CA1251347A - Free spinning laminated nut with automatic lock - Google Patents
Free spinning laminated nut with automatic lockInfo
- Publication number
- CA1251347A CA1251347A CA000531671A CA531671A CA1251347A CA 1251347 A CA1251347 A CA 1251347A CA 000531671 A CA000531671 A CA 000531671A CA 531671 A CA531671 A CA 531671A CA 1251347 A CA1251347 A CA 1251347A
- Authority
- CA
- Canada
- Prior art keywords
- nut
- segments
- loading
- load
- bolt
- 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
Landscapes
- Bolts, Nuts, And Washers (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
The invention provides a caged nut comprised of stacked-conical spring segments that automatically and positively self-locks when tightened to a selected pre-loading, without adjustment. The nut is free running until seated, and the automatic lock mechanism ratchets freely with respect to the cage while the nut is being run down to its sealed position. Reverse rotation of the cage is prevented, however. A ratcheting element in the automatic lock mechanism allows the nut to be tightened by free rotation in the "on" direction but the ratchet prevents rotation in the "off" direction. At whatever value of preload desired, the nut is tightened to the extent necessary to provide that pre-load and the automatic lock mechanism will lock it positively in that position. The invention also includes a caged nut having stacked conical spring washer segments in which the segments are so formed as to provide a more uniform thread loading, over the entire length of the threaded portion of the segments. The invention further includes a caged free-spinning nut characterized by a prevailing tongue resisting counter-rotation having at least two washer segments in which one of the segments is formed of a material which takes a permanent set upon loading and the other segment is formed of a material that returns substantially to its original form following release of the loading force.
The invention provides a caged nut comprised of stacked-conical spring segments that automatically and positively self-locks when tightened to a selected pre-loading, without adjustment. The nut is free running until seated, and the automatic lock mechanism ratchets freely with respect to the cage while the nut is being run down to its sealed position. Reverse rotation of the cage is prevented, however. A ratcheting element in the automatic lock mechanism allows the nut to be tightened by free rotation in the "on" direction but the ratchet prevents rotation in the "off" direction. At whatever value of preload desired, the nut is tightened to the extent necessary to provide that pre-load and the automatic lock mechanism will lock it positively in that position. The invention also includes a caged nut having stacked conical spring washer segments in which the segments are so formed as to provide a more uniform thread loading, over the entire length of the threaded portion of the segments. The invention further includes a caged free-spinning nut characterized by a prevailing tongue resisting counter-rotation having at least two washer segments in which one of the segments is formed of a material which takes a permanent set upon loading and the other segment is formed of a material that returns substantially to its original form following release of the loading force.
Description
3 ~7 BACKGROUND OF THE INVENTION
Free spinning laminated nuts utilizing lamina-tions of hex shaped hardened coned-disc springs, formed as a helex or tapped to match the bolt threads are known in the prior art. Such nuts (sold by Peterson-American Corporation under the trademark "Elephant" nuts) have stacked aligned multi-ple threaded discs retained by a steel outer hex shaped cage.
Wrenching dimensions may conform to standard SAE~IFI sizes.
These nuts are free running until seated. Locking load is applied by additional rotation after seating, which compresses and partially flattens the conical spring discs with resulting mechanical interference on the thread flanks due to the change in hole size as the conical disc flattens. This results i~ thread interference that resists unloading that might other-wise occur as a result of vibration. Thus, the independently loaded conical spring threaded segments when flattened create a thread interference that tends to lock the nut against rotation, or loosening, when subjected to vibration.
As compared to other free spinning locknuts, these nuts effect a dimensional change under loading. Theyhave a conical spring ac~ion tha~ enables them to be coun~er rotated over half a turn or so without loss of total load or loss of interference.
However, the prior art laminated nut, described above, requires for positive locking a secondary operation of adjustment to align holes for cotter key insertion, wiring, or requires mechanical nut deformation into a slot or recess. Further, in the prior art, the loading on the threads of the nut segments in non-uniform, to the extent such thae the stress is concentrat-ll 5 ~3~ ~
~ed in the first thread adjacent the bearing surface. At that¦point the stress may be as much as 200% or more higher than ¦the average stress in the remaining threads.
l SUMMARY OF THE INVENTION
According the present invention, the above referred l to disadvantages of the prior art Elephant nuts are elimina~ed, 10 ¦ and a new combination of elements is provided which forms ~
caged laminated nut that automatically and positively self-locks when tightened to a selected pre-loading 9 without adjustment.
¦The nut is free running until seated, and the automatic lock ¦mechanism ratchets freely with respect to the cage while the ¦nut is being run down to its seated position. Reverse rotation ¦of the cage is prevented, however, A ratcheting element in ¦the automatic lock mechanism allows the nut to be tightened ¦by free rotation in the "on" direction, but the ratchet prevents ¦rotation in the l-off" direction. At whatever value of pre-load ¦desired, the nut is tightened to the extent necess~ry to provide ¦that pre-load and the automatic lock mechanism will lock lt ¦positively in that position without "backing or filling" neces-¦sary to cotter key locking.
¦ To back off or remove the nut~ a tool is required to unlock the locking elements of the automatic lock~ and only then can ~he nut be rotated in the loosening direc~ion.
The invention also includes a new laminated nut having stacked conical spring washer segments in which the segments are so formed as to provide a more uniform thread loading, over the entire length of the threaded portion of the segment , ~ 5 ~
as compared ~o the prior art laminated nut referred ~o above.
According to the invention the load/deflection ratio of at least one of the conical spring washer segments is made greater for a~other spring segment. Preferably the segment next to the load surface is made wi~h the larger load/deflection ratio, for example by making that segment of greater thickness than the other spring washer segment. When the segment nearest to the load is thus made of increased load/deflection ratio then another of the spring washers c\f lesser thickness, then the washer of greater ioad/deflection ratio will deflect at a smaller rate than the other con~eal spring washer and when the nut is fully tightened will take up or absorb a greater portion of the total stress than otherwise would be the case.
This causes the load to be more evenly distributed among the threads of the various laminated spring washer segments and tends to eliminate or reduce failure by successive (i.e.g one after another) ~hread strlpping or by shearing of the bolt~
According to a broad aspect, the invention relates to a nut composed of stacked internally-threaded conical spring washer segements retained in stacked, aligned, relationship by a surrounding cage, said segments being threaded around a bolt as a single unit, said segements including a top segment having a predetermined deflection when subjected to a predeter-mined axial load and a bottom segment having a clifferent pr etermined deElection when subjected to the same axial load.
3~
- 4a -RIEF DESCRIPTION OF THE DRAWINGS
Figure 1 of the drawings is a side view, partly in section, of a spindle for a front drive automobile in which the tapered roller bearings are pre-loaded to a selected value by an au~omatic locking caged laminated nut constructed in accordance with the present invention.
Figure 2 is a plan view of the automatic locking nut of Figure 1.
Figure 3 is a sectional view along the lines 3 3 of the nut in Figure 2.
Figure 4 is a side view of the nut of Figure 2.
Figure 5 is a plan view of the ratchet plate of the, automatic nut locking mechanism.
Figures 6 and 7 are partial views showing ~he opera~ion of the ratchet lock mechanism.
Figure 8 is a view~ similar to Figure 3, of a modifi-cation of the caged laminated nut of this inven~ion, incorporat-ing means for loading the threads of the conical spring segments more uniformly than was the case in prior art laminated nut.
In Figures 3 and 8 it will be noticed that, for conve nience, the outer edges of the washers are shown to be cylindri-cal. In actuality each of these surfaces would be slightly conical.
Figure 9 is a graph comparng the effect oE relaxation or dimensional changes on a solid nut with the effect of such changes on an Elephant nut. The nut size illustrated is M23 X
1.5.
Figures 10, 11 and 12 show a tool, or fixture for disengagement of the nut lock for removal of the nut.
DETAXLED DESCRIPTION
A particularly important application of the present invention is for spindles for front wheel drive automobiles.
Figure 1 shows such a spindle 10, including tapered roler bear-ings 12,14 which must, for proper operation, be pre-loaded to a selected value and then maintained pre-loaded at that value for long periods of operation, including operation while subject to vibration and shock.
A spindle nut for pre-loading said bearings and main-taining the pre-~oad during operations of the automobile, con-structed according to the present invention, is shcwn at 18.
After assembly of the spindle components, nut 18 ~ 3 ~
is run down freely, either by hand or by tool 3 on the threaded end portion of the spindle bolt 20 until it seats against a washer which transmits the force to a collar or wheel hub splined to the spindle at 16. The collar in turn transmits the pre- -S loading force to the tapered roller bearings 12,14. Such forcemay be, for example, of the order of magnitude of 5000 psi.
After the spindle nut seats, it is tightened by a wrench until the force it applies to the bearings is increased to the selected pre-loading value. The spindle bolt is placed in tension, and the tapered roller bearings are pre-loaded in compression. Tightening of nut 18 creates this tension and compression, to a degree determined by ~he nut tightening torque. The total clamp load generated by the nut is in the magnitude of 17,000 to 22,000 pounds.
The "turndown" of nut 18 will seat th~ bottom face of the nu~ flatly against the flat top of the washer on which it bears. It also, after it seats, will partially flatten the conical spring washer segments 40,42,44,46 (Fig. 3) and thereby create a spring force which gradually increases as ~he segments become more and more flattened, i.e. as they approach their planar position. The design is such that when the nut is fully tightened the conical spring segments are still no~ completely flat,but still have some bow. A typical bolt load design will flatten the conical spring washers by 60/70~/o~ They are not en~irely flattened.
As the nut 20 is tightened 9 ratchet lock 32, as shown in Figures 2,3,4,5,6, and 7~ will ratchet, with the lugs 34 being freed from the locking slots 26 in cage 22 as the cage is rotated clockwise. The ratchet lock has four fingers 36 integral therewith, composed of spring steel just as is the ~1 case with the conical spring sçgments. These four fingers act to center the nut on the bolt and, in addition, one of them drops into and engages a slot 38 in the side of the spindle bolt and thus locks the ratchet plate 32 to the spindle bolt against relative rotation, just as soon as the nut is rotated on the bolt by as little as ~, of a turn. When this happens, the ratchet plate 32 in effect becomes locked to the spindle 20. However, the nut itself can still be rotated (tightened/or loosened depending on the direction of rotation,) by the ratchet-ing action shown in Figures 6 and 7 as explained above, simplyby turning cage 22 with a socket wrench which in turn rstates the conical spring segments 40,42,44 and 46 in somewhat the same manner (until they are seated) as a solid nut is run down on a bolt.
The nut can thus be tightened, to the position in which it exerts the selected preload force on bearings 12,14 and then will be automatically locked by one of the lugs 36 being engaged in slot 38 in the side of the bolt. No backward rotation is necessary to form that lock, at exactly the desired pre-load Ratchet 32 and lugs 34 thereon enable the nut to be tightened to exactly the desired pre-load and then hold the nut in that position.
In the ratcheting operation, during run down of the nut 18, there must of course be some provision made to allow lugs 34 to disengage from the slots 26 in cage 22~ This is provided by forming slots in the sidewall of cage 22 at each corner of the hexagonal cage. Such slots allow each side wall to flex between the slots, and about the lower corner as a hinge, thus allowing the cage to free itself from lugs 34 as the cage is rotated clockwise relative to the spindle bolt and ratchet lock 32.
Thus there is formed ~ new automatic and positive lock which requires only tightening ~f the nut with the usual wrench. Once in place and locked in the desired position, it simply won't come loose, regardless of vibrations, and fully meets presently known product liability requirements.
The use of this lock is of course not limited to laminated nuts. It may also be used with solid nuts. I~ has particular utility however for lock nuts for spindles for fron~
drive automobiles where a high degree of precision and at the same time positive safety is required.
~ s previously stated~ all parts of the lock nu~ of this invention can be made of spring steel or othPr ~pring material and the ratcheting action in the embodiment shown is provided by flexing of the side walls of the nut. ~owever, the flexing need only be very slight and it is found in practice that the usual socket wrench tolerances are sufficient to allow the socket head to fit over the nut, and to rotate the nut, with ratcheting action and consequent side wall flexing without bend-ing. In fact, the flexing wall action ~ends to hold the socket or the nut until it is tighteened to the point where the ~atchet locks in final position and the socket is to be removedO
In the embodiment shown, twelve lugs 34, and 6 slots 26 are provided, The load bearing components of nut 18, as shown in ~igures 2 through 7, consist of four conical washer spring segments 40,42,44 and 46 which are stacked and aligned to form in effect a laminated nut.
It should be noted that the combination shown of the ratchet wi~h self seeking fingers provides an entirely new result, of substantial commercial advantage. The job not only can be done better, but also cheaper.
The angle used for each cone shaped spring segment can be calulated by a formula disclosed in Schnoor's Disc Spring Handbook, pages 12-17. As previously stated, the spring discs are not calculated completely to flatten under the designed load; they flex, both up and down as the bolt elongates, con-tracts, or vibrates.
Figure 9 compares the results obtained rom a solid nut shown at the left of the Figure and so marked, with the results obtained from a spring disc laminated nut with cone spring segments. As will be seen, the bearing pre-loads are maintained over wide ranges of deflection for the conical spring disc laminated nuts (the two right hand curves~ as compared with the 9 solid nut in the left hand curves.
The formulas relating to loads necessary to fla~ten cone-spring discs show that, other things being held constant, the load to flatten will increase with disc thickness. This principl~ is utilized in Figure 8 to provide a nut of greater
Free spinning laminated nuts utilizing lamina-tions of hex shaped hardened coned-disc springs, formed as a helex or tapped to match the bolt threads are known in the prior art. Such nuts (sold by Peterson-American Corporation under the trademark "Elephant" nuts) have stacked aligned multi-ple threaded discs retained by a steel outer hex shaped cage.
Wrenching dimensions may conform to standard SAE~IFI sizes.
These nuts are free running until seated. Locking load is applied by additional rotation after seating, which compresses and partially flattens the conical spring discs with resulting mechanical interference on the thread flanks due to the change in hole size as the conical disc flattens. This results i~ thread interference that resists unloading that might other-wise occur as a result of vibration. Thus, the independently loaded conical spring threaded segments when flattened create a thread interference that tends to lock the nut against rotation, or loosening, when subjected to vibration.
As compared to other free spinning locknuts, these nuts effect a dimensional change under loading. Theyhave a conical spring ac~ion tha~ enables them to be coun~er rotated over half a turn or so without loss of total load or loss of interference.
However, the prior art laminated nut, described above, requires for positive locking a secondary operation of adjustment to align holes for cotter key insertion, wiring, or requires mechanical nut deformation into a slot or recess. Further, in the prior art, the loading on the threads of the nut segments in non-uniform, to the extent such thae the stress is concentrat-ll 5 ~3~ ~
~ed in the first thread adjacent the bearing surface. At that¦point the stress may be as much as 200% or more higher than ¦the average stress in the remaining threads.
l SUMMARY OF THE INVENTION
According the present invention, the above referred l to disadvantages of the prior art Elephant nuts are elimina~ed, 10 ¦ and a new combination of elements is provided which forms ~
caged laminated nut that automatically and positively self-locks when tightened to a selected pre-loading 9 without adjustment.
¦The nut is free running until seated, and the automatic lock ¦mechanism ratchets freely with respect to the cage while the ¦nut is being run down to its seated position. Reverse rotation ¦of the cage is prevented, however, A ratcheting element in ¦the automatic lock mechanism allows the nut to be tightened ¦by free rotation in the "on" direction, but the ratchet prevents ¦rotation in the l-off" direction. At whatever value of pre-load ¦desired, the nut is tightened to the extent necess~ry to provide ¦that pre-load and the automatic lock mechanism will lock lt ¦positively in that position without "backing or filling" neces-¦sary to cotter key locking.
¦ To back off or remove the nut~ a tool is required to unlock the locking elements of the automatic lock~ and only then can ~he nut be rotated in the loosening direc~ion.
The invention also includes a new laminated nut having stacked conical spring washer segments in which the segments are so formed as to provide a more uniform thread loading, over the entire length of the threaded portion of the segment , ~ 5 ~
as compared ~o the prior art laminated nut referred ~o above.
According to the invention the load/deflection ratio of at least one of the conical spring washer segments is made greater for a~other spring segment. Preferably the segment next to the load surface is made wi~h the larger load/deflection ratio, for example by making that segment of greater thickness than the other spring washer segment. When the segment nearest to the load is thus made of increased load/deflection ratio then another of the spring washers c\f lesser thickness, then the washer of greater ioad/deflection ratio will deflect at a smaller rate than the other con~eal spring washer and when the nut is fully tightened will take up or absorb a greater portion of the total stress than otherwise would be the case.
This causes the load to be more evenly distributed among the threads of the various laminated spring washer segments and tends to eliminate or reduce failure by successive (i.e.g one after another) ~hread strlpping or by shearing of the bolt~
According to a broad aspect, the invention relates to a nut composed of stacked internally-threaded conical spring washer segements retained in stacked, aligned, relationship by a surrounding cage, said segments being threaded around a bolt as a single unit, said segements including a top segment having a predetermined deflection when subjected to a predeter-mined axial load and a bottom segment having a clifferent pr etermined deElection when subjected to the same axial load.
3~
- 4a -RIEF DESCRIPTION OF THE DRAWINGS
Figure 1 of the drawings is a side view, partly in section, of a spindle for a front drive automobile in which the tapered roller bearings are pre-loaded to a selected value by an au~omatic locking caged laminated nut constructed in accordance with the present invention.
Figure 2 is a plan view of the automatic locking nut of Figure 1.
Figure 3 is a sectional view along the lines 3 3 of the nut in Figure 2.
Figure 4 is a side view of the nut of Figure 2.
Figure 5 is a plan view of the ratchet plate of the, automatic nut locking mechanism.
Figures 6 and 7 are partial views showing ~he opera~ion of the ratchet lock mechanism.
Figure 8 is a view~ similar to Figure 3, of a modifi-cation of the caged laminated nut of this inven~ion, incorporat-ing means for loading the threads of the conical spring segments more uniformly than was the case in prior art laminated nut.
In Figures 3 and 8 it will be noticed that, for conve nience, the outer edges of the washers are shown to be cylindri-cal. In actuality each of these surfaces would be slightly conical.
Figure 9 is a graph comparng the effect oE relaxation or dimensional changes on a solid nut with the effect of such changes on an Elephant nut. The nut size illustrated is M23 X
1.5.
Figures 10, 11 and 12 show a tool, or fixture for disengagement of the nut lock for removal of the nut.
DETAXLED DESCRIPTION
A particularly important application of the present invention is for spindles for front wheel drive automobiles.
Figure 1 shows such a spindle 10, including tapered roler bear-ings 12,14 which must, for proper operation, be pre-loaded to a selected value and then maintained pre-loaded at that value for long periods of operation, including operation while subject to vibration and shock.
A spindle nut for pre-loading said bearings and main-taining the pre-~oad during operations of the automobile, con-structed according to the present invention, is shcwn at 18.
After assembly of the spindle components, nut 18 ~ 3 ~
is run down freely, either by hand or by tool 3 on the threaded end portion of the spindle bolt 20 until it seats against a washer which transmits the force to a collar or wheel hub splined to the spindle at 16. The collar in turn transmits the pre- -S loading force to the tapered roller bearings 12,14. Such forcemay be, for example, of the order of magnitude of 5000 psi.
After the spindle nut seats, it is tightened by a wrench until the force it applies to the bearings is increased to the selected pre-loading value. The spindle bolt is placed in tension, and the tapered roller bearings are pre-loaded in compression. Tightening of nut 18 creates this tension and compression, to a degree determined by ~he nut tightening torque. The total clamp load generated by the nut is in the magnitude of 17,000 to 22,000 pounds.
The "turndown" of nut 18 will seat th~ bottom face of the nu~ flatly against the flat top of the washer on which it bears. It also, after it seats, will partially flatten the conical spring washer segments 40,42,44,46 (Fig. 3) and thereby create a spring force which gradually increases as ~he segments become more and more flattened, i.e. as they approach their planar position. The design is such that when the nut is fully tightened the conical spring segments are still no~ completely flat,but still have some bow. A typical bolt load design will flatten the conical spring washers by 60/70~/o~ They are not en~irely flattened.
As the nut 20 is tightened 9 ratchet lock 32, as shown in Figures 2,3,4,5,6, and 7~ will ratchet, with the lugs 34 being freed from the locking slots 26 in cage 22 as the cage is rotated clockwise. The ratchet lock has four fingers 36 integral therewith, composed of spring steel just as is the ~1 case with the conical spring sçgments. These four fingers act to center the nut on the bolt and, in addition, one of them drops into and engages a slot 38 in the side of the spindle bolt and thus locks the ratchet plate 32 to the spindle bolt against relative rotation, just as soon as the nut is rotated on the bolt by as little as ~, of a turn. When this happens, the ratchet plate 32 in effect becomes locked to the spindle 20. However, the nut itself can still be rotated (tightened/or loosened depending on the direction of rotation,) by the ratchet-ing action shown in Figures 6 and 7 as explained above, simplyby turning cage 22 with a socket wrench which in turn rstates the conical spring segments 40,42,44 and 46 in somewhat the same manner (until they are seated) as a solid nut is run down on a bolt.
The nut can thus be tightened, to the position in which it exerts the selected preload force on bearings 12,14 and then will be automatically locked by one of the lugs 36 being engaged in slot 38 in the side of the bolt. No backward rotation is necessary to form that lock, at exactly the desired pre-load Ratchet 32 and lugs 34 thereon enable the nut to be tightened to exactly the desired pre-load and then hold the nut in that position.
In the ratcheting operation, during run down of the nut 18, there must of course be some provision made to allow lugs 34 to disengage from the slots 26 in cage 22~ This is provided by forming slots in the sidewall of cage 22 at each corner of the hexagonal cage. Such slots allow each side wall to flex between the slots, and about the lower corner as a hinge, thus allowing the cage to free itself from lugs 34 as the cage is rotated clockwise relative to the spindle bolt and ratchet lock 32.
Thus there is formed ~ new automatic and positive lock which requires only tightening ~f the nut with the usual wrench. Once in place and locked in the desired position, it simply won't come loose, regardless of vibrations, and fully meets presently known product liability requirements.
The use of this lock is of course not limited to laminated nuts. It may also be used with solid nuts. I~ has particular utility however for lock nuts for spindles for fron~
drive automobiles where a high degree of precision and at the same time positive safety is required.
~ s previously stated~ all parts of the lock nu~ of this invention can be made of spring steel or othPr ~pring material and the ratcheting action in the embodiment shown is provided by flexing of the side walls of the nut. ~owever, the flexing need only be very slight and it is found in practice that the usual socket wrench tolerances are sufficient to allow the socket head to fit over the nut, and to rotate the nut, with ratcheting action and consequent side wall flexing without bend-ing. In fact, the flexing wall action ~ends to hold the socket or the nut until it is tighteened to the point where the ~atchet locks in final position and the socket is to be removedO
In the embodiment shown, twelve lugs 34, and 6 slots 26 are provided, The load bearing components of nut 18, as shown in ~igures 2 through 7, consist of four conical washer spring segments 40,42,44 and 46 which are stacked and aligned to form in effect a laminated nut.
It should be noted that the combination shown of the ratchet wi~h self seeking fingers provides an entirely new result, of substantial commercial advantage. The job not only can be done better, but also cheaper.
The angle used for each cone shaped spring segment can be calulated by a formula disclosed in Schnoor's Disc Spring Handbook, pages 12-17. As previously stated, the spring discs are not calculated completely to flatten under the designed load; they flex, both up and down as the bolt elongates, con-tracts, or vibrates.
Figure 9 compares the results obtained rom a solid nut shown at the left of the Figure and so marked, with the results obtained from a spring disc laminated nut with cone spring segments. As will be seen, the bearing pre-loads are maintained over wide ranges of deflection for the conical spring disc laminated nuts (the two right hand curves~ as compared with the 9 solid nut in the left hand curves.
The formulas relating to loads necessary to fla~ten cone-spring discs show that, other things being held constant, the load to flatten will increase with disc thickness. This principl~ is utilized in Figure 8 to provide a nut of greater
2~ load carrying ability because of more uniform thread loading, or increased fatigue life, and of greater self blocking character-istics.
In Figure 8 the bottom cone shaped spring washer segment 72 is of about twice the thickness of the two other segments 68 and 70. This results in a more even distribution of the load, Erom bolt to nut, over the length of the threaded sections 68,70, and 72. Thus the nut is less likely to fail by shear of the bolt, stripping of the threads, or by fatigue failures. A substantial improvemen~ results with no additional cost, simply by novel design.
~ 3~
Three laminated segments are shown in Figure 8 but ~- less or more for example 2 or 4 could be used. The automatic lock of Figures l through 7 also could be added to Figure B
if desired.
S Figures 10,11 and 12 show a tool, or fix~ure for disengagement of the nut lock for removal of the nut. Pin 82 fits in the centering recess of spindle bolt 20 and an arm 84 extends therefrom over the edge of the bolt and under lug 36. Thus lug 36 is lifted out of slot 38, allowing it to be turned, and removed, by a socket wrench which fits over outer cage 22.
Some modifications of this invention will of course be obvious to those skilled in the art. In the embodiment shown in the drawings the components, including the conical spring segments, are made of heat treated spring steel as a preferred material. However, it is possible as a modification of the preferred embodiment to provide a prevailing torque characteristic (interference after counter rotation), by incorpo rating a non heat treatable washer segment in the nut that is permanently flattened by the nut loading. This feature is significant to bearing applications that require bearing clearance adjustment.
Previous designs of the Elephant type nut~ prior to the present inventor, used conical spring segments but did not relate the ununiform nut loading of the segments to functional deflection characteristics. The possible concen tration of loading, in a nut-bolt thread fastening, nearly two thirds of all tension loading occurs at the first thread engaged. This uneven loading of previous multiple element nuts caused accelerated deflection of the first element. The results of this accelerated deflected element caused high stress on the male threads of the bolt wi~h possible thread shear ~esults. Nuts previously made in this manner and commercially marketed would not meet SAE or IFI industry requirements for strength. It is an industry accepted practice that nut strength shear requirements must exceed bolt tensile strength so that the mode of failure is bolt breakage.
The present invention combines the industry established formula used for predicting conical washer beha~iour, (Ref., page 13, Adolf-Schnoor "Disc Spring Handbook") with industry proven load distribution characteristics in nut-bolt joint applications. This combination used in association with other nut bolt tolerance standards allows for design of spring washer segments with predictable behaviour related to bolt loading.
The nut design as proposed is based upon near uniform washer segment deflection and loading bottom to top.
With respect to the mechanically positive automatic lock mechanism of the invention, the lock mechanism automatically engages in a slot or groove or grooves in the associated bolt, stud or shaft, which can be driven by hand or power tools to desired ~orque or clamp load requirements, and is positively locked from counter rotation. The combination of an automatic--self seeking secondary lock mechanism and nut with predictable load-deflection characteristics that contributes spring loading, allows fastener loading of precise joint preload with the torque and clamp load tolerances of industry used power tools. This combination is particularly adapta'ble to loading bearings that require defined preload. Further, the design of this invention does not require any secondary adjustment for precise loading.
Further advantages of the present invention are (1) ~x~
the establishment of design criteria ~hat will produce uniform deflection of the nut related to nut-bolt joint loading that will provide predictable load-deflection and resultant inter-ference for blocking. This combination will provide nut strength relationships commensurate with established industry standards.
The uniform loading of the nut top to bottom is accomplished by varying the washer segment thickness related to loading.
The bottom washer with the greatest load would be the heavy member with subsequent washers reduced in thickness. This means that washer segment thickness can be thickness that is greater than the pitch, more than a single pitch or less than a pitch.; (2) the provision of a parallel load surface for critical loading of joints that contain bearings. Heretoforeg the nut required grinding or special surface finishes related to perpendicularity of the axis of the thread to provide uniform interface loading. The resilient action of this invention allows the in~erface surface to self seek for uniform loading.;
and (3) the provision of an inexpensive tool for the purpose of easily defeating the locking devise to facilitate removal and reuse.
ll l ~3~
¦ OPERATING EXAMPLE
¦ To illustrate the application of ~he ;nvention ~o a ¦ particular use, the following is an example of the automatic ¦nut lock as manufactured for use as the spindle lock nut of-a 11981 Escort and Lynx Ford front wheel drive car:
¦ Ford engineering specified load ME-900.10= 46,5001bs I Proof Load ¦ Application - Front wheel spindle nut design load =
¦ 17-22,000 lbs.
¦ Assembly Torque 180-220 lb.ft.
¦ Nut to have six threads with design dimensional stack ¦ tolerance to accomodate ive threads minimum.
¦ Nut Construction:
I
Conical spring washer elements, o078'l thick with crown of .050", material 1065-1070 spring steel, ratchet locking mechanism and cage - also spring steel. Cage is .036"~ Lock Mechanism is ,040 thick.
Application Description:
Spindle nut to be hand started, driven by Rockwell Tool at 125 RPM. Locking Mechanism to self seek lockinl ;
slot and ratchet free to design clamp load.
The sample spindle nut described above does not incorp-orate varied thickness conical spring washer element. This appli cation is utilizing less than 50% of the nut proof load capacity and is not susceptible to hi8h shear loading.
In Figure 8 the bottom cone shaped spring washer segment 72 is of about twice the thickness of the two other segments 68 and 70. This results in a more even distribution of the load, Erom bolt to nut, over the length of the threaded sections 68,70, and 72. Thus the nut is less likely to fail by shear of the bolt, stripping of the threads, or by fatigue failures. A substantial improvemen~ results with no additional cost, simply by novel design.
~ 3~
Three laminated segments are shown in Figure 8 but ~- less or more for example 2 or 4 could be used. The automatic lock of Figures l through 7 also could be added to Figure B
if desired.
S Figures 10,11 and 12 show a tool, or fix~ure for disengagement of the nut lock for removal of the nut. Pin 82 fits in the centering recess of spindle bolt 20 and an arm 84 extends therefrom over the edge of the bolt and under lug 36. Thus lug 36 is lifted out of slot 38, allowing it to be turned, and removed, by a socket wrench which fits over outer cage 22.
Some modifications of this invention will of course be obvious to those skilled in the art. In the embodiment shown in the drawings the components, including the conical spring segments, are made of heat treated spring steel as a preferred material. However, it is possible as a modification of the preferred embodiment to provide a prevailing torque characteristic (interference after counter rotation), by incorpo rating a non heat treatable washer segment in the nut that is permanently flattened by the nut loading. This feature is significant to bearing applications that require bearing clearance adjustment.
Previous designs of the Elephant type nut~ prior to the present inventor, used conical spring segments but did not relate the ununiform nut loading of the segments to functional deflection characteristics. The possible concen tration of loading, in a nut-bolt thread fastening, nearly two thirds of all tension loading occurs at the first thread engaged. This uneven loading of previous multiple element nuts caused accelerated deflection of the first element. The results of this accelerated deflected element caused high stress on the male threads of the bolt wi~h possible thread shear ~esults. Nuts previously made in this manner and commercially marketed would not meet SAE or IFI industry requirements for strength. It is an industry accepted practice that nut strength shear requirements must exceed bolt tensile strength so that the mode of failure is bolt breakage.
The present invention combines the industry established formula used for predicting conical washer beha~iour, (Ref., page 13, Adolf-Schnoor "Disc Spring Handbook") with industry proven load distribution characteristics in nut-bolt joint applications. This combination used in association with other nut bolt tolerance standards allows for design of spring washer segments with predictable behaviour related to bolt loading.
The nut design as proposed is based upon near uniform washer segment deflection and loading bottom to top.
With respect to the mechanically positive automatic lock mechanism of the invention, the lock mechanism automatically engages in a slot or groove or grooves in the associated bolt, stud or shaft, which can be driven by hand or power tools to desired ~orque or clamp load requirements, and is positively locked from counter rotation. The combination of an automatic--self seeking secondary lock mechanism and nut with predictable load-deflection characteristics that contributes spring loading, allows fastener loading of precise joint preload with the torque and clamp load tolerances of industry used power tools. This combination is particularly adapta'ble to loading bearings that require defined preload. Further, the design of this invention does not require any secondary adjustment for precise loading.
Further advantages of the present invention are (1) ~x~
the establishment of design criteria ~hat will produce uniform deflection of the nut related to nut-bolt joint loading that will provide predictable load-deflection and resultant inter-ference for blocking. This combination will provide nut strength relationships commensurate with established industry standards.
The uniform loading of the nut top to bottom is accomplished by varying the washer segment thickness related to loading.
The bottom washer with the greatest load would be the heavy member with subsequent washers reduced in thickness. This means that washer segment thickness can be thickness that is greater than the pitch, more than a single pitch or less than a pitch.; (2) the provision of a parallel load surface for critical loading of joints that contain bearings. Heretoforeg the nut required grinding or special surface finishes related to perpendicularity of the axis of the thread to provide uniform interface loading. The resilient action of this invention allows the in~erface surface to self seek for uniform loading.;
and (3) the provision of an inexpensive tool for the purpose of easily defeating the locking devise to facilitate removal and reuse.
ll l ~3~
¦ OPERATING EXAMPLE
¦ To illustrate the application of ~he ;nvention ~o a ¦ particular use, the following is an example of the automatic ¦nut lock as manufactured for use as the spindle lock nut of-a 11981 Escort and Lynx Ford front wheel drive car:
¦ Ford engineering specified load ME-900.10= 46,5001bs I Proof Load ¦ Application - Front wheel spindle nut design load =
¦ 17-22,000 lbs.
¦ Assembly Torque 180-220 lb.ft.
¦ Nut to have six threads with design dimensional stack ¦ tolerance to accomodate ive threads minimum.
¦ Nut Construction:
I
Conical spring washer elements, o078'l thick with crown of .050", material 1065-1070 spring steel, ratchet locking mechanism and cage - also spring steel. Cage is .036"~ Lock Mechanism is ,040 thick.
Application Description:
Spindle nut to be hand started, driven by Rockwell Tool at 125 RPM. Locking Mechanism to self seek lockinl ;
slot and ratchet free to design clamp load.
The sample spindle nut described above does not incorp-orate varied thickness conical spring washer element. This appli cation is utilizing less than 50% of the nut proof load capacity and is not susceptible to hi8h shear loading.
Claims (2)
1. A nut composed of stacked internally-threaded conical spring washer segments retained in stacked, aligned, relationship by a surrounding cage, said segments being threaded around a bolt as a single unit, said segments including a top segment having a predetermined deflection when subjected to a predetermined axial load and a bottom segment having a different predetermined deflection when subjected to the same axial load.
2. The nut of claim 1 wherein said top segment has a predetermined thickness for producing a preselected load/
deflection ratio and a bottom segment having a predetermined thickness greater than the thickness of the top segment by a preselected amount sufficient to cause the load from said bolt to said nut to be more evenly distributed over the length of both said top and bottom segments.
deflection ratio and a bottom segment having a predetermined thickness greater than the thickness of the top segment by a preselected amount sufficient to cause the load from said bolt to said nut to be more evenly distributed over the length of both said top and bottom segments.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000531671A CA1251347A (en) | 1980-09-16 | 1987-03-11 | Free spinning laminated nut with automatic lock |
Applications Claiming Priority (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US187,833 | 1980-09-16 | ||
| US06/187,833 US4383787A (en) | 1980-09-16 | 1980-09-16 | Free spinning laminated nut with automatic lock |
| CA000385934A CA1251346A (en) | 1980-09-16 | 1981-09-15 | Free spinning laminated nut with automatic lock |
| CA000531671A CA1251347A (en) | 1980-09-16 | 1987-03-11 | Free spinning laminated nut with automatic lock |
Related Parent Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000385934A Division CA1251346A (en) | 1980-09-16 | 1981-09-15 | Free spinning laminated nut with automatic lock |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1251347A true CA1251347A (en) | 1989-03-21 |
Family
ID=25669435
Family Applications (2)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000531671A Expired CA1251347A (en) | 1980-09-16 | 1987-03-11 | Free spinning laminated nut with automatic lock |
| CA000577061A Expired CA1259830A (en) | 1980-09-16 | 1988-09-09 | Free spinning laminated nut with automatic lock |
Family Applications After (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000577061A Expired CA1259830A (en) | 1980-09-16 | 1988-09-09 | Free spinning laminated nut with automatic lock |
Country Status (1)
| Country | Link |
|---|---|
| CA (2) | CA1251347A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113266634A (en) * | 2021-05-10 | 2021-08-17 | 鲁东大学 | Spring pin for electric power fitting convenient to robot maintenance operation |
-
1987
- 1987-03-11 CA CA000531671A patent/CA1251347A/en not_active Expired
-
1988
- 1988-09-09 CA CA000577061A patent/CA1259830A/en not_active Expired
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113266634A (en) * | 2021-05-10 | 2021-08-17 | 鲁东大学 | Spring pin for electric power fitting convenient to robot maintenance operation |
| CN113266634B (en) * | 2021-05-10 | 2022-08-05 | 鲁东大学 | A spring pin for electric power fittings that is convenient for robot maintenance work |
Also Published As
| Publication number | Publication date |
|---|---|
| CA1259830A (en) | 1989-09-26 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| US4383787A (en) | Free spinning laminated nut with automatic lock | |
| US6019556A (en) | Locking fastener assembly | |
| JP3112940B2 (en) | Fastener with lock screw | |
| US5207543A (en) | Connecting device with a nut and bolt to prevent loosening and losing the nut | |
| US7128511B2 (en) | Fastener | |
| US4267870A (en) | Screw fastener with multi-point wrenching head and locking capabilities | |
| US5855463A (en) | Bolt and nut thread friction locking device with opposite hand threads with a captured spring or spring lock washer | |
| GB2265197A (en) | Self locking nut | |
| US20020015628A1 (en) | Fastener assembly including a screw element and a supporting element | |
| US4854794A (en) | Connector of the nut-and-bolt type | |
| US4930962A (en) | Nut and stud assembly | |
| US3648749A (en) | Fastener assembly with locking capabilities | |
| US20130164093A1 (en) | Fastener | |
| EP0065344A1 (en) | Screw threaded fastener | |
| EP0130304B1 (en) | Double locknut assembly and combination of locknut assembly with a bolt | |
| US3329057A (en) | Threaded fastener device | |
| US5564875A (en) | Locking fastener | |
| CA2349554C (en) | Fastener | |
| CA1251347A (en) | Free spinning laminated nut with automatic lock | |
| EP4121662B1 (en) | Locking threaded fastener assembly | |
| WO1999002870A1 (en) | Torque limiting device | |
| JPH0687713U (en) | Lock screw | |
| JPH1068409A (en) | Locknut |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |