CA1196944A - Bearing ring or the like with set screw - Google Patents
Bearing ring or the like with set screwInfo
- Publication number
- CA1196944A CA1196944A CA000455508A CA455508A CA1196944A CA 1196944 A CA1196944 A CA 1196944A CA 000455508 A CA000455508 A CA 000455508A CA 455508 A CA455508 A CA 455508A CA 1196944 A CA1196944 A CA 1196944A
- Authority
- CA
- Canada
- Prior art keywords
- screw
- set screw
- tapped
- threads
- ring
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
- F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
- F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
- F16C35/063—Fixing them on the shaft
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C19/00—Bearings with rolling contact, for exclusively rotary movement
- F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
- F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
- F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls
-
- 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
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C2226/00—Joining parts; Fastening; Assembling or mounting parts
- F16C2226/10—Force connections, e.g. clamping
Abstract
BEARING RING OR THE LIKE WITH SET SCREW
ABSTRACT OF THE DISCLOSURE
The invention contemplates an improved set-screw shaft mounting for a machine element such as the inner race ring of an antifriction bearing. Tolerances are closely controlled for both the set-screw threads and the tapped-hole threads, for the case of set-screw threads which are yieldable in the context of an interference (i.e., friction-fit) to the tapped hole, the interference being such as to occasion a friction torque which is but a small fraction of the conven-tional maximum comfortable torque of wrench appli-cation by a machinist, using a conventional wrench, such as an Allen wrench. The low friction torque enables the machinist to know precisely when the set screw intercepts the shaft into which it is driven, and he can then know that his manually applied maximum torque will be serving essentially only the intended purpose of clamping to the shaft.
Extended running life is realized for bearings thus mounted, as compared to conventional set-screw clamping.
ABSTRACT OF THE DISCLOSURE
The invention contemplates an improved set-screw shaft mounting for a machine element such as the inner race ring of an antifriction bearing. Tolerances are closely controlled for both the set-screw threads and the tapped-hole threads, for the case of set-screw threads which are yieldable in the context of an interference (i.e., friction-fit) to the tapped hole, the interference being such as to occasion a friction torque which is but a small fraction of the conven-tional maximum comfortable torque of wrench appli-cation by a machinist, using a conventional wrench, such as an Allen wrench. The low friction torque enables the machinist to know precisely when the set screw intercepts the shaft into which it is driven, and he can then know that his manually applied maximum torque will be serving essentially only the intended purpose of clamping to the shaft.
Extended running life is realized for bearings thus mounted, as compared to conventional set-screw clamping.
Description
6~
B~ARING RING OR THE LIKE WITH SET SCREW
BACKGROUND OF THE INVENTION
The invention relates to set-screw retentlon of a bearing ring, such as the inner race ring of an antifriction bearing, to a shaft, for hopefully fixed antirotational engagement to the shaft.
Antifriction bearings used in fans, blowers, conveyors and other industrial machinery are fre-quently slide-fitted (i.e., loosely fitted) into position on straight shafting and locked to the shaft by means of set screws. Set screws are thread-mounted into tapped holes in the inner ring of such a bearing, with a non-interference fit~ generally a clearance in the order of 0.002 inch, because an interference fit can give rise to such local stress as to rupture the ring, it being noted that generally the pitch diameter of threads in the tapped hole is greater than inner-ring thickness, i.e., greater than 18 depth of the tapped hole.
49~ ~ -Orlomoski, Patent No. 3,517,717 discloses self-locking screws with threads having yieldable rib formations for such interference fit -to tapped holes as to effecti.vely lock a screw against loose-ness, virtually regardless of the vibratory (orrotating) and load environment to which the parts secured by the screw may be subjected. But the use of threads with yieldable rib formations presents a problem for bearing-ring mountiny to a shaft, because conventional specifications for the interferenee fit of such screws call for such high interference as offer unpredictable set-serew holding ability. High interferenee suggests the prospeet of great holding ability, but this is a delusion if, as is the faet with current specifications, the torque needed to advance the high-interference set-screw fit is anything like the maximum torque to which the inner bearing ring can be safely subjected. There is thus uncertainty as to whether the encountered torque is that of binding the set-screw point to the shaft or is that of advancing the set screw in the tapped hole. With such uncertainty, the value of interference fit via yieldable thread formations can be lost, and what the machinist may have thought was a good setting torque for binding the inner ring to the shaft may turn out to be an ineffective, inadequate and destructive fit, destructive of the parts, of bearing life, and of production time for the involved machine.
BRIEF STATE~ENT OF T~E INVENTION
It is an object of the invention to provide a substantially improved set-screw relationship, :Eor the (: -speclfic situation of effectively anchoring a shaft-mounted machine element, such as the inner riny of an antifriction bearing, to a shaft.
It is a specific object to achieve the above object within the limitation of use of standard wrench techniques by machinists having merely ordinary skill.
Another specific object is to provide a set-screw and tapped-hole relationship such that yieldable inter-ference characterizes set-screw advance in the tapped hole at a torque level which is materially less than the tolerable maximum torque of binding the set-screw point into the shaft, so that the machinist will not be deceived or uncertain with regard to effectiveness 15 of his securing the bearing ring to the shaft. -~-For the range of shaft sizes evaluated to date, namely, shafts of l/2 to 2-inch diameter, the invention achieves the foregoing objects by careful control of tolexances as to set-screw pitch diameter and as to pitch diameter of threads in the tapped hole. Gener-ally, for this range of shaft size, for which set-screw sizes will range from so called "10-32" at the small end to "3/8 x 2~" at the large end, the maximum com-bined interference of the involved pitch diametexs is about 0.005 inch, resulting in screw-advancing torsional resistance which is but a small fxaction of the tolerable maximum torque of binding the screw point into the 28 shaft.
,. . ~ ... .. , .. _ .. _ =___~_ _ . _ , - . .. . .. .. _ 4~
DETAILED DESCRIPTION
The invention will be described for a preferred embodiment, in conjunction with the accompanying drawings, in which:
Fig. 1 is a fragmentary vertical sectional view through an antifriction bearing suitable for set-screw mounting to a shaft;
Fig. 2 is a left-end view of the inner ring of the bearing of Fig. 1; and Fig. 3 is a graph depicting torque as a function of interference, to comparatively show a range of critical importance to the invention, as compared with standard dimensional relationships.
Fig. 1 shows the invention embodied in an anti-fri,ction bearing comprising inner and outer race rings 10-11 with interposed antifriction elements 12 riding the races of rings 10-11, and with a plastic retainer 13 holding the elements 12 in suitably spaced relation about the bearing axis. The particular bearing shown has a so-called wide inner ring 10, for which one axial end extends in a region 14 beyond the corresponding axial end of the outer ring 11; within region 14, two like tapped set-screw holes 15-16 will be understood to accommodate set screws 17-18 at 90-degree spacing about the bearing axis. To lock the inner ring to a shaft 19 of cold rolled steel, the two set screws are driven into the shaft 19, under circumstances of maximum torque and yieldable interference fit, to be described.
Each of the set screws 17-18 is of the self~loc]cing thread variety, commercially available from Holo-Krome --4-- ..
__, .. . .
~9~
Company, West E~artford, Connecticut, being character-ized by a continuous yieldable rib on that flank of ~he thread which is not relied upon for radially inward force development when driven against the shaft (19). In other words, and considering the driven end of a set screw to be its upper end, the thread of each set screw is specified for full-area conformance of the upper flank (of the thread) to the corresponding flank of the tapped thread 15 (16) in which it is -to fit; and the continuous yieldable rib is an integral formation of the lower flank (of the thread) such that it will have specified interference with the lower flank of the tapped thread 15 (16) in which it is to fit.
The foregoing relationship, i.e., set-screw lnter-ference with the tapped hole, has been found to require --further definition, if the commercially available self-locking set screw is to serve for extended re-tention of an antifriction bearing ring to a shaftO The reason for this is that data from the commercial source (or from any other source) is not suitable for the mounted-bearing situation. For example, and referring to Fig. 3, commer-cial-source data and recommendations for a l/~-inch diameter screw having 28 threads per inch call for a standard thread-size tolerance of +0.002 to +0.008 inch, with respect to pitch diameter, and for a tapped-hole thread tolerance of -0.001 to +0.002 inch, with respect to the pitch diameter; with such tolerances, the torque to advance the screw in its tapped hole can be as great as 25 inch-pounds.
.. . . . . . . _ . . . . .
For the case of a socketed set-screw configu-ration, as shown for standard Allen-wrench drive of the set screw, it is considered that a rnaximum tight-ening torque of 75 inch-pounds is the practical lirnit of wrench-driven action. This torque is readily, comfortably and manually achievable by the machinist, using the standard Allen-wrench; but the problem with standard tolerance specifications is that, even if they are carefull.y followed, the machinist will have great difficulty in recognizing the point at which the screw engages the shaft and in knowing that he has applied sufficient torque (beyond the frictional torque of screw advance in the tapped hole) to produce an effective screw-point engagement to the shaft. If friction torque is too great, the machinist can be deceived into thinking he has tightened the screw to the shaft when in fact he has either not reached the shaft or he has only barely engaged the shaft.
In accordance with the invention, tolerances are so selected for both the set screws and the tapped holes that a maximum friction torque of 11 inch-pounds is realized, thus providing a substantially enlarged margin within which to be assured that 75 inch-pound wrench torque will very substantially drive the point of each set screw against the shaft. At the same time, the further result is obtained that set-screw engage~
ment to the shaft is an unmistakable event, calling for immediate elevation of torque, at very little incremen-tal rotation of the screw. To achieve this result, for the l/~-inch by 2~ screws involved, FigO 3 shows that .. ...
r ~6~
tapped-hole thread tolerance plus set-screw thread tolerance should, when combined, not exceed 0.005 inch; illustratively, this results from a tapped-hole thread tolerance of 0 to 0.003 inch and a set-screw thread tolerance of 0.003 to 0.005 inch, each with respect to the pltch diameter of the threads.
~or set-screw tolerance of the character indicated, in conjunction with a bearing inner riny 10 of 1.000 to 1.005 inch bore diameter and 1.332 outer diameter, fitted to shafting of 0.996-inch diameter cold rolled steel, very dramatic improve-ments in inner ring mounting have been observed in destructive misaligning overload testing. In these cases, the set screws have been 1/4 x 28 gaged to 15 0.226~ inch pitch diameter within the tolerance +0.003 to +0.005; screw length has been 0.187 inch, from an Allen-socketed upper end to a concaved (118 included angle) and spirally knurled "point", all of hardness Rc 45 to ~3. And the inner-race ring hardness has been Rc 59 to 63. All bearings tested were subjected to what would otherwise be considered a destructive misaligning overload, spring-loaded at a level of 440 inch-pounds in the direction to twist the bearing raceways out of the same plane, and with a steady driven inner-ring speed of 755 ~.p.m. Bearings retained by standard set-screws (i.e., non-yielding and not self-locking) ~ould loosen their set screws in relatively short time (e.g., less than one minute to a small number of hours) or would ultimately destroy the bearing, whereas those retained by the indicated clearance-controlled interference fit of yieldable set-screws 17-18, not only is the number of hours extended more than ten-fold, but in virtually every case, the bearing remained in place on the shaft, even though the bearings showed signs of wear; and in a significant number of cases, the mounte~ bear-ing was fit for further service, even after 2S0-hours running.
The invention has been described for the specific example of yieldable set-screw fastenings, with low-torque interference fit, in the so-called 1/4 x 28 size. The principles of the invention have, however, been found to be applicable to other sizes, accommodated on shafts ranging from 0.5-inch --to 2-3/16-inch diameter, for which applicable set-screw sizes are as follows:
Maximum `-Combined Interference, Allen-Wrench Design Maximum Over Pitch 20 Threads Torque Limit Friction Torque Diameter -10-3233 in.~lbs. 11 in.-lbs. 0.005 1/4~2875 in.-lbs. 11 in.-lbs. 0.005 5/16-24150 in.-lbs. 21 in.-lbs. 0.006 3/8-24270 in.~lbs. 25 in.-lbs. 0.006 In the discussion thus far, it has been brought out that the drag torque of the advancing set screw should not be so great as to deceive the mechanic into thinking the set screw point is tight against the shaft when in fact it is not. A further corollary benefit of controlling this torque is that the difference between the drag torque and the maximum turning torque (i.e., 75 in.-lbs. for the 1/4-inch slze) is the torque range available within which _ _ . _ . .. . .
~a69~ ( to lock the inner ring 10 to the shaft. In other words, if drag torque is too great, there may nok be enough torque range within which to assuredly and securely lock ring 10 to the shaft; yet, with the invention, the lesser drag torque provides a large rangè within which to develop an assuredly secure locked relationship.
While the invention has been described in . detail for a specific embodiment, it will be under-stood that modifications may be made, as for different sizes and thread specifications, without departing from the scope of the invention.
B~ARING RING OR THE LIKE WITH SET SCREW
BACKGROUND OF THE INVENTION
The invention relates to set-screw retentlon of a bearing ring, such as the inner race ring of an antifriction bearing, to a shaft, for hopefully fixed antirotational engagement to the shaft.
Antifriction bearings used in fans, blowers, conveyors and other industrial machinery are fre-quently slide-fitted (i.e., loosely fitted) into position on straight shafting and locked to the shaft by means of set screws. Set screws are thread-mounted into tapped holes in the inner ring of such a bearing, with a non-interference fit~ generally a clearance in the order of 0.002 inch, because an interference fit can give rise to such local stress as to rupture the ring, it being noted that generally the pitch diameter of threads in the tapped hole is greater than inner-ring thickness, i.e., greater than 18 depth of the tapped hole.
49~ ~ -Orlomoski, Patent No. 3,517,717 discloses self-locking screws with threads having yieldable rib formations for such interference fit -to tapped holes as to effecti.vely lock a screw against loose-ness, virtually regardless of the vibratory (orrotating) and load environment to which the parts secured by the screw may be subjected. But the use of threads with yieldable rib formations presents a problem for bearing-ring mountiny to a shaft, because conventional specifications for the interferenee fit of such screws call for such high interference as offer unpredictable set-serew holding ability. High interferenee suggests the prospeet of great holding ability, but this is a delusion if, as is the faet with current specifications, the torque needed to advance the high-interference set-screw fit is anything like the maximum torque to which the inner bearing ring can be safely subjected. There is thus uncertainty as to whether the encountered torque is that of binding the set-screw point to the shaft or is that of advancing the set screw in the tapped hole. With such uncertainty, the value of interference fit via yieldable thread formations can be lost, and what the machinist may have thought was a good setting torque for binding the inner ring to the shaft may turn out to be an ineffective, inadequate and destructive fit, destructive of the parts, of bearing life, and of production time for the involved machine.
BRIEF STATE~ENT OF T~E INVENTION
It is an object of the invention to provide a substantially improved set-screw relationship, :Eor the (: -speclfic situation of effectively anchoring a shaft-mounted machine element, such as the inner riny of an antifriction bearing, to a shaft.
It is a specific object to achieve the above object within the limitation of use of standard wrench techniques by machinists having merely ordinary skill.
Another specific object is to provide a set-screw and tapped-hole relationship such that yieldable inter-ference characterizes set-screw advance in the tapped hole at a torque level which is materially less than the tolerable maximum torque of binding the set-screw point into the shaft, so that the machinist will not be deceived or uncertain with regard to effectiveness 15 of his securing the bearing ring to the shaft. -~-For the range of shaft sizes evaluated to date, namely, shafts of l/2 to 2-inch diameter, the invention achieves the foregoing objects by careful control of tolexances as to set-screw pitch diameter and as to pitch diameter of threads in the tapped hole. Gener-ally, for this range of shaft size, for which set-screw sizes will range from so called "10-32" at the small end to "3/8 x 2~" at the large end, the maximum com-bined interference of the involved pitch diametexs is about 0.005 inch, resulting in screw-advancing torsional resistance which is but a small fxaction of the tolerable maximum torque of binding the screw point into the 28 shaft.
,. . ~ ... .. , .. _ .. _ =___~_ _ . _ , - . .. . .. .. _ 4~
DETAILED DESCRIPTION
The invention will be described for a preferred embodiment, in conjunction with the accompanying drawings, in which:
Fig. 1 is a fragmentary vertical sectional view through an antifriction bearing suitable for set-screw mounting to a shaft;
Fig. 2 is a left-end view of the inner ring of the bearing of Fig. 1; and Fig. 3 is a graph depicting torque as a function of interference, to comparatively show a range of critical importance to the invention, as compared with standard dimensional relationships.
Fig. 1 shows the invention embodied in an anti-fri,ction bearing comprising inner and outer race rings 10-11 with interposed antifriction elements 12 riding the races of rings 10-11, and with a plastic retainer 13 holding the elements 12 in suitably spaced relation about the bearing axis. The particular bearing shown has a so-called wide inner ring 10, for which one axial end extends in a region 14 beyond the corresponding axial end of the outer ring 11; within region 14, two like tapped set-screw holes 15-16 will be understood to accommodate set screws 17-18 at 90-degree spacing about the bearing axis. To lock the inner ring to a shaft 19 of cold rolled steel, the two set screws are driven into the shaft 19, under circumstances of maximum torque and yieldable interference fit, to be described.
Each of the set screws 17-18 is of the self~loc]cing thread variety, commercially available from Holo-Krome --4-- ..
__, .. . .
~9~
Company, West E~artford, Connecticut, being character-ized by a continuous yieldable rib on that flank of ~he thread which is not relied upon for radially inward force development when driven against the shaft (19). In other words, and considering the driven end of a set screw to be its upper end, the thread of each set screw is specified for full-area conformance of the upper flank (of the thread) to the corresponding flank of the tapped thread 15 (16) in which it is -to fit; and the continuous yieldable rib is an integral formation of the lower flank (of the thread) such that it will have specified interference with the lower flank of the tapped thread 15 (16) in which it is to fit.
The foregoing relationship, i.e., set-screw lnter-ference with the tapped hole, has been found to require --further definition, if the commercially available self-locking set screw is to serve for extended re-tention of an antifriction bearing ring to a shaftO The reason for this is that data from the commercial source (or from any other source) is not suitable for the mounted-bearing situation. For example, and referring to Fig. 3, commer-cial-source data and recommendations for a l/~-inch diameter screw having 28 threads per inch call for a standard thread-size tolerance of +0.002 to +0.008 inch, with respect to pitch diameter, and for a tapped-hole thread tolerance of -0.001 to +0.002 inch, with respect to the pitch diameter; with such tolerances, the torque to advance the screw in its tapped hole can be as great as 25 inch-pounds.
.. . . . . . . _ . . . . .
For the case of a socketed set-screw configu-ration, as shown for standard Allen-wrench drive of the set screw, it is considered that a rnaximum tight-ening torque of 75 inch-pounds is the practical lirnit of wrench-driven action. This torque is readily, comfortably and manually achievable by the machinist, using the standard Allen-wrench; but the problem with standard tolerance specifications is that, even if they are carefull.y followed, the machinist will have great difficulty in recognizing the point at which the screw engages the shaft and in knowing that he has applied sufficient torque (beyond the frictional torque of screw advance in the tapped hole) to produce an effective screw-point engagement to the shaft. If friction torque is too great, the machinist can be deceived into thinking he has tightened the screw to the shaft when in fact he has either not reached the shaft or he has only barely engaged the shaft.
In accordance with the invention, tolerances are so selected for both the set screws and the tapped holes that a maximum friction torque of 11 inch-pounds is realized, thus providing a substantially enlarged margin within which to be assured that 75 inch-pound wrench torque will very substantially drive the point of each set screw against the shaft. At the same time, the further result is obtained that set-screw engage~
ment to the shaft is an unmistakable event, calling for immediate elevation of torque, at very little incremen-tal rotation of the screw. To achieve this result, for the l/~-inch by 2~ screws involved, FigO 3 shows that .. ...
r ~6~
tapped-hole thread tolerance plus set-screw thread tolerance should, when combined, not exceed 0.005 inch; illustratively, this results from a tapped-hole thread tolerance of 0 to 0.003 inch and a set-screw thread tolerance of 0.003 to 0.005 inch, each with respect to the pltch diameter of the threads.
~or set-screw tolerance of the character indicated, in conjunction with a bearing inner riny 10 of 1.000 to 1.005 inch bore diameter and 1.332 outer diameter, fitted to shafting of 0.996-inch diameter cold rolled steel, very dramatic improve-ments in inner ring mounting have been observed in destructive misaligning overload testing. In these cases, the set screws have been 1/4 x 28 gaged to 15 0.226~ inch pitch diameter within the tolerance +0.003 to +0.005; screw length has been 0.187 inch, from an Allen-socketed upper end to a concaved (118 included angle) and spirally knurled "point", all of hardness Rc 45 to ~3. And the inner-race ring hardness has been Rc 59 to 63. All bearings tested were subjected to what would otherwise be considered a destructive misaligning overload, spring-loaded at a level of 440 inch-pounds in the direction to twist the bearing raceways out of the same plane, and with a steady driven inner-ring speed of 755 ~.p.m. Bearings retained by standard set-screws (i.e., non-yielding and not self-locking) ~ould loosen their set screws in relatively short time (e.g., less than one minute to a small number of hours) or would ultimately destroy the bearing, whereas those retained by the indicated clearance-controlled interference fit of yieldable set-screws 17-18, not only is the number of hours extended more than ten-fold, but in virtually every case, the bearing remained in place on the shaft, even though the bearings showed signs of wear; and in a significant number of cases, the mounte~ bear-ing was fit for further service, even after 2S0-hours running.
The invention has been described for the specific example of yieldable set-screw fastenings, with low-torque interference fit, in the so-called 1/4 x 28 size. The principles of the invention have, however, been found to be applicable to other sizes, accommodated on shafts ranging from 0.5-inch --to 2-3/16-inch diameter, for which applicable set-screw sizes are as follows:
Maximum `-Combined Interference, Allen-Wrench Design Maximum Over Pitch 20 Threads Torque Limit Friction Torque Diameter -10-3233 in.~lbs. 11 in.-lbs. 0.005 1/4~2875 in.-lbs. 11 in.-lbs. 0.005 5/16-24150 in.-lbs. 21 in.-lbs. 0.006 3/8-24270 in.~lbs. 25 in.-lbs. 0.006 In the discussion thus far, it has been brought out that the drag torque of the advancing set screw should not be so great as to deceive the mechanic into thinking the set screw point is tight against the shaft when in fact it is not. A further corollary benefit of controlling this torque is that the difference between the drag torque and the maximum turning torque (i.e., 75 in.-lbs. for the 1/4-inch slze) is the torque range available within which _ _ . _ . .. . .
~a69~ ( to lock the inner ring 10 to the shaft. In other words, if drag torque is too great, there may nok be enough torque range within which to assuredly and securely lock ring 10 to the shaft; yet, with the invention, the lesser drag torque provides a large rangè within which to develop an assuredly secure locked relationship.
While the invention has been described in . detail for a specific embodiment, it will be under-stood that modifications may be made, as for different sizes and thread specifications, without departing from the scope of the invention.
Claims (8)
1. An antifriction bearing, comprising inner and outer race rings, antifriction elements riding the races of said rings, at least one axial end of said inner ring being characterized by a region extending axially beyond the corresponding axial end of said outer baring ring, a tapped radial set-screw hole in said inner-ring region, and a set screw in said -tapped hole, the pitch diameter of said set screw being in the range up to at least substantially 3/8 inch, and the threads of said set screw and tapped hole having yieldable inter-ference fit with a combined maximum interference of substantially 0.005 inch.
2. An antifriction bearing according to claim 1, in which said tapped hole is one of two at substantially 90-degree spacing, and said set screw is one of two in the respective tapped holes.
3. An antifriction bearing according to claim 1, in which said set screw is of pitch diameter greater than its length.
4. An antifriction bearing according to claim 1, in which the pitch diameter of threads in said tapped hole is greater than the thickness of said inner race ring.
5. An antifriction bearing according to claim 1, in which said set screw has threads with yieldable rib formations having yieldable inter-ference fit with standard threads in the tapped hole.
6. An antifriction bearing according to claim 1, in which the inner end of said set screw is of the knurled-cup variety.
7. As an article of manufacture, a machine element having a circumferentially continuous annular body of bore to fit a shaft, a tapped radial set-screw hole in said body, and a set screw in said tapped hole, the pitch diameter of said set screw being in the range up to at least substantially 3/8 inch, and the threads of said set screw and tapped hole having yiedlable interference fit with a combined maximum interference of substantially 0.005 inch.
8. The article of claim 7, wherein said element is the inner race ring of an antifriction bearing, and said tapped hole is intermediate the raceway region and one of the axial ends of said ring.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000455508A CA1196944A (en) | 1984-05-31 | 1984-05-31 | Bearing ring or the like with set screw |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000455508A CA1196944A (en) | 1984-05-31 | 1984-05-31 | Bearing ring or the like with set screw |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1196944A true CA1196944A (en) | 1985-11-19 |
Family
ID=4127977
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000455508A Expired CA1196944A (en) | 1984-05-31 | 1984-05-31 | Bearing ring or the like with set screw |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1196944A (en) |
-
1984
- 1984-05-31 CA CA000455508A patent/CA1196944A/en not_active Expired
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