Title of Invention

AN IMPROVED RAILCAR CONNECTOR ASSEMBLY

Abstract

When slack-free railcar connector assemblies are placed under very high tensile loading, the connector assembly components will stretch and allow a typical "rigid" gravity wedge to descend into a fully seated position between the components and lock-in the tensile loads. The locked-in loads become additive in nature when successively encountered compressive loads are expenenced by the connector assembly, thereby increasing the lateral drawbar anglmg forces as wellas accelerating coupling component wear. The wedge component ot the present invention includes a means for vertically supporting and retaining the wedge in a holding position slightly above the normally fully seated position during the tensile loading, thereby eliminating the build up of tensile forces in the connector assembly. PRICE: THIRTY RUPEES

Full Text

The present invention generally relates to railcar connector assemblies, and more particularly to an improved arrangement for a slackless railcar connector assembly in which the gravity wedge is prevented from fully seating during very high tensile buff loading on the connector. Prevention of the wedge from fully seating will eliminate the wedge from storing the tensile forces within the assembly, which said stored forces act as additive forces to later experienced compressive loads acting on the connector assembly. 2. Railway cars are connected together generally by connector assemblies, namely articulated connectors, drawbars, or E or F type couplers. Two mating ends of a coupler on two successive railcars are joined together, while the respective opposite ends of the coupler extend into the center sill on each respective railcar, wherein they are each secured by a pin or key means for transmitting longitudinal loads into the railcar center sill. One type of slackless connector assembly which feamres a drawbar positioned and held within a center sill is shown in U.S. Pat. No.S, 115,926 to Kaufhold, wherein a "rigid" gravity-actuated wedge is used to maintain a slack-free connection within the connector assembly. When component wear occurs on the various elements comprising the connector assembly system, increased longitudinal clearances develop between the follower block and pocket casting, and this clearance or slack is constantly being taken-up by the action of the dropping rigid wedge. Recent laboratory tests have indicated that stretching in die car body structure and/or the surrounding connector components due to heavy draft tension loads will also create a temporary space or slack between the follower block and the pocket casting, into which the rigid wedge will drop. When the high tension loads are released, most of die loads will be stored within the connector assembly due to the rigid wedge dropping, and then locking the components in place. A subsequent buff load (compressive type load) will be additive to the forces already locked into the assembly, thereby imparting unanticipated longitudinal loads at the follower block and connector end interface. These additional and unanticipated loads will induce higher lateral drawbar angling forces, as well as accelerated component wear. SUMMARY OF THE INVENTION Accordingly, it is a principal object of the present invention to provide an improved slackless railcar connector assembly that will prevent tensile loads from being stored within the connector assembly after die railcar has been placed under a heavy draft or tensile load. Another object of the present invention is to provide an imroved slackless railcar connector assembly which will eliminate tensile pre-loading, and be capable of receiving die full buff load experienced by die train, yet still adjust to die increased clearances created when the system wears. Yet another object of the present invention is to provide an improved gravity wedge which has a resilient means for supporting or holding the wedge in a vertical direction during tensile loads so that the wedge will not drop into a fully seated position during the period of die applied tensile loading. Basically, the present invention includes a 'floatable' wedge which has a resilient means attached thereon and which protrudes slightly beyond one or both faces of the wedge so that a small, but controlled gap symmetrically remains between the wedge face(s) and the adjacent surface(s). When railcar tensile loads are released, the only locked-in-force operating on the connector assembly will be that dictated by the compressive load rate of the resilient means. The resilient means has a load rate large enough to maintain the controlled gap even after the tensile load has been released. The improved wedge will operate in buff exactly like prior art "rigid" wedges and when the buff or compressive load has been released, the wedge will maintain its vertical position as the resilient means "feeds out" and holds the wedge in place, until the next-experienced tensile loading. Accordingly the present invention provides an improved railcar connector assembly having a longitudinal axis and undergoing tensile and compressive loading along said axis, said connector assembly comprising a pocket casting having an end wall and an open pocket forward of said end wall, a coupler member, a wedge having a front wall, a back wall, a top end and a bottom end, and a follower block with a front surfrice and a rear surfrice, said follower block and said wedge received in said pocket such that said follower block Is spaced from said pocket end wall by said wedge, said follower block from surface in contact with said coupler member and said follower block rear surface in contact with said wedge front wall, said wedge back wall contacting said pocket casting end wall, said wedge having a first fully seated position and a second fully seated position, said first fully seated position defining a first wedge location relative to said follower block and said pocket casting end wall wherein said wedge is longitudinally aligned with and in simultaneous contact with said follower block and pocket casting end wall as said connector assembly undergoing tensile loading, said second fully seated position defining a second wedge location relative to said follower block and said pocket casting end wall wherein said wedge is longitudinally aligned with and in simultaneous contact with said follower block and said pocket casting end wall as said connector assembly undergoes compressive loading, wherein the improvement comprising : means attached to said wedge for vertically supporting said wedge at a holding position during tensile loading in order to eliminate a build-up of forces which otherwise occurs within said connector assembly if said wedge is allowed to drop into said first fully seated position during tensile loading, said holding position located above said first fully seated position. Further objects and advantages of the present invention will become apparent upon reading the following detailed description in conjunction with the accompanying drawings wherein : Figure 1 is a top view of a prior art slack-less connector assembly; Figure 2 is a partial cross-sectional side view of the assembly of Figure 1; Figure 3 is a cross-sectional side view of the connector assembly of the present invention with supporting means attached to the gravity wedge; Figure 4 is a front view of a gravity wedge of the present invention; Figure 4A is a more detailed side view of the present invention shown in Figure 3; Figure 5 is a front view of a gravity wedge incorporating multiple supporting means; Figure 6 is a side view of an elastomeric spring used as the preferred supporting means of the present invention; Figure 7 is a cross sectional view of the present invention with the supporting means comprising a spring-loaded plunger assembly featuring stacked, belleville washers; Figure 7a Is a detailed view of the plunger assembly of Fig. 7 using a helical spring. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Referring ow to Figures 1 and 2, railcar connector assemblies 10 are usually anchored within and project outwardly from a railcar center sill, generally shown at 12. in order to couple ends of a railcar together. While there are several types of connectors applicable to the present invention, such as articulated connectors, E and F type couplers, and drawban (including rotary drawbars), the illustrated preferred embodiment of the present invention will be described using a drawbar. In Figure 1, it is to be understood diat the longimdinal axis "L" of the center sill 12, which is secured beneath the railcar, coincides widi a longimdinal axis of the railcar. The center sill 12 is of standard construction comprising an inverted U-shaped channel member having a top wall 11, sidewalls 14 and 16, and out-turned flanges 18 and 20 at the lower, open bottom 22 of the inverted U-shaped sill. A drawbar illustrated at 5 has a bun end IS with an outer convex surface 17, an inner concave surface 19. and an opening or pin hole 25 extending through and normal to the longitudinal axis of the center sill for receiving a connecting pin 200. Opening 25 is formed by a continuously curved concave inner surface 26. Pin 200 is an elongate, vertically disposed bar which indirectly couples the drawbar to the center sill, having a cylindrical edge surface 206 in mated engagement with cylindrical surface 107 of opening 105 in short yoke casting 100. The short yoke casting 100 is held within the sill 12 by channel member 220 and rests against center sill front stops 240. A pin bearing block 90 has a concave cylindrical front surface 91 that abuts rear convex edge surface 206 on pin 200, as well as an outward convex back surface 92 abatting inner concave surface 19 on drawbar butt end 15. Pocket casting 40 fits within the car center sill 12 at a predetermined longitudinal spacing from the back wall 110 of unitary short yoke casting 100 and is held within the sill by support bracket 230. Pocket casting 40 has a generally flat, but sloped interior rear wall 42, a bottom interior surface 44 and an exterior rear wall surface 48 which abuts the front face 151 of either a spacer block 150 or the rear stops 250 of the center sill. A follower block 50 is located within pocket casting 40 and has a concave front surface 51 that abuts outer convex curved surface 17 of drawbar butt end 15. The follower block 50 also has a rear surface 52 in contact with gravity wedge 70 and a bottom surface 57 resting on bottom surface 44 of pocket casting 40 to keep concave front surface 51 symmetrical with pin hole 25 of drawbar 5. Gravity wedge 70 has a generally flat front wall 71 that abuts generally flat rear surface 52 of follower block 50 and also has a generally flat back wall 73 that abuts with interior wall 42 of pocket casting 40. The center sill sidewalls 14, 16. are provided with access slots (not shown) which allow the wedge 70 to be held up for installation purposes. Rear outside wall surface 48 of pocket casting 40 bears against the front face 151 of spacer 150 or center sill rear stops 250 if a spacer block is not used. Spacer block member 150 is a fabricated rectangular housing which includes a rigid frame that is capable of withstanding the impact loads imparted vipon the center sill. Spacer block 150 consists of two substantial vertical plates 152,154 equal in length and held in a spaced, parallel relationship from each other by cross plate members 153 and 155. Vertical plate members 152, 154 project upwardly from the open bottom 22 of center sill 12 to abut inside surface 9 of center sill top wall 11. Cross plate memben 153, 155 are not of substantial strength and axe vertically centered between the height of spacer block member 150. Spacer block 150 typically replaces the yoke and draft member (not shown) which are commonly used wbten a standard coupler arrangement is connected within the center sill. If a spacer member is not used, the pocket casting 40 is typically cast as one long member such that die pocket casting in effect, contains a built-in spacer block so that the pocket casting rear wall surface 48 abuts die 1 center sill rear stops 250. Due to dimensional irregularities in cast members, it is more typical to use a standard pocket casting member 40 along with a fabricated spacer member 150. Operationally, when the connector assembly 10 experiences a compressive or buff load, drawbar 5 will be pushed along the longitudinal axis towards rear stops 250. Short yoke 100, being pinned to butt end 15, will move backwards in the same direction, but only by the minute distance which cumulatively represents the amount of free slack between the remaining connector assembly components. As seen from viewing Figure 2, butt end 15 pushes follower block 50 directly against rigid gravity wedge 70, wherein the forces are then transferred from die wedge into the pocket casting 40. Since pocket casting 40 is indirectly abutting rear stops 250, the compressive forces will be transferred directly into the spacer block, and then into the rear stops, before eventually being transferred into each of the center sill sidewalls 14,16. Likewise, when a tensile or draft load is experienced by the connector assembly, drawbar 5 will be pulled Lu a longitudinal direction such that bun end 15 will move toward front stops 240. Since the drawbar is connected to pin 200 and therefore, short yoke 100, forces will be transmitted fcom the drawbar, into the short yoke, and then into front stops 240, where they are eventually distributed into the center sill sidewalls 14,16. Upon pulling movement of the drawbar butt end 15, it is appreciated diat a small gap will appear between the butt end 15 and follower block 50, causing rigid gravity wedge 70 to descend into pocket casting 40, thereby removing the slack or grap created between the butt end 15 and follower block 50. Under very heavy tensile loading, it can be appreciated from the above operational description that wedge 70 will downwardly descend and remove the artificially created free slack which occurs in the connector assembly when the components are stretched by the pulling action. According to tbe present invention shown in Figures 3-6, a "floating" gravity wedge 70 is incorporated into the connector assembly 10 wherein the wedge is provided with an attached set of supporting means 60 for vertically supporting and holding the wedge in a position slightly above a fully seated position when the connector assembly is under tensile or draft loads. It should be made clear that all connector assembly components of the present invention will be referenced using the same numerals as the prior art system, including the gravity wedge. As previously described, a prior art "rigid" wedge 70 will have a natural teiKlency to drop by gravity within the pocket casting 40 when the drawbar butt end 15 is pulled along the longitudinal axis during tensile, draft loading. As described, the connector assembly components will separate or stretch, allowing the wedge to fall into die slack or space created upon stretching. This dropped position is considered a first seated position. While in the first seated position, the weight of the wedge will cause front wall 71 and back wall 73 to respectively push against surfaces 52 and 42 and take-\sp the available free slack ' between the connector components. However, removing the free slack while the railcar is being pulled ana under tensile loading is not desirable because a rigid gravity wedge will remain in this first seated position and "lock-in" most of the tensile loads applied to the connector dirough the seating action. The locked-in forces are additive in nature to compressive loads that are later experienced when the train is being pushed and under compressive loading. Detrimentally, the additive forces accelerate component wear and create higher lateral drawbar angling forces which may contribute to wheel lift. The present invention on the other hand, prevents the wedge from falling into the first seated position during tensile loading because die supporting means 60 which is provided in the front and back walls 71 and 73 of the wedge, symmetrically maintain the wedge in a holding position slightly above the first fully seated position. As the Figures 3-6 show, the 1 means 60 is resilient and protrudes slightly beyond the walls 71,73 of the wedge so that a small amount of controlled gap, herein designated as "X", remains between the wedge walls and the adjacent surfaces. In this case, the adjacent surfaces will be the follower block rear surface wall 52, and the pocket casting rear sloped wall 42 and it is preferable that the controlled gap "X" be about 0.125 inches. Figure 3 shows that the wedge can be provided with a single supporting means on each of the front and back walls, or it can comprise multiple supporting means on both walls. For example. Figures 4 and 5 show that the multiple supporting means could consist of two horizontally or two vertically aligned and spaced means, or it can consist of more complicated multiple sets of means like that of Figure 5, where the wedge is shown as having four supporting means 60 on each front and back wall 71,73. The actual size, location, aixl the number of supporting means used for supporting wedge 70 is not crucial to the operation of the invention as long as the supporting means has the capability to keep the wedge frx}m fully seating and relatively square within the pocket casting during tensile loading, tt is envisioned that the supporting means 60 of the preferred embodiment be comprised of an elastomeric material having spring-like characteristics. For example. Figure 4A shows wedge 70 incorporating an elastomeric spring means 62 operably functioning as each supporting means 60, wherein each elastomeric means 62 is received into a blind bore 85, which is foimed on each wall of wedge 70. The bores 85 can either be cast as part of the wedge or later machined into it Each blind bore has a bore inlet 86, bore sidewalls 88, and a bore base 87. The depth of each bore is interrelated to the compression characteristics of the chosen supporting means 60, which in this case, is a function of the compressibility of the elastomeric supporting spring 62. This is best understood by referring to Figures 4A and 6, where "D" is the diameter of bore 85 if a round hole is used, and "H" is the bore depth. with the compressed state of the elastomeic means 62 of Figure 6 being a function of the bore volume "V", described by the formula V=3.141(D/2)2H. As Figure 6 illustrates, the elastomeric supporting means 62 has a compressed height equal to the depth "H" of blind bore 83, and an uncompressed height of Ho, where the distance determined by H-Ho should be equal to X", or the amount of the desired controlled gap, which is preferably 0.125 inches. It should be understood that the shape of elastomeric supporting spring means 62 is more a function of the bote volume "V", meaning that elastomeric supporting means 62 does not have to be limited to strictly cylindrically-shaped forms. Figure 6 illustrates this point where spring means 62 is shown having a base diameter of "Dz", which is equal to bore diameter "D", and an upper diameter of "D1", which is less than the diameter of "D2" to the extent that when the elastomeric spring means 62 is fully compressed from height "HO" to height "H", the bore hole volume "V" will almost be completely filled by the elastomeric material bulging or expanding during compression. Besides the unlimited profile choices available, it is also envisioned diat die elastomeric supporting means 62 can be secured within blind bore 85 through a number of different ways. For example, means 62 could be secured to base 87 by bonding, or it could be "press" fitted into the bore 85 with the body of spring means 62 bemg tighUy secured between sidewalls 88, or it even could be secured by using a peg on the base of die supporting means which engages a uncompressed hole formed within bore base 87. In any event, once elastomeric supporting spring 62 is so attached, it will extend outwardly beyond each wedge wall 71,73 in its uncompressed state by the desired controlled gap "X* and be at least partially complementary in shape to that of blind bore 85. The supporting means of the present invention must also exhibit characteristics which allow die wedge to fully widistaad buff and shear loading experienced by the supporting means and yet still have the capability of adjusting to the increased clearances (slack) created within the connector assembly as the system wears. Therefore, it is preferable that the elastomeric supporting means be comprised of material exhibiting a compressive load rate between about 100,000 and 200,000 pounds per inch for installed pieces loaded in parallel. With these rates, it is preferable that a minimum of two supporting means 62 and a maximum of four means per side of wedge 70 be provided in order to prevent cocking or misalignment of the wedge through added stability. It is also desirable that the lateral shear rate of the elastomeric material be relatively high, say between about 75,000 and 150,000 pounds per inch in order to prevent significant shear deformation when protruding beyond the wedge face by the amount of the controlled gap "X". It is also desirable that the material exhibit a value of about 40 to 60 in durometer when using the Shore D scale at a temperamre of 70" F. This necessarily means that the elastomeric material must also be sufficiently resilient at -40" F in order to follow a compression and release deformation through about 15% of its free or uncompressed height "H*. at a cycling rate of about 5 hertz. It is also preferable that the chosen elastomeric material have a coefficient of friction between about .3 and .5 as between the elastomeric material and the adjacent cast steel surfaces. With these characteristics, each elastomeric ^ring will fiiUy compress and not extend beyond wedge walls 71,73 at low "magnitute loads, say as low as 20,000 pounds, or at high loads, say as high as 40,000 pounds. Under the fully compressed condition, the wedge 70 will operationally be equivalent to a "rigid' wedge device wherein the wedge can again resume a fully seated position. However, is to be understood that this second fully seated position is equivalent to the first fully sealed position, except that the wedge and connector assembly component are now under compressive buff loading where the entire loading experienced by the follower block 50 will be transferred into the wedge, and then finally into the pocket casting 40. Under buff loading, the elastomeric material comprising the supporting means must also have characteristics which make the wedge capable of withstanding high compressive loads without settling of the material once the load is released. Settling is a condition where the elastomeric spring will lose the ability to fully retum to its original free¬standing position, in this case "Hg", after undergoing several tensile and compressive cycles. This means that when a buff load is released, the resilient supporting means should have the capability to "feed out" to the original holding position such that wedge 70 is again retained in a vertical position slightly above the first fully seated position. The wedge will remain in this first seated position until the connector assembly again experiences its next buff or compressive load, thereby eliminating the possibility of the wedge dropping into the first seated position and storing tensile forces within the connector assembly. Figure 7 and 7A shows a second embodiment of the present invention, wherein the supporting means 60 is comprised of a spring-loaded device or plunger assembly 170 instead of the resilient elastomeric supporting means. As the two figures show, the spring-loaded plunger supporting means 170 is comprised of a steel spring 173, either in the form of stacked Belleville washers, or as a single helical coil steel spring, a phmger keep 186 having a centrally located orifice 189, and a plunger 180 that is in intimate contact with steel spring 17S. For the sake of discussing this particular embodiment, reference to "steel" spring should be understood to encompass either type of spring shown in Figure 7 or Figure 7A. In either case, actioo of the steel spring causes plunger tip 184 to project duraugh orifice 189 for supporting contact with either rear follower block surface S2 or sloped interior wall 42 of pocket casting 40, depending upon which side of wedge 70 each spring-loaded phmger assembly is positioned. The phinger keep 186 has a generally geometric shape which is complementary to the geometric shape of each of the blind bores 85 and inchides a peripohery 187'having matcbed threads 188 to those threads 88A machined into the sidewalls 88 of blind bores 85. It should be understood that threads 88A are to be provided only at the bore inlet area 86, and are not to extend completely to bore base 87. Plunger keep 186 functions as a means for holding spring assembly 170 within bores 85 when the keep is threaded into each of the bore inlets 86. Figure 7 illustrates that each bore base 87 will support the steel spring 175, with the spring extending upwardly towards bore inlet 86 until it contacts bottom surface 185 of plunger keep 186. The steel spring 175 is sized such that there is very little tolera^e_betwMn the bore sidewalls 88 and the spring, thereby avoiding the need to permanently secure and prevent the spring from moving within the bore. It is also envisioned that with eidier type of steel spring, more than one spring will be required in order to maintain wedge 70 in the holding position. As Figure 7 shows, several Belleville washers have been stacked within bore 85 as a means of achieving a high enough spring rate for holding the wedge. Alternative mediods could include adding several bore and plunger assemblies to each wall of the wedge; this method would be especially well suited for the helical coil situation. Plunger "tip 184 has a peripheral shoulder 182 that is upwardly projected into abutting contact with plunger keep bottom surface 185 through the action of spring 175. As plunger keep 186 is threaded downwardly into bore 85, bottom surface 185 will contact and push shoulder 182 downward onto spring 175, thereby compressing the spring and causing plunger tip 184 to lower itself through orifice 189 and retract further mto die blind bore 85. In this way, the controlled gap "X' between wedge 70 and the follower and pocket casting surfaces 52,42, respectively, can be adjusted by threading plunger keep 186 either inwardly or outwardly within blind bore 85. Phunger tip 184 is preferably comprised of a solid piece of elastomeric material having a dimensional size and complementary shape to orifice 189 at its upper portion, while the shoulder 182 is slighty smaller in dimensional size to bore 85. Like the elastomeric supporting means of the preferred embodiment, the elastomeric plunger tip 184 of this embodiment will fully compress within bore 85 whenever a compressive or buff load is experienced, and when that load is released, each plunger tip 184 will support and maintain wedge 70 in the holding position by action of spring 175 pushing plunger 180 outward of bore 85. It is also preferable that phanger tip 184 exhibit the same compression and shear loading strengths, as well as the same durometer and coefficient of friction properties of the elastomeric material of the preferred embodiment. When using either of the supporting means embodiments just disclosed, the lateral drawbar angling forces on the connecting assembly will be greatly reduced. This will aid in protecting the connecting assembly components from pre-mamre wear, thereby increasing their operational lives. The foregoing details have been provided to describe the best mode of the invention and further variations and modifications may be made without departing from the spirit and scope of the invention, which is defined in the following claims. WE CLAIM : 1. All improved railcar connector assembly having a longitudinal axis and undergoing tensile and compressive loading along said axis, said connector assembly comprising a pocket casting having an end wall and an open pocket forward of said end wall, a coupler member, a wedge having a front wall, a back wall, a top end and a bottom end, and a follower block with a front surface and a rear surface, said follower block and said wedge received in said pocket such that said follower block is spaced from said pocket end wall by said wedge, said follower block from surface in contact with said coupler member and said follower block rear surface in contact with said wedge front wall, said wedge back wall contacting said pocket casting end wall, said wedge having a first full seated position and a second fully seated position, said first fully seated position defining a first wedge location relative to said follower block and said pocket casting end wall wherein said wedge is longitudinally aligned with and in simultaneous contact with said follower block and pocket casting end wall as said connector assembly undergoing tensile loading, said second fully seated position defining a second wedge location relative to said follower block and said pocket casting end wall wherein said wedge is longitudinally aligned with and in simultaneous contact with said follower block and said pocket casting end wall as said connector assembly undergoes compressive loading, wherein the improvement comprising: means attached to said wedge for vertically supporting said wedge at a holding position during tensile loading in order to eliminate a build-up of forces which otherwise occurs within said connector assembly if said wedge is allowed to drop into said first fully seated position during tensile loading, said holding position located above said first fully seated position. 2. The improved railcar connector assembly as claimed in claim 1 wherein said holding position is defined as a vertical position above said first fully seated position where a controlled gap is simultaneously maintained between said wedge tront wall and said follower block rear surface and between said wedge back wall and said pocket casting end wall during tensile loading on said connector assembly. 3. The improved railcar connector assembly as claimed in claim 2 wherein said controlled gap is detennined by a compressive load rate of said supporting means. 4. The improved railcar connector assembly as claimed in claim 3 wherein said wedge-supporting means is repeatably capable of restoring said w'edge to said holding position after said compressive load is released from said connector assembly, thereby re-establishing the same said controlled gap. 5. The improved railcar connector assembly as claimed in claim 4 wherein said compression of said supporting means and said relative extent of travel of said supporting means is limited, said limited extent of travel not interfering with said operation of said wedge in removing free slack which is developed within said connector assembly from wear. 6. The improved railcar connector assembly as claimed in claim 5 wherein said supporting means is capable of compressing at a compressive load between about 20,000 pounds and 40,000 pounds, thereby allowing said supporting means to drop into said fully seated position. 7. The improved railcar connector assembly as claimed in claim 6 wherein said controlled gap at said holding position is at least 0.125 inches. 8. the improved railcar connector assembly as claimed in claim 7 wherein said wedge supporting means is comprised of at least one spring attached to at least one of said wedge front and back walls, said spring being received within a blind bore. 9. The improved railcar connector assembly as claimed in claim 8 wherein said spring is made from an elastomeric material, said elastomeric spring having a compressive load rate between about 100,000 and 200,000 pounds per inch. 10. The improved railcar connector assembly as claimed in claim 9 wherein said elastomeric spring has a lateral shear rate between about 75,000 and 150,000 pounds per inch. 11. The improved railcar connector assembly as claimed in claim 10 wherein said elastomeric spring has a coefficient of friction between about 0.3 and 0.5. 12. The improved railcar connectpt assembly as claimed in claim 6 wherein said spring Is comprised of a plunger assembly, said plunger assembly comprised of a steel spring received within said blind bore, a plunger keep having a centrally located orifice and Ihreadably engaged within said blind bore for retaining said steel spring, and a plunger having a shoulder and a tip, said plunger disposed between plunger keep and said steel spring wherein said plunger shoulder is held in continuous contact against said plunger keep by said steel spring, said plunger tip extending through said orifice of said pluti^er keep by an amount necessary to maintain said wedge in said position above said fiilly seated position. 13. The improved railcar assembly as claimed in claim 12 wherein said connector member is comprised of an articulated connector, said articulated connector having a male end and a female end, said female end integrally incorporating said pocket casting, therein such that an arcuate forward end of said male end extends into said pocket and contacts said follower block front surface. 14. An improved railcar connector assembly substantially as herein described with reference to the accompanying drawings.

Documents:

1070-mas-1995 abstract.jpg

1070-mas-1995 abstract.pdf

1070-mas-1995 claims.pdf

1070-mas-1995 correspondence-others.pdf

1070-mas-1995 correspondence-po.pdf

1070-mas-1995 description (complete).pdf

1070-mas-1995 drawings.pdf

1070-mas-1995 form-1.pdf

1070-mas-1995 form-26.pdf

1070-mas-1995 form-4.pdf

1070-mas-1995 others.pdf

1070-mas-1995 petition.pdf