US20170008539A1 - Slack adjuster for railcar brake - Google Patents
Slack adjuster for railcar brake Download PDFInfo
- Publication number
- US20170008539A1 US20170008539A1 US14/793,768 US201514793768A US2017008539A1 US 20170008539 A1 US20170008539 A1 US 20170008539A1 US 201514793768 A US201514793768 A US 201514793768A US 2017008539 A1 US2017008539 A1 US 2017008539A1
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- US
- United States
- Prior art keywords
- tube
- jaw
- slack adjuster
- groove
- bearing collar
- 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.)
- Abandoned
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B61—RAILWAYS
- B61H—BRAKES OR OTHER RETARDING DEVICES SPECIALLY ADAPTED FOR RAIL VEHICLES; ARRANGEMENT OR DISPOSITION THEREOF IN RAIL VEHICLES
- B61H15/00—Wear-compensating mechanisms, e.g. slack adjusters
- B61H15/0035—Wear-compensating mechanisms, e.g. slack adjusters mechanical and self-acting in both directions
- B61H15/0042—Wear-compensating mechanisms, e.g. slack adjusters mechanical and self-acting in both directions by means of linear adjustment
- B61H15/0057—Wear-compensating mechanisms, e.g. slack adjusters mechanical and self-acting in both directions by means of linear adjustment with screw-thread and nut
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D65/00—Parts or details
- F16D65/38—Slack adjusters
- F16D65/40—Slack adjusters mechanical
- F16D65/62—Slack adjusters mechanical self-acting in both directions for adjusting excessive and insufficient play
- F16D65/66—Slack adjusters mechanical self-acting in both directions for adjusting excessive and insufficient play with screw-thread and nut
Abstract
Description
- The present invention generally relates to a slack adjuster for a railway car braking system.
- Railway cars are widely used for transportation of goods and passengers throughout the United States and abroad. Railway cars generally include one or more truck assemblies including a plurality of specially designed wheels for traveling along a vast infrastructure of railway car tracks. Braking systems are generally disposed between adjacent pairs of wheels for facilitating the stopping or slowing down of the railway car.
- A braking system can generally include a pair of brake assemblies corresponding to a pair of trucks supporting a railway car. Each of the brake assemblies includes leading and trailing brake beam assemblies, each with a pair of brake heads having brake shoes for contact with an outer periphery of the wheels when the leading and trailing brake beam assemblies are moved away from one another. Commonly, an air cylinder is provided between the pair of brake assemblies in the braking system for generating the force that causes such movement. The air cylinder or another actuator is connected to each of the pair of brake assemblies and respective leading and trailing brake beam assemblies through a linkage system including various rods and levers.
- Many braking systems further include assemblies conventionally known as slack adjusters for adjusting the movement of the leading and trailing brake beam assemblies of the respective brake assemblies as required. In particular, slack adjusters compensate for brake shoe wear and wheel wear by adjusting its length. Typically, a slack adjuster is built into one of the rods in linkage system.
- Accordingly, the slack adjuster must be capable of withstanding a large amount of force. For example, certain slack adjusters must be capable of withstanding more than of 20,000 to 30,000 pounds of force during operation. In order to accommodate such a large amount of force, the load bearing components of the slack adjuster are typically connected using intricate bolting systems. With such systems, however, the parts must be thicker than may otherwise be necessary to accommodate the holes for the bolts, and each of the holes must he precisely cut.
- Therefore, an improved system or method for attaching components of a slack adjuster capable of bearing a large amount of force would be useful.
- Aspects and advantages of the invention are set forth below in the following description, or may be obvious from the description, or may he learned through practice of the invention.
- In one exemplary embodiment of the present invention, a slack adjuster is provided for a railroad car braking system. The slack adjuster defines an axial direction and a circumferential direction. The slack adjuster includes a first jaw, a rod assembly attached to the first jaw, a nut assembly having at least a portion rotatably engaged with the rod assembly, and a tube attached to the nut assembly. The tube extends generally along the axial direction between a first end and a second end. Additionally, the tube encloses at least a portion of the rod assembly. The slack adjuster additionally includes a second jaw including a base attached to the second end of the tube. The base of the second jaw defines a groove therein extending generally along the circumferential direction, at least a portion of the tube crimped into the groove in the base of the second jaw attaching the tube to the base of the second jaw.
- In another exemplary embodiment of the present invention, a slack adjuster is provided for a railroad car braking system defining an axial direction and a circumferential direction. The slack adjuster includes a first jaw and a second jaw. The first jaw is positioned at a first end of the slack adjuster along the axial direction and the second jaw is positioned at a second end of the slack adjuster along the axial direction. The slack adjuster additionally includes a rod assembly attached to the first jaw and extending generally along the axial direction, a tube attached to the second jaw and also extending generally along the axial direction, and a nut assembly configured to transfer a force between the rod assembly and the tube. The nut assembly includes a first bearing collar defining a groove therein extending generally along the circumferential direction. At least a portion of the tube is crimped into the groove in the first bearing collar, attaching the tube to the first bearing collar.
- In an exemplary aspect of the present disclosure, a method for manufacturing a slack adjuster for a railroad car braking system is provided. The slack adjuster defines an axial direction and the method includes attaching a first jaw to a rod assembly, positioning a nut assembly over a threaded portion of the rod assembly, and attaching the nut assembly to a tube extending generally along the axial direction such that at least a portion of the nut assembly is fixed along the axial direction relative to the tube. The method also includes attaching the tube to a base of a second jaw by crimping a portion of the tube into a groove defined in the base of the second jaw, fixing the base of the second jaw to the tube.
- Those of ordinary skill in the art will better appreciate the features and aspects of such embodiments, and others, upon review of the specification.
- A full and enabling disclosure of the present invention, including the best mode thereof to one skilled in the art, is set forth more particularly in the remainder of the specification, including reference to the accompanying figures, in which:
-
FIG. 1 provides a braking system in accordance with an exemplary embodiment of the present disclosure installed in an exemplary railway car truck. -
FIG. 2 provides a perspective view of a slack adjuster in accordance with an exemplary embodiment of the present disclosure. -
FIG. 3 provides a close up exploded view of a portion of the exemplary slack adjuster ofFIG. 2 , prior to installation of a pawl box. -
FIG. 4 provides a close-up perspective view of a portion of the exemplary slack adjuster ofFIG. 2 , with the pawl box installed. -
FIG. 5 provides a side, cross-sectional view of a center portion of the exemplary slack adjuster ofFIG. 2 . -
FIG. 6 provides a perspective view of a first bearing collar of a nut assembly of the exemplary slack adjusterFIG. 2 . -
FIG. 7 provides a perspective view of a second bearing collar of the nut assembly of the exemplary slack adjuster ofFIG. 2 -
FIG. 8 provides a perspective view of a second end of the exemplary slack adjuster ofFIG. 2 . -
FIG. 9 provides a side, cross-sectional view of the second end of the exemplary slack adjuster ofFIG. 2 . -
FIG. 10 provides a side, cross-sectional view of a crimp die for crimping a portion of the tube of the exemplary slack adjuster ofFIG. 2 into a groove defined in a component of the exemplary slack adjuster ofFIG. 2 . -
FIG. 11 provides a flow diagram of a method for manufacturing a slack adjuster in accordance with an exemplary aspect of the present disclosure. - Reference now will be made in detail to embodiments of the invention, one or more examples of which are illustrated in the drawings. Each example is provided by way of explanation of the invention, not limitation of the invention. In fact, it will be apparent to those skilled in the art that various modifications and variations can be made in the present invention without departing from the scope or spirit of the invention. For instance, features illustrated or described as part of one embodiment can be used with another embodiment to yield a still further embodiment. Thus, it is intended that the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents.
- Referring now to the Figures,
FIG. 1 provides abraking system 50 in accordance with an exemplary embodiment of the present disclosure. Thebraking system 50 is generally referred to as a body mounted brake system, configured for attachment to a body of a railway car (not shown). It should be appreciated, however, that in other exemplary embodiments, thebraking system 50 may instead he what is generally referred to as a truck mounted brake system mounted to a railway car truck. - As shown, the
braking system 50 generally includes a leadingbraking system 52 and a trailingbraking system 54 spaced from one another along a longitudinal direction L. The leadingbraking system 52 may be configured with a leading railway car truck having a plurality of wheels and mounted under the railway car (not shown), and similarly the trailingbraking system 54 may be configured with a trailing railway car truck having a plurality of wheels and also mounted under the railway car (not shown). The wheels of the leading and trailing railway car trucks may be configured to engage an infrastructure of railway car tracks. As used herein, the terms “leading” and “trailing” are terms used to describe a location of certain components relative to other components, it being understood that in other embodiments, the orientation of such components may be reversed. - The leading and trailing
braking system brake beam assembly 56 and a trailingbrake beam assembly 58. Each of the leading and trailingbrake beam assemblies braking assemblies brake heads 60 disposed at their respective outer ends. Thebrake heads 60 each include one ormore brake shoes 62 defining a thickness and configured to contact an outer periphery of respective wheels of the railway car trucks. - The
braking system 50 is configured to generate friction with the wheels of the respective railway car trucks to slow the railway car. For the embodiment depicted, the leading and trailingbrake beam assemblies brake assemblies brake shoes 62 and the respective wheels. More particularly, thebraking system 50 generally includes abrake cylinder 64 configured to move the respective leading and trailingbrake beam assemblies lever assembly 66. Thelever assembly 66 generally includes a plurality oflevers 68 and fixedlength rods 70 to generate the desired movement of the respectivebrake beam assemblies brake cylinder 64. However, as thebrake shoes 62 on thebrake beam assemblies braking system 50, a thickness of therespective brake shoes 62 and a diameter of the respective wheels may be reduced. In order to accommodate these reductions, aslack adjuster 72 is provided. Theslack adjuster 72 is configured to shorten in length in order to compensate for the reduced thickness of thebrake shoes 62 and/or diameter of the wheels. - One having skill in the art will appreciate, however, that in other exemplary embodiments, the
braking system 50 may have any other suitable configuration of leading or trailingbrake assemblies brake beam assemblies brake system 50 may utilize any other suitable means for generating a braking force other than thebrake cylinder 64, and additionally, or alternatively, may utilize any other suitable configuration oflever assembly 66 to transfer such braking force to the leading and trailingbrake assemblies slack adjuster 72 may be positioned elsewhere in thebraking system 50, or may be configured in any other suitable manner to compensate for the reduction in the thickness of thebrake shoes 62 and/or the diameter of the various wheels. - Referring now to
FIG. 2 , aslack adjuster 100 in accordance with an exemplary embodiment of the present disclosure is depicted. Theexemplary slack adjuster 100 depicted inFIG. 2 may be configured in substantially the same manner as theslack adjuster 72 described above with reference to FIG.1, and accordingly may be utilized in a braking system such as theexemplary braking system 50 also described above with reference toFIG. 1 . - The
slack adjuster 100 depicted defines an axial direction A, a radial direction R, and a circumferential direction C, and extends generally along the axial direction A between afirst end 102 and asecond end 104. Theslack adjuster 100 includes afirst jaw 106 positioned at thefirst end 102 and asecond jaw 108 positioned at thesecond end 104. Arod assembly 110 is attached to thefirst jaw 106 and extends generally along the axial direction A. Additionally, atube 112 is attached to thesecond jaw 108 and also extends generally along the axial direction A. Thetube 112 encloses at least a portion of therod assembly 110. As will be discussed in greater detail below, a nut assembly 114 (seeFIG. 5 ) having at least a portion rotatably engaged with therod assembly 110 is configured to transfer a force between therod assembly 110 and thetube 112 and is also configured to allow therod assembly 110 to extend or retract relative to thetube 112. - Referring now also to
FIGS. 3 and 4 , theslack adjuster 100 additionally includes apawl box 116 attached to anouter surface 118 of thetube 112 over a pair ofpawl openings 120 in thetube 112. More particularly,FIG. 3 provides a close-up perspective view of theslack adjuster 100 ofFIG. 2 prior to attachment of thepawl box 116, andFIG. 4 provides a close-up perspective view of theslack adjuster 100 ofFIG. 2 after attachment of thepawl box 116. - As may be clearly seen in
FIG. 3 , thetube 112 defines a pair ofpawl openings 120 and at least onelocator opening 122 positioned adjacent to thepawl openings 120. More particularly, for the embodiment depicted, thetube 112 defines twolocator openings 122. Thepawl openings 120 are positioned adjacent to the nut assembly 114 of the slack adjuster 100 (seeFIG. 5 , below) and are each configured to receive a pawl that restricts or allows rotational movement of at least a portion of the nut assembly 114 relative to thetube 112. Moreover, thepawl box 116 includes amain slot 124 configured to hold the one or more pawls in thepawl openings 120 of thetube 112 when attached to thetube 112. Thepawl box 116 additionally includes atrigger slot 126. Thetrigger slot 126 is configured to receive a trigger that selectively engages or disengages one or both of the pawls to allow theslack adjuster 100 to extend or retract as necessary. - Moreover, the
pawl box 116 additionally includes at least onelocator tab 128 and at least twocoupling projections 130. More particularly, for the embodiment depicted, thepawl box 116 include twolocator tabs 128. When thepawl box 116 is attached to thetube 112, thelocator tabs 128 of thepawl box 116 extend into thelocator openings 122 in thetube 112. It should be appreciated, however, that in other exemplary embodiments, thetube 112 may define any other suitable number oflocator openings 122, and similarly thepawl box 116 may include any other suitable number oflocator tabs 128. Additionally, or alternatively, thetube 112 may not define anylocator openings 122, and instead the at least onelocator tab 128 may be configured to extend into one or more of thepawl openings 120. - Moreover, referring particularly to
FIG. 4 , for the embodiment depicted, thepawl box 116 is attached to thetube 112 by forming the at least twocoupling projections 130 of thepawl box 116 around theouter surface 118 of thetube 112. For example, thepawl box 116 may be attached to thetube 112 by placing thetube 112 in a circular die, and pressing thepawl box 116 onto thetube 112 such that thecoupling projections 130 are pressed/deformed by the circular die around theouter surface 118 of thetube 112 to hold thepawl box 116 in place. Such a configuration may allow for aslack adjuster 100 capable of more easily being assembled or manufactured. More particularly, with such a configuration thepawl box 116 need not be welded to the outer surface of thetube 112 of theslack adjuster 100, - Referring still to
FIG. 4 , and now also toFIG. 5 , the nut assembly 114 of theexemplary slack adjuster 100 ofFIG. 2 will now he described. As stated,FIG. 4 provides a close-up perspective view of a center portion of theslack adjuster 100 ofFIG. 2 . Additionally,FIG. 5 provides a side, cross-sectional view of the center portion of theslack adjuster 100 ofFIG. 2 . - As may be more clearly seen in
FIG. 5 , the nut assembly 114 generally includes anut 132 defining a threadedopening 134 rotatably engaged with a threaded portion 136 of therod assembly 110. More particularly, for the embodiment depicted, thenut 132 is threaded onto (or screwed onto) the threaded portion 136 of therod assembly 110. As will be understood, thenut 132 also includes a geared outer surface 138 configured to be engaged by the pair of pawls received in the pair ofpawl openings 120 of thetube 112. The not assembly 114 additionally includes afirst bearing collar 140 and asecond bearing collar 142. Thefirst bearing collar 140 is sometimes referred to as a cone collar, and thesecond bearing collar 142 is sometimes referred to simply as a bearing collar. The first andsecond bearing collars nut 132 along the axial direction A for constraining thenut 132 along the axial direction A of theslack adjuster 100 relative to thetube 112. - A
pair spring washers 144 are provided between thenut 132 and thefirst bearing collar 140 to bias thenut 132 away from thefirst bearing collar 140 along the axial direction A. For the embodiment depicted, thenut 132 includes abearing 146 between thenut 132 andspring washers 144 to allow for thenut 132 to more easily rotate relative to thespring washers 144 andfirst bearing collar 140. Additionally, thefirst bearing collar 140 includes a taperedcone surface 148 corresponding in shape with a tapered surface defined at an axial end 150 of thenut 132. When thenut 132 is pressed against the taperedcone surface 148 of the first bearing collar 140 (after having overcome the bias of the spring washers 144), thenut 132 may be fixed rotationally to thefirst hearing collar 140. Abearing 152 is also provided between thesecond bearing collar 142 at an oppositeaxial end 154 of thenut 132 to allow thenut 132 to more easily rotate relative to thesecond bearing collar 142. - The first and
second bearing collars tube 112. During operation of theslack adjuster 100, an axial force may be applied between the first andsecond jaws slack adjuster 100. The nut assembly 114 is configured to transfer such a force between the rod assembly 110 (which receives the force from and/or transfers the force to the first jaw 106) and thetube 112 assembly (which receives the force from and/or transfers the force to the second jaw 108). More particularly, for theexemplary slack adjuster 100 depicted, thefirst bearing collar 140 is configured to transfer such force between therod assembly 110 and thetube 112. However, in other embodiments, thesecond bearing collar 142 may additionally, or alternatively, be configured to transfer such force. Accordingly, the attachment between first and/orsecond bearing collars tube 112 must be capable of withstanding a potentially large amount of force applied between the first andsecond jaws slack adjuster 100 along the axial direction A. - The inventors in the present application have found that contrary to conventional wisdom, the nut assembly 114 may be attached to the
tube 112 by crimping, while still being capable of withstanding the potentially large amount of force along the axial direction A. Such an attachment method, the inventors found is enabled at least in part due to the selection of materials and design of the components, as discussed below. - For example, referring now also to
FIG. 6 , depicting a close-up, perspective view of thefirst bearing collar 140 of the nut assembly 114, thefirst bearing collar 140 defines agroove 156 in anouter surface 158 extending generally along the circumferential direction C. At least a portion of thetube 112 is crimped into thegroove 156 of thefirst hearing collar 140, rigidly attaching thetube 112 to thefirst bearing collar 140. Moreover, thefirst bearing collar 140 defines acenter opening 160 through which a portion therod assembly 110 extends (FIG. 5 ). The exemplaryfirst bearing collar 140 depicted is a solid component between thecenter opening 160 and thegroove 156 free from any openings or holes. - Additionally, for the embodiment depicted, the
first bearing collar 140 of the nut assembly 114 may be formed of a steel material having a tensile strength of at least about seventy-five (75) kilopounds per square inch (“ksi”) and a yield strength of at least about sixty (60) ksi. More particularly, thefirst bearing collar 140 may have a tensile strength of at least about eighty (80) ksi and a yield strength of at least about sixty-five (65) ksi, or may have a tensile strength of at least about eighty-five (85) ksi and a yield strength of at least about seventy (70) ksi. For example, thefirst hearing collar 140 may he formed of a Chinese No. 45 steel. Moreover, thetube 112 may also be formed of a steel material having a tensile strength of at least about seventy (70) ksi and a yield strength of at least about sixty (60) ksi. More particularly, thetube 112 may have a tensile strength of at least about seventy-five (75) ksi and a yield strength of at least about sixty-five (65) ksi, or may have a tensile strength of at least about eighty (80) ksi and a yield strength of at least about seventy (70) ksi. For example, thetube 112 may be formed of a 1026 carbon steel, conforming to the American Society for Testing and Materials (“ASTM”) A513 Type 5 Drawn Over Mandrel. - It should be appreciated, that as used herein, terms of approximation, such as “about” or “approximately,” refer to being within a ten percent (10%) margin of error.
- Notably, prior configurations have attached the
first bearing collar 140 to thetube 112 by having a plurality of holes extending along the radial direction R between thecenter opening 160 and theouter surface 158 of thefirst bearing collar 140 corresponding to similar openings in thetube 112. The holes in thefirst bearing collar 140 in prior configurations were threaded such that bolts may be used to attach thefirst bearing collar 140 to thetube 112. Such a configuration required each hole to he precisely drilled and tapped. Additionally, such a configuration required an increased thickness of thetube 112 andfirst bearing collar 140 such that thetube 112 andfirst bearing collar 140 could withstand the necessary forces along the axial direction A despite the holes drilled therethrough. By contrast, however, with the present configuration no such holes need to be drilled and/or threaded in order to attach thetube 112 andfirst bearing collar 140. Accordingly, the present configuration may provide for a much more efficient and less time-consuming process for manufacturing and attaching thefirst bearing collar 140 to thetube 112. Additionally, thetube 112 may define a lesser thickness, such that a weight of thetube 112 andslack adjuster 100 are decreased with the present configuration. - Similarly, referring still to
FIG. 5 and now also toFIG. 7 , depicting a close-up, perspective view of thesecond bearing collar 142 of the nut assembly 114, thesecond bearing collar 142 also defines agroove 162 in anouter surface 164 extending generally along the circumferential direction C. At least a portion of thetube 112 is crimped into thegroove 162 and thesecond bearing collar 142, attaching thetube 112 to thesecond bearing collar 142. Thesecond bearing collar 142 also defines acenter opening 166 through which a portion of therod assembly 110 extends. Thesecond bearing collar 142 is also a solid component between thecenter opening 166 and thegroove 162 defined in itsouter surface 164, free from any openings or holes, and may be formed of the same material as thefirst bearing collar 140 discussed above. Accordingly, the present configuration may also provide for a much more efficient and less time-consuming process for attaching thesecond bearing collar 142 to thetube 112 and for manufacturing theslack adjuster 100, as well as the other benefits discussed above. - Referring now to
FIGS. 8 and 9 , a perspective view and side cross-sectional view of thesecond end 104 of theslack adjuster 100 are provided. Similar to the first andsecond bearing collars second jaw 108 of theexemplary slack adjuster 100 depicted is attached to thetube 112 by crimping. More particularly, thesecond jaw 108 includes a substantially smoothcylindrical base 168 defining agroove 170 in anouter surface 172 extending generally along the circumferential direction C. At least a portion of thetube 112 is crimped into thegroove 170 in thebase 168 of thesecond jaw 108, attaching thetube 112 to thebase 168 of thesecond jaw 108. For the exemplary embodiment depicted, thegroove 170 in thebase 168 of thesecond jaw 108 also defines a width WG along the axial direction A and a depth DG along the radial direction R. In certain exemplary embodiments, the width WG of thegroove 170 in the base 168 thesecond jaw 108 may be at least about 0.40 inches wide, at least about 0.50 inches wide, or at least about 0.75 inches wide. Additionally, in certain exemplary embodiments, the depth DG of thegroove 170 in thebase 168 of thesecond jaw 108 may be at least about 0.10 inches deep, at least about 0.15 inches deep, or at least about 0.20 inches deep. - Moreover, as shown most clearly in
FIG. 9 , thesecond jaw 108 includes aflange 174 having a width WF along the axial direction A. For the embodiment depicted, theflange 174 has a width WF along the axial direction A of at least about 0.15 inches. Additionally, thesecond jaw 108 may be formed of a steel material having a tensile strength of at least about eighty (80) ksi and a yield strength of at least about seventy (70) ksi. More particularly, thesecond jaw 108 may have a tensile strength of at least eighty-five (85) ksi and a yield strength of at least about sixty-five (75) ksi, or may have a tensile strength of at least about ninety (90) ksi and a yield strength of at least about eighty (80) ksi. For example, thesecond jaw 108 may be formed of 1035 steel. - It should be appreciated, however, that the dimensions provided above are by way of example only, and that in other exemplary embodiments, the
flange 174 may have any other suitable width WF, thegroove 170 in thebase 168 of thesecond jaw 108 may have any other suitable width WG, and thegroove 170 in thebase 168 of thesecond jaw 108 may also have any other suitable depth DG. For example, in other exemplary embodiments, theflange 174 may be at least about 0.20 inches wide, at least about 0.25 inches wide, or at least about 0.30 inches wide. Additionally, or alternatively, in other exemplary embodiments, thegroove 170 in thebase 168 may be an overly wide groove, defining a width WG greater than or equal to about three inches, greater than or equal to about five inches, or greater than or equal to about seven inches. Further, in still other exemplary embodiments, thegroove 170 in thebase 168 may actually be a plurality of circumferential grooves spaced along thebase 168 of thesecond jaw 108. Such a configuration may provide additional strength to the connection between thesecond jaw 108 and thetube 112. - Notably, the inventors have unexpectedly found that the
slack adjuster 100 can withstand a relatively large force along the axial direction A with thefirst bearing collar 140 and thesecond jaw 108 attached to thetube 112 by crimping. More particularly, the inventors have unexpectedly found that aslack adjuster 100 in accordance with the following exemplary embodiment can withstand a relatively large force along the axial direction A with thefirst bearing collar 140 and thesecond jaw 108 attached to thetube 112 by crimping: (a) when thetube 112 is formed of a material having a tensile strength of at least about eighty (80) ksi and a yield strength of at least about seventy (70) ksi; (b) when thefirst bearing collar 140 is formed of a material having a tensile strength of at least about eighty-five (85) ksi and a yield strength of at least about seventy (70) ksi; (c) when thesecond jaw 108 is formed of a material having a tensile strength of at least about ninety (90) ksi and a yield strength of at least about eighty (80) ksi; (d) when thesecond jaw 108 includes aflange 174 having a width WF along the axial direction of at least about 0.15 inches; and (e) when thesecond jaw 108 defines agroove 170 in the base 168 having a width WG of at least about 0.50 inches and a depth DG of at least about 0.15 inches. With such an exemplary embodiment, the inventors have unexpectedly found that theexemplary slack adjuster 100 may be capable of withstanding at least about 60,000 pounds of force along the axial direction A. Such a configuration may therefore withstand the typical forces incurred during operation of a braking system, plus an additional safety factor. - Referring particularly to
FIG. 9 , thebase 168 of thesecond jaw 108 defines acentral opening 176 extending generally along the axial direction A through at least a portion of thebase 168 of thesecond jaw 108. Thebase 168 of thesecond jaw 108 is a solid component between thecentral opening 176 and thegroove 170, free from any openings or holes. It should be appreciated, however, that in other exemplary embodiments, thebase 168 may not include anopening 176. Accordingly, the present configuration may also provide for a much more efficient and less time-consuming process for attaching thebase 168 of thesecond jaw 108 to thetube 112 and for manufacturing theslack adjuster 100, as well as the other benefits discussed above. - Referring now to
FIG. 10 , a close-up view is provided of agroove 178 defined in anouter surface 180 of acomponent 182 and a crimp die 184. The crimp die 184 is configured to move generally along the radial direction R and press/deform a portion of the tube 112 (original shape oftube 112 shown as numeral 112′ in phantom) into thegroove 178 defined in theouter surface 180 of thecomponent 182. The crimp die 184 defines a width WCD along the axial direction A. The width WCD of the crimp die 184 is chosen such that once the portion of thetube 112 is pressed/deformed into thegroove 178 defined in theouter surface 180 thecomponent 182, such portion of thetube 112 conforms to the shape of thegroove 178. For example, the width WCD of the crimp die 184 may be approximately equal to a width WG, of thegroove 178 minus twice a thickness TT of thetube 112. Such a configuration may provide an attachment point capable of withstanding the axial forces required by theslack adjuster 100. - The exemplary groove depicted defines a pair of
inner edges 186 and a pair of top ledges 188 (along the axial direction A). Additionally, the crimp die 184 defines a crimpingportion 190 defining a pair of crimpingedges 192. For the exemplary embodiment depicted, each of theinner edges 186, thetop ledges 188, and the crimpingedges 192 define a radius, or a radius of curvature RC, greater than zero. More particularly, for the embodiment depicted, each of theinner edges 186, thetop ledges 188, and the crimpingedges 192 define a radius RC greater than or equal to about ⅛th of an inch (0.125 inches). However, in other exemplary embodiments, one or more of theinner edges 186, thetop ledges 188, and the crimpingedges 192 may define a radius RC greater than or equal to about 1/10th of an inch (0.10 inches), greater than or equal to about ⅙th of an inch (0.16 inches), or greater than or equal to about ¼th of an inch (0.25 inches). Moreover, it should be appreciated, that in still other exemplary embodiments, one or more of theinner edges 186, thetop ledges 188, and the crimpingedges 192 may define any other suitable radius RC, or may define a radius RC equal to zero (i.e., a ninety degree edge). As used herein, the term “radius” or “radius of curvature” and is the radius of the circle that touches a curve at a given point and has the same tangent and curvature at that point. - Furthermore, it should be appreciated, that the
exemplary groove 178 defined in theouter surface 180 of thecomponent 182 depicted inFIG. 10 may represent one or more of thegroove 156 defined in theouter surface 158 of thefirst bearing collar 140, thegroove 162 defined in theouter surface 164 of thesecond bearing collar 142, and/or thegroove 170 defined in theouter surface 172 of thebase 168 of thesecond jaw 108. Further, in certain exemplary embodiments, one or more other portions of theexemplary slack adjuster 100 may be attached using a similar crimping method. For example, referring back briefly toFIG. 2 , theexemplary slack adjuster 100 additionally includes an end cap 194 defining agroove 196 extending generally along the circumferential direction C in an outer surface with at least a portion of thetube 112 crimped therein, attaching thetube 112 to the end cap 194. As will be appreciated, at least a portion of therod assembly 110 slidably extends through an opening in the end cap 194 (not shown), and the end cap 194 does not support an axial force applied between the first andsecond jaws - Referring now to
FIG. 11 , a flow diagram is provided of an exemplary method (200) for manufacturing a slack adjuster for railroad car braking system in accordance with an exemplary aspect of the present disclosure. In certain exemplary aspects, the exemplary method (200) may be used to manufacture the exemplary slack adjuster depicted inFIG. 2 and described above. - As indicated, the exemplary method (200) generally includes at (202) attaching a first jaw to a rod assembly and at (204) positioning a nut assembly over a threaded portion of the rod assembly. Moreover, the exemplary method (200) includes at (206) attaching the nut assembly to a tube extending generally along the axial direction, such that at least a portion of the nut assembly is fixed along the axial direction relative to the tube. Although not depicted, in certain exemplary aspects, attaching the nut assembly to the tube at (206) may include crimping a portion of the tube into a groove defined in an outer surface of a first bearing collar and/or crimping a portion of the tube into a groove defined in an outer surface of a second bearing collar.
- Referring still to
FIG. 11 , the exemplary method (200) includes at (208) attaching the tube to a base of a second jaw by crimping a portion of the tube into a groove defined in the base of the second jaw, fixing the base of the second jaw to the tube. In certain exemplary aspects, attaching the tube to a base of the second jaw by crimping a portion of the tube into the groove defined in the base of the second jaw at (208) includes crimping a portion of the tube into the groove defined in the base of the second jaw using a plurality of crimp dies. Each of the plurality of crimp dies includes a crimping portion, and in certain exemplary aspects, each of the crimping portions may define a crimping edge having a radius of at least about ⅛th of an inch. However, in other exemplary aspects, the crimping edges of the crimping portions may define any other suitable radius, or no radius at all. - Moreover, for the exemplary method (200) depicted in
FIG. 11 , the method (200) further includes attaching a pawl box to the tube at (210). Attaching the pawl box to the tube at (210) may include positioning the pawl box over a pair of pawl openings defined in the tube such that at least one locator tab of the pawl box extends into at least one locator opening defined in the tube. Additionally, attaching the pawl box to the tube at (210) may also include forming a pair of coupling projections around an outer surface of the tube. - As is also depicted, for the exemplary method (200) depicted in
FIG. 11 , the exemplary method (200) also includes reconditioning the slack adjuster at (212). Reconditioning the slack adjuster at (212) may take place, e.g., after extended use of the slack adjuster wherein repairs may be necessary. For example, reconditioning the slack adjuster at (212) may take place after ten years or more of use of the slack adjuster. Alternatively, reconditioning the slack adjuster at (212) may take place during an initial manufacturing of the slack adjuster in order to readjust or correct a mistake made during such manufacturing process. Regardless, reconditioning the slack adjuster at (212) may include removing the second jaw from the tube by shearing off the portion of the tube crimped into the groove in the base of the second jaw with a plurality of crimp dies. Moreover, in other exemplary aspects, reconditioning the slack adjuster at (212) may additionally or alternatively include removing one or more portions of the nut assembly by shearing off the portion of the tube crimped into the groove in the first bearing collar and/or the portion of the tube crimped into the groove in the second bearing collar. The crimp dies used for shearing off such portions of the tube may define a width along the axial direction of the slack adjuster approximately equal to or slightly less than a width of the respective groove. However, in other exemplary aspects, reconditioning the slack adjuster at (212) may alternatively include removing the portion of the tube crimped into the groove in the base of the second jaw and/or a groove in one or more portions of the nut assembly by using a tube cutter, machining such portion off, or using any other suitable method. - This written description uses examples to disclose the invention, including the best mode, and also to enable any person skilled in the art to practice the invention, including making and using any devices or systems and performing any incorporated methods. The patentable scope of the invention is defined by the claims, and may include other examples that occur to those skilled in the art. For example, in other embodiments, elements of the exemplary methods described herein may be performed in any suitable order. Such other examples are intended to be within the scope of the claims if they include structural elements that do not differ from the literal language of the claims, or if they include equivalent structural elements with insubstantial differences from the literal language of the claims.
Claims (20)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/793,768 US20170008539A1 (en) | 2015-07-08 | 2015-07-08 | Slack adjuster for railcar brake |
PCT/US2016/039995 WO2017007652A1 (en) | 2015-07-08 | 2016-06-29 | Slack adjuster for a railroad car braking system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US14/793,768 US20170008539A1 (en) | 2015-07-08 | 2015-07-08 | Slack adjuster for railcar brake |
Publications (1)
Publication Number | Publication Date |
---|---|
US20170008539A1 true US20170008539A1 (en) | 2017-01-12 |
Family
ID=57685707
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US14/793,768 Abandoned US20170008539A1 (en) | 2015-07-08 | 2015-07-08 | Slack adjuster for railcar brake |
Country Status (2)
Country | Link |
---|---|
US (1) | US20170008539A1 (en) |
WO (1) | WO2017007652A1 (en) |
Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB354810A (en) * | 1929-06-24 | 1931-08-10 | Bromsregulator Svenska Ab | Improvements in automatic slack adjusters for brakes on railway cars and the like |
US2774449A (en) * | 1955-01-07 | 1956-12-18 | Bromsregulator Svenska Ab | Double-acting type slack adjuster for brakes |
US3326335A (en) * | 1965-06-16 | 1967-06-20 | Sloan Valve Co | Double acting slack adjuster |
US3404759A (en) * | 1967-01-19 | 1968-10-08 | Universal Railway Devices Co | Two way automatic slack adjuster |
US3516696A (en) * | 1968-08-21 | 1970-06-23 | Amsted Ind Inc | Slack adjuster |
US3668224A (en) * | 1970-07-02 | 1972-06-06 | Theodor Petrzilka | PROCESS OF PRODUCING 6a, 10a-TRANS-6a,7,8,10a-TETRAHYDRODIBENZO (b,d)-PYRANS |
US3900086A (en) * | 1974-11-04 | 1975-08-19 | Sloan Valve Co | Automatic double-acting slack adjuster |
US4593797A (en) * | 1984-07-16 | 1986-06-10 | Sloan Valve Company | Compression type railroad brake slack adjuster |
US4657230A (en) * | 1980-04-21 | 1987-04-14 | American Standard Inc. | Overtravel spring assembly for slack adjuster |
US4825980A (en) * | 1984-02-13 | 1989-05-02 | Sloan Valve Company | Railroad brake slack adjusters |
US20090065312A1 (en) * | 2007-09-06 | 2009-03-12 | Howard Sommerfeld | Slack adjuster for railway vehicle brake rigging |
US20160075353A1 (en) * | 2014-09-17 | 2016-03-17 | New York Air Brake, LLC | Slack Adjuster Having A One Piece Housing |
US20160229430A1 (en) * | 2015-02-06 | 2016-08-11 | Westinghouse Air Brake Technologies Corporation | "Vented Draining Slack Adjuster End Cap" |
Family Cites Families (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB368594A (en) * | 1931-03-21 | 1932-03-10 | Procedes Dabeg Soc D Expl Des | Improvements in adjusting devices for the brakes of railway vehicles |
US9272718B2 (en) * | 2013-02-13 | 2016-03-01 | New York Air Brake, LLC | Slack adjuster environmental improvements |
AU2014284572B2 (en) * | 2013-07-01 | 2017-11-23 | Wabtec Holding Corp. | Slack adjuster contaminant mitigation device |
-
2015
- 2015-07-08 US US14/793,768 patent/US20170008539A1/en not_active Abandoned
-
2016
- 2016-06-29 WO PCT/US2016/039995 patent/WO2017007652A1/en active Application Filing
Patent Citations (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB354810A (en) * | 1929-06-24 | 1931-08-10 | Bromsregulator Svenska Ab | Improvements in automatic slack adjusters for brakes on railway cars and the like |
US2774449A (en) * | 1955-01-07 | 1956-12-18 | Bromsregulator Svenska Ab | Double-acting type slack adjuster for brakes |
US3326335A (en) * | 1965-06-16 | 1967-06-20 | Sloan Valve Co | Double acting slack adjuster |
US3404759A (en) * | 1967-01-19 | 1968-10-08 | Universal Railway Devices Co | Two way automatic slack adjuster |
US3516696A (en) * | 1968-08-21 | 1970-06-23 | Amsted Ind Inc | Slack adjuster |
US3668224A (en) * | 1970-07-02 | 1972-06-06 | Theodor Petrzilka | PROCESS OF PRODUCING 6a, 10a-TRANS-6a,7,8,10a-TETRAHYDRODIBENZO (b,d)-PYRANS |
US3900086A (en) * | 1974-11-04 | 1975-08-19 | Sloan Valve Co | Automatic double-acting slack adjuster |
US4657230A (en) * | 1980-04-21 | 1987-04-14 | American Standard Inc. | Overtravel spring assembly for slack adjuster |
US4825980A (en) * | 1984-02-13 | 1989-05-02 | Sloan Valve Company | Railroad brake slack adjusters |
US4593797A (en) * | 1984-07-16 | 1986-06-10 | Sloan Valve Company | Compression type railroad brake slack adjuster |
US20090065312A1 (en) * | 2007-09-06 | 2009-03-12 | Howard Sommerfeld | Slack adjuster for railway vehicle brake rigging |
US20160075353A1 (en) * | 2014-09-17 | 2016-03-17 | New York Air Brake, LLC | Slack Adjuster Having A One Piece Housing |
US20160229430A1 (en) * | 2015-02-06 | 2016-08-11 | Westinghouse Air Brake Technologies Corporation | "Vented Draining Slack Adjuster End Cap" |
Also Published As
Publication number | Publication date |
---|---|
WO2017007652A1 (en) | 2017-01-12 |
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