Threaded type fastener
BACKGROUND OF THE INVENTION 
     The invention relates to an improved threaded fastener, for example, a bolt or screw and more particularly to the type of a bolt employed in what is generally referred to as a torque nut. Ever since the first use of threaded fasteners there has been suggested numerous ways and means for preventing the inadvertent loosening of the fastener relative to the piece being secured thereby. The very traditional known &#34;lock&#34; washer would be a well recognized example. Another example would be the cutting of a slot into the free end of a bolt where the slot extends coaxially into the center of the bolt. 
     Even though many of these, and other similar devices and constructions worked reasonably well in certain applications there are certain applications where there exists a real need for an improved means or construction for preventing the fasteners from turning in either direction and losing their desired position and in some cases pre-set critical fastening force or holding power. 
     An example of such a fastener where the need of an improved locking means may be useful is the torque screw type fastener employing torque nuts of the type illustrated in U.S. Pat. No. 4,622,730. One of the many applications of the torque nuts disclosed in this patent is to secure a roller bearing to the journal of a shaft such as the work roll of a rolling mill. 
     These bearings are not only very large expensive items but may operate under extremely high load conditions and speeds and wherein during operation there is a great concern that the bearing be kept from over heating. One of the contributing factors of over heating of the bearing is the degree of &#34;tightness&#34; with which the bearings are held on their journals. While it is required that the bearings be held very firmly, they can not be held so firmly so as to create excessive frictional generated heat leading to early bearing failure. 
     To add to the difficulty, the system with which the bearing is employed and the bearing itself is continuously subject to thermal expansion and dynamic vibrations. Thus there exist a serious need to provide in this and many other cases a screw type fastener useful in a situation where the member being fastened is subject to vibrations and thermal expansion, which will allow a pre-set fastening power or holding position to be maintained. The holding force required may be anywhere between 0 and 100 percent of the maximum holding force the fastener is capable of exerting, but which will still be prevented for turning and hence disturbing the pre-set fastening force. 
     It should be noted that while the torque nuts of the type disclosed in the aforesaid patent are designed not to come loose and remain tight on vibrating on pulsating equipment this is on the general assumption that the nuts have been fully torqued. 
     SUMMARY OF THE INVENTION 
     It is the object of the present invenion to provide an improved threaded type fastener, either for example as a single standard fastener or as one or more of the pre-stressed nuts and bolts of the mechanical stress bolt type fasteners of the aforesaid patent. 
     More particularly, it is an object to provide in combination with a threaded bolt an integral specially designed part or a separate independent part or element that will engage a portion of the bolt in a manner to prevent inadvertent relative rotation between the bolt and the member being held thereby, for use in an application where the bolt is to be maintained in a desired position relative to the member and/or to exert a desired pre-set holding force or power on the member. 
     It is still a further object to form the integral part as an axially extending sloped cut in the outer surface of the threaded or non-threaded portion of the bolt to form a spring like member adopted to forcefully contact a portion of the member being held to prevent relative rotational movement between the two elements, or in the alternative as to the separate independent part, in place of the spring like member an independent spring biased member or a bar spring can be used to carry out the same objectives. 
    
    
     SUMMARY OF THE DRAWINGS 
     The present invention can be better understood when the accompanied description is read along with the following drawings, of which: 
     FIG. 1 is a partial sectional view of a trust collar assembly employed to retain a bearing on a journal of a rolling mill roll and employing the features of the invention, 
     FIG. 2 is a partial end view showing a roll journal-thrust collar arrangement according to a second embodiment of the invention, 
     FIG. 3A is a section view taken along lines A--A of FIG. 2, 
     FIG. 3B is a section view taken along lines B--B of FIG. 2, 
     FIG. 4 is a view, similar to FIG. 1, of a third embodiment of the invention, 
     FIG. 5 is a view, similar to FIG. 1, of a fourth embodiment of the invention, and 
     FIG. 6 is an outside view and FIG. 7 a partial sectional view of a fifth embodiment of the invention. 
    
    
     DETAIL DESCRIPTION OF THE INVENTION 
     With reference first to FIG. 1, there is shown a portion of a rolling mill roll 8, more particularly of a journal portion 10 thereof and the outer axial portion of a well known roller bearing 12 employed to rotatably support the roll. The portion of the bearing shown consist of an inner race 14, one of the rollers of the bearing 16 and an outer race 18. While not shown, the end of the roll 8 terminates immediately to the left of a ring 20, which can be made in the form of a well known split ring, mounted on a reduced portion of the roll, the ring forcibly engages a collar portion 22 of the roll. 
     Between the split ring 20 and the inner race 14 a thrust collar assembly 24 is provided to secure in a desired manner the bearing 12 to the journal portion 10 of the roll. The assembly included a thrust collar 26 mounted concentrically with respect to the adjacent neck portion of the roll and having two bolt circles, the holes of the inner one receiving several equally spaced apart bolts 28, the inner threaded ends thereof being threadedly secured in a spacer ring 30 having its outer circumferencial end portion with a circular enlarged end portion for engaging the split ring 20 by two perpendicular surfaces, one being a load or thrust transferring surface. 
     In the radially outward bolt circle, the thrust collar 26 is provided with a number of equally spaced holes for receiving a number of standard bolts 32 that function as torque jack bolts of the type disclosed in the aforesaid U.S. Pat. No. 4,622,730. In the illustrated case the roll journal portions has a diameter of 231/2 inches and a inner race of a 231/2 inches diameter in its inner most axial portion. 
     The shaft portion of each bolt 32 is formed with separate axial portions, the outer most portion 34 having a threaded connection with the adjacent portion of the thrust collar 26, the portion that extends away from the collar engaging a thrust ring 36 having its opposite end in thrust or load transferring contact with the inner race 14 of the bearing 12. In this way, according to the teaching of U.S. Pat. No. 4,622,730 on the torquing of the bolts 32, the bolts are pre-stressed a pre-determined amount between the bearing and the roll which pre-stressing force holds the bearing on the roll by a pre-determined force. 
     The inner shaft portion 38 of each bolt is provided with a sloped opening, such as formed by a saw cut, extending from the front of the inner shaft portion towards the rear thereof but terminating adjacent the head portion of the bolt and before the cut intersects the center axis of the bolt. This construction forms a spring like member 40 having a projecting outer circular face that forcefully engages a similar inner circular cooperative face of the thrust collar 26, the contact tending to collapse the spring like member as indicated in comparing the full line position with the dash line position in FIG. 1. 
     This construction allows the jack bolts to be tightened or torqued to a degree less than their maximum torque so that the bearing can be held with a desired holding force, but not to the extent of creating over heating in the context discussed above, and wherein the spring like members 40 of the bolts will insure that the bolts will not inadvertently turn even though they are not tight or under any load. 
     The embodiment of FIGS. 2, 3A, and 3B is similar in function and principle to the embodiment of FIG. 1, but is designed to accommodate a bearing holding arrangement where the distance between the bearing and roll end is much smaller than what is shown in FIG. 1. For this reason like part in FIG. 1 will have similar reference members in FIGS. 2, 3A, and 3B and only one jack bolt and guide bolt will be described, it being understood that the other similar bolts are identical. In this second embodiment and in referring first to FIG. 3A the ring 36 is provided with a threaded portion 42 to threadedly receive the outer end of guide bolts 32. The thrust collar 26 has a two part bolt opening, identified as 44 and 46, the head of the bolt being received within the portion 44 while the center portion thereof passes through the part 46 of the opening. While not fully shown, in the construction of FIG. 2 and about which more will be discussed below, the thrust collar transfers its pre-stressed force to the ring 48, which in this embodiment takes the form of a split ring. 
     It will be appreciated that the thrust ring 36 is only held against the inner race 14 of the bearing 12 by the guide bolts 32 and is allowed to &#34;float&#34; since it is not physically connected to the thrust collar 26 and the guide bolts are allowed to freely move relative to the thrust collar. 
     In the second embodiment, with reference first to FIG. 3B, as noted above the thrust collar 26 is designed to accommodate a &#34;short&#34; thrust collar design, however, the collar is provided with a set screw pre-stress jack design instead of standard employed bolts as jack bolts. In this case a set screw 50 takes the place of the jack bolts and is threadedly engaged with the thrust collar 36 by threaded hole 52 formed internally in the collar, the outer end of the which has a set screw opening 54, the inner end engaging the ring 36 in a thrust transferring manner. As noted in FIG. 3B, the outer end of the thrust collar engages the spring ring 48 to transfer the pre-stress force of the set screw to the roll 10. Instead of the spring like member 40 of FIG. 1, there is provided for each set screw a button 56 received in an opening 58, the button being biased outwardly by a spring 60 that fits around the lower shaft portion of the button and wherein the outer portion of the button forcefully contacts the adjacent inner part of the collar 26 to hold it against inadvertent rotation. 
     It will be appreciated that in some bearing securing constructions it may be desired to back off the set screw screws 50 from contact with the ring 36 to a pre-set holding and/or restraining position with respect to the bearing 12, in which case the ring will be allowed to move axially relative to the bearing since the guide bolts are permitted to move relative to the thrust collar 26. 
     Turning now to FIG. 2, which is an outside view of the end facing the heads of the guide bolts 32 and jack set screws 54, there is illustrated a common bolt circle 61 the circumferential positions of the two different bolts, there being shown several equally spaced jack set screws 54 and several equally spaced guide bolts. Also shown in FIG. 2, is a link type fastener 63 for the split ring 48. 
     The embodiments of FIGS. 4 and 5, are the same in principle and function as the embodiment of FIG. 1, FIG. 5 illustrates the opposite end of the roll, similar parts appearing in FIG. 1 have been marked with similar reference numbers. In FIG. 4 the jack bolts 32 instead of having an non-threaded inner portion, the threads are extended the full length of the shaft portion of the bolts. The spring like members 62 forcefully engages the adjacent threaded portions of the thrust collar 36 to hold the jack bolts against inadvertent turning. 
     In FIG. 5 the spring like member of each bolt takes the form of a two piece head of the torque jack bolt, the two pieces being indicated at 64 and 66, in which their outer axial portions most adjacent to the inner portions of the collar 26 forcefully contact the collar to prevent inadvertent rotation of the bolt. 
     Turning now to the last embodiment and to FIGS. 6 and 7, this embodiment is similar in function and principle to the embodiment of FIG. 1 and again similar parts of FIG. 1 are identified with similar reference numbers. Instead of the spring biased button of each torque jack set screws shown in FIG. 3, an external spring member is provided for each set screw in the form of a tension bar 68 having one end positioned and secured to the thrust collar 26 by a bolt-washer unit 70 and having its hooked shaped other end arranged to pass through an opening 72 to forcefully engage an adjacent portion of the set screw 50, as best shown in FIG. 6, to thereby prevent undesired rotation of the set screw. 
     As earlier noted, while the invention has been shown and described in conjunction with several different forms of torque jack-set screw bolts for securing a roller bearing, in its broadest aspects it is meant to relate to a single fastener, such as a standard bolt-nut, or set screw used for any usual purpose. Thus the single bolt shown in the various embodiments of the drawings can be used as a single fastener as their present counterparts are now employed. In addition, as to the thrust collar embodiments shown and described, the invention can be modified from the forms shown and employed for different purposes without deporting from the scope and spirit of the invention.