member, however, continues to rotate.
; 10 To provide uni~orm rotation and wear of the bearing surfaces and ultimate better control o~ rictional forces, it is desireable that coupling o~ torques acting ; upon the apparatus be minimize~. The present invention accomplishes this by ~tructurally de~igning the driven element such that torque created by the driving mean3 acts in a plane juxtaposed to the flange bearing surface of the outer bearing element. In the ca~e of ~ sp~ocket- type driven element, the arc of the sprocket teeth defines a plane sllbstantially coplanar with the plane of the flange surface.
To further improve the frictional force control of the present invention, a means is pro~ided to selectively move or press the driven member against the flange of the outer bearing element. Several alternate means may be employed to accompliqh this result, but a preferred means is to provide a yieldable resilient means positioned against the driven member. The yielda~le re~ilient means may increasingly bear against the driven member which in turn causes an increase in frictional foxce between the driven member and flange. This function may be desireable when light loads are being carried by the rollers.
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1~75183 i i DESCRIPTION OF TEIE DRAWINGS:
Figure 1 is a perspective view of the roller apparatus employing a slip drive in accordance with the present invention.
Figure 2 is a side view of a slip drive and roller in accordance with the present invention.
Figure 3 is a side section view of a slip drive in accordance with the present invention.
Figure 4 i~ arl exploded perspective view of a slip drive in accordance with the present inventiorl.
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~75~ 33 DETAILED DESCRIPTION OF THE P~EFERRED EMBODXMENT:
The roller conveyor apparaltus o~ Figure 1 i~
comprised of three major parts: a frame ~tructure consisting of two parallel rails 10, 12; a plurality of rollers 14 mounted on axles 16 supported ~y rai.ls 10, 12 and a roller drive which is here illustrated as sprocket~ 20 and chain 18. The power ma~ be supplied by any motor (not shown) typically used to drive chain.
Rollers 14 and axles 16 are generally positioned horizon~ally between rails 10, 12 with xollers 14 providing a conveying surface to articles placed on the roller~. To prevent material~ from contacting spxockets 20 and chain 18, both are positioned within a safety enclosure 22. Enclosure 22 serves both as a safety guard and lateral guide for articles being moved along the conveyor. :~-Bach roller 14 i~ an elongated cylinder, usually made of metal sheet material. As ~een in Figure 2, one end of roller 14 houses a typical bearing assembly 24 mounted on axle 16. The innex race of the assembly i~ typically ~ecured or keyed to axle 16 while the outer race i5 keyed to roller 14, thereby providing the roller 14 the ability to rotate about a stationary axle 16.
Figure 3 depicts in side section the slip type functional bearing assembly in accordance with the present invention. As ~hown, there are three major elements: an outer bearing element or sleeve 26; an inner bearing element or bushing 30; and a driven ele~ent which is sprocket 20.
Sleeve 26 fits tightly within roller 14 and has a flange 28 which ~buts the mouth edge of roller 14. Inner bushing 30 ~.
'.i ~ J~,r~ 3 fits over and is ke~ed to stationary axle 16. The key mechanism may be either ~hrough known slot arrangemen~s in the event axle 16 is cylindrical or via geometry of bushing cros~ection if ~he axle 16 is oE the hexagonal type.
Sprocket 20 has a lateral and annular cylindrical extension 21 which ~its between beariny sleeve 26 and bushing 30, Juxtaposed to the wall of sprocket 20 faciny roller 14 is flange 32 o~ bushing 30. Flange 32 fAcilitates insertion a~d removal of bushing 30 and may serve still another important function as descrihed below.
Axle3 16 which are stationary may be keyed by any conventional 810t and torque arrangement with rails 10/ 12 or retained motionless by virtue of geometry in ~as~s where the axles have a hexagonal cross-sectlon and are p~sitioned within hexag~nal rail slots. Cotter pins 17 seen ln Figure
2 may be employed to ensure axles 16 remain between rails 10, 12.
The composition of sleeve 26 and bushing 30 may be of any number of suitable materials but pre~erabl~ should be a polymeric substance such as Delrin~, a tradename of the DuPont Neymours Company. The sprocket 20 may, or example, be made of a glass illed polymeric material such as nylon.
The particular composition of any of the elements, however, is not a critical feature of the invention with the appropriat~
features being wear resistance and amenabillty to friction.
When the chain 18 is driven by a motor (not shown), each sprocket 20 is turned about bushing 30~ The frictional forces generated by the contact between the surfaces vf sprocket 20 and flange ~, and also be~wean the _ ~f ... .
.... _ ..... _ .. . .. .. . . . . .
~7S1~33 surfaceq of sprockek extension 21 and bearing 2~ cause roller3 14 to rotate. Increasing load obviou~ly increa~es the frictional force generated between the surfa~e~ of extension 21 and bearing 26. Contact between sprocket 20 and flange 28 is largely independent of load.
In many slip-type drive devic~s for conveyor roller assemblies~ increasing load per roller necessitate~
an increasillgly large counter-torque to occur before 81ip-page results. It should be noted that frictional forc~s are directly proportlonal to the force normal to the pla~e o~
the contacting sur~aces. For roller conveyors, the normal force is the load acting downward on the roller. ~o over-come the frictional force torque due to the load, a counter-; torque (e.g. line pressure of the articles or ~n object lodged between rollers) equal to the frictional torque must be exerted.
~ Although conveyor roller assemblies are ordinarily ; designed to handle certain magnitudes of loads, the load can still vary considerably from one lot of articles to another ~0 within a given magnitude. Often, it is desireable that the accumulating characteristics of a powered roller assembly be kept sub tantially constant. In other words, while the load per roller increases~ it is fre~uently desired th~t accumu- -lation occur when line pressure reaches a particular level just as would occalr at lower loads per roller so that no further increase in line pressure occurs. The fragile nature o~ articlec~ at high load le~els may well be identical to that of article!s at low load levels and too much line pressure could damage the articles. Addikionally, it is f~
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;
~7~.83 prudent that safety features at least remain constant when load levels increase.
A distinct advantage of the present invention i8 the provision of a means to minimize changes in the friction-S al forces as load per roller changes. As seen in Figure 3 and the exploded perspective of Figure 4~ t~e surface of sprocket 20 contacts flang~ 28. The contact is maintained by the pressure of a helical spring 36 mounted about axle 1 between a nut 3~ and flange 32 of b~aring 30 which while 19 keyed againRt rotational movement relative to axle 16, may be moved longitudinally. Thus, an increase in pressure of spring 36 by movement of nut 38 against 1ange 32 will in turn increase the pressure of flange 32 against sprocket 20 and therefore the frictional force between sprocket 20 and flange 28. This provides an additional frictional toxque-t~
the frictional torque created by ~rictional f~rc~ between sprocket extension 21 and bearing member 26. As stated before, the former torque has the advantage of being virtually independen~c of load.
~he precise mechanism by which pressure of sprocket 20 against flange 32 i~ regulated is not critical. For example, other means could be utilized ~uch as a s~ationary disc member which is keyed to the axle again~t xotational and longi~udinal movement and i9 adapted to receive a plurality of adju~table set screws which may bear against flange 32 or, alte~rnatively, but l~ss pr~erably, the surface of sprock~t 20 itself~ Additionally, the helical s`pring 36 could be~ enlarged to bear directly against sprocket ~' .
_g_ 2~ or an intermediate washer. It would be necessary, however, to key bearing 30 against movement along axle 16.
Under one ~et of circums~ances, the pressure exerted by the surface of sprocket 20 may be so small as to negligibly contribute to the total frictional torque. For example, by properly choosing materials having low coefficients of friction and, when needed, providing solid luhricants, the frictional force can indeed be maintained small. This may be a very desirable circumstance when heavy loads per roller are being experienced by the conveyor assembly.
As the load per roller decreases the surface of sprocket 20 can be urged against ~lange 28 to incr~ase the frictional force. Since this force is acting over a greater distance than the other force component, it should be understood that an excellent degree of control can be exerted over ~he total frictional to~que~ Thus, for light or heavy loads, the total frictional force, torque and therefore the nece3sary counter-torque for accumulation can be maintained essentially the sameO
Another advantage is that each roller can be individually adjusted so as to create zones of varying accumulation characteristics. For example, it may be desirable to create a zone where slippage readily occurs as a safety precaution due to the easy access individuals or operators may have to the assembly in this zone. In such a zone any foreign object would readily stop movement of the -rollers. While in other areas of the assembly well pro-tected by a covering or other means, the frictional torque could be set higher.
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. ' ,. . ': , . -~5~33 Still another advantage may be realized when it is necessary to incline the entire roller assembly slightly to move articles to a higher position relative to ~n initial position. For light loads, frictional slip drives often suffer from the counter-torque cre,ated by gravity being greater than frictional torque genlarated by the load~
Slippage occurs as the articles move up the incline. By being able to regulate and hereincrease the frictional torque, this problem can largely be minimized.
Other advantages~ modifications, and variations may be understood after a reading of this description. It should be understood, however, that all such variations, advantages and modifications should be construed within the spirit of the scope of the claimsO
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The composition of sleeve 26 and bushing 30 may be of any number of suitable materials but pre~erabl~ should be a polymeric substance such as Delrin~, a tradename of the DuPont Neymours Company. The sprocket 20 may, or example, be made of a glass illed polymeric material such as nylon.
The particular composition of any of the elements, however, is not a critical feature of the invention with the appropriat~
features being wear resistance and amenabillty to friction.
When the chain 18 is driven by a motor (not shown), each sprocket 20 is turned about bushing 30~ The frictional forces generated by the contact between the surfaces vf sprocket 20 and flange ~, and also be~wean the _ ~f ... .
.... _ ..... _ .. . .. .. . . . . .
~7S1~33 surfaceq of sprockek extension 21 and bearing 2~ cause roller3 14 to rotate. Increasing load obviou~ly increa~es the frictional force generated between the surfa~e~ of extension 21 and bearing 26. Contact between sprocket 20 and flange 28 is largely independent of load.
In many slip-type drive devic~s for conveyor roller assemblies~ increasing load per roller necessitate~
an increasillgly large counter-torque to occur before 81ip-page results. It should be noted that frictional forc~s are directly proportlonal to the force normal to the pla~e o~
the contacting sur~aces. For roller conveyors, the normal force is the load acting downward on the roller. ~o over-come the frictional force torque due to the load, a counter-; torque (e.g. line pressure of the articles or ~n object lodged between rollers) equal to the frictional torque must be exerted.
~ Although conveyor roller assemblies are ordinarily ; designed to handle certain magnitudes of loads, the load can still vary considerably from one lot of articles to another ~0 within a given magnitude. Often, it is desireable that the accumulating characteristics of a powered roller assembly be kept sub tantially constant. In other words, while the load per roller increases~ it is fre~uently desired th~t accumu- -lation occur when line pressure reaches a particular level just as would occalr at lower loads per roller so that no further increase in line pressure occurs. The fragile nature o~ articlec~ at high load le~els may well be identical to that of article!s at low load levels and too much line pressure could damage the articles. Addikionally, it is f~
.
;
~7~.83 prudent that safety features at least remain constant when load levels increase.
A distinct advantage of the present invention i8 the provision of a means to minimize changes in the friction-S al forces as load per roller changes. As seen in Figure 3 and the exploded perspective of Figure 4~ t~e surface of sprocket 20 contacts flang~ 28. The contact is maintained by the pressure of a helical spring 36 mounted about axle 1 between a nut 3~ and flange 32 of b~aring 30 which while 19 keyed againRt rotational movement relative to axle 16, may be moved longitudinally. Thus, an increase in pressure of spring 36 by movement of nut 38 against 1ange 32 will in turn increase the pressure of flange 32 against sprocket 20 and therefore the frictional force between sprocket 20 and flange 28. This provides an additional frictional toxque-t~
the frictional torque created by ~rictional f~rc~ between sprocket extension 21 and bearing member 26. As stated before, the former torque has the advantage of being virtually independen~c of load.
~he precise mechanism by which pressure of sprocket 20 against flange 32 i~ regulated is not critical. For example, other means could be utilized ~uch as a s~ationary disc member which is keyed to the axle again~t xotational and longi~udinal movement and i9 adapted to receive a plurality of adju~table set screws which may bear against flange 32 or, alte~rnatively, but l~ss pr~erably, the surface of sprock~t 20 itself~ Additionally, the helical s`pring 36 could be~ enlarged to bear directly against sprocket ~' .
_g_ 2~ or an intermediate washer. It would be necessary, however, to key bearing 30 against movement along axle 16.
Under one ~et of circums~ances, the pressure exerted by the surface of sprocket 20 may be so small as to negligibly contribute to the total frictional torque. For example, by properly choosing materials having low coefficients of friction and, when needed, providing solid luhricants, the frictional force can indeed be maintained small. This may be a very desirable circumstance when heavy loads per roller are being experienced by the conveyor assembly.
As the load per roller decreases the surface of sprocket 20 can be urged against ~lange 28 to incr~ase the frictional force. Since this force is acting over a greater distance than the other force component, it should be understood that an excellent degree of control can be exerted over ~he total frictional to~que~ Thus, for light or heavy loads, the total frictional force, torque and therefore the nece3sary counter-torque for accumulation can be maintained essentially the sameO
Another advantage is that each roller can be individually adjusted so as to create zones of varying accumulation characteristics. For example, it may be desirable to create a zone where slippage readily occurs as a safety precaution due to the easy access individuals or operators may have to the assembly in this zone. In such a zone any foreign object would readily stop movement of the -rollers. While in other areas of the assembly well pro-tected by a covering or other means, the frictional torque could be set higher.
: :
. ' ,. . ': , . -~5~33 Still another advantage may be realized when it is necessary to incline the entire roller assembly slightly to move articles to a higher position relative to ~n initial position. For light loads, frictional slip drives often suffer from the counter-torque cre,ated by gravity being greater than frictional torque genlarated by the load~
Slippage occurs as the articles move up the incline. By being able to regulate and hereincrease the frictional torque, this problem can largely be minimized.
Other advantages~ modifications, and variations may be understood after a reading of this description. It should be understood, however, that all such variations, advantages and modifications should be construed within the spirit of the scope of the claimsO
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Claims (5)
1. A roller conveyor apparatus comprising:
(a) a plurality of hollow, cylindrical rollers mounted for rotary movement about stationary axles fixedly secured to spaced, side-support frames, each of said rollers having a rotary bearing assembly at one end thereof;
(b) a driving means for rotating said plurality of rollers; and (c) a slip friction assembly having associated with each said stationary axle:
i. an inner bearing member secured to said stationary axle within the other end of its respective said roller, ii. a driven member having a disc portion adapted to engage the driving means and a cylindrical hub extension positioned within said other end of its respective said roller and having inner and outer bearing surfaces, said inner bearing surface ad-apted to rotate on said inner bearing member, and iii. an outer bearing member having a flange portion and a sleeve portion, said sleeve portion exten-ding into said other end in continuous juxta-position with and secured to the inner side of its respective said roller, said sleeve portion having an inner diameter substantially identical to the outer diameter of the outer bearing surface of said driven member and providing a surface against which said outer surface of said hub extension may engage, said flange portion posi-tioned in an abutting relation with the mouth of said other end of its respective said roller and adjacent said disc portion of said driven member, such that the engagement of said disc portion with the driving means is substantially co-planar with the interface of said disc portion with said flange portion.
(a) a plurality of hollow, cylindrical rollers mounted for rotary movement about stationary axles fixedly secured to spaced, side-support frames, each of said rollers having a rotary bearing assembly at one end thereof;
(b) a driving means for rotating said plurality of rollers; and (c) a slip friction assembly having associated with each said stationary axle:
i. an inner bearing member secured to said stationary axle within the other end of its respective said roller, ii. a driven member having a disc portion adapted to engage the driving means and a cylindrical hub extension positioned within said other end of its respective said roller and having inner and outer bearing surfaces, said inner bearing surface ad-apted to rotate on said inner bearing member, and iii. an outer bearing member having a flange portion and a sleeve portion, said sleeve portion exten-ding into said other end in continuous juxta-position with and secured to the inner side of its respective said roller, said sleeve portion having an inner diameter substantially identical to the outer diameter of the outer bearing surface of said driven member and providing a surface against which said outer surface of said hub extension may engage, said flange portion posi-tioned in an abutting relation with the mouth of said other end of its respective said roller and adjacent said disc portion of said driven member, such that the engagement of said disc portion with the driving means is substantially co-planar with the interface of said disc portion with said flange portion.
2. The apparatus as claimed in claim 1 in which the driven member is a sprocket and the driving means is a chain, the teeth of said sprocket being formed on the outer periphery of said disc and being substantially co planar with the inter-face of the sprocket disc with the flange.
3. The apparatus as claimed in claim 1 or 2 including an adjustable resilient means for biasing said disc toward said flange.
4. The apparatus as claimed in claim 1 or 2 including an adjustable resilient means for biasing said disc toward said flange, and in which said resilient means includes a helical spring about said axle, one end of which is associated with said disc, and an adjustable means associated with the other end of the spring for selectively compressing or releasing said spring.
5. The apparatus as claimed in claim 1 or 2 including an adjustable resilient means for biasing said disc toward said flange, and in which said resilient means includes a helical spring about said axle, one end of which is associated with said disc, and an adjustable means associated with the other end of the spring for selectively compressing or releasing said spring and said bearing member is keyed to said axle against rotational movement and is free to slide along said axle, said inner bearing member having a head in the form of a flange disc with a diameter greater than the inner diameter of said cylindrical hub and additionally positioned between said hub and helical spring, said helical spring abutting said flange disc whereby said flange disc selectively presses against and releases said hub in response to movement of said adjusting means to cause respectively greater and lesser frictional forces to occur between said driven member and said flange portion of the outer bearing member.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA306,414A CA1075183A (en) | 1978-06-28 | 1978-06-28 | Slip friction roller drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA306,414A CA1075183A (en) | 1978-06-28 | 1978-06-28 | Slip friction roller drive |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1075183A true CA1075183A (en) | 1980-04-08 |
Family
ID=4111801
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA306,414A Expired CA1075183A (en) | 1978-06-28 | 1978-06-28 | Slip friction roller drive |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1075183A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4406360A (en) * | 1980-12-22 | 1983-09-27 | Conveyersmith, Inc. | Accumulating conveyer |
| CN107032041A (en) * | 2017-01-17 | 2017-08-11 | 辽宁科技学院 | A kind of friction protection conveyer that can stop at any time and its application method |
| CN108341209A (en) * | 2017-12-21 | 2018-07-31 | 新昌县新凌凯博机械有限公司 | A kind of bearing conveying device |
-
1978
- 1978-06-28 CA CA306,414A patent/CA1075183A/en not_active Expired
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4406360A (en) * | 1980-12-22 | 1983-09-27 | Conveyersmith, Inc. | Accumulating conveyer |
| CN107032041A (en) * | 2017-01-17 | 2017-08-11 | 辽宁科技学院 | A kind of friction protection conveyer that can stop at any time and its application method |
| CN108341209A (en) * | 2017-12-21 | 2018-07-31 | 新昌县新凌凯博机械有限公司 | A kind of bearing conveying device |
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