US2916163A - High capacity draft gear - Google Patents

High capacity draft gear Download PDF

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Publication number
US2916163A
US2916163A US766169A US76616958A US2916163A US 2916163 A US2916163 A US 2916163A US 766169 A US766169 A US 766169A US 76616958 A US76616958 A US 76616958A US 2916163 A US2916163 A US 2916163A
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Prior art keywords
spring
gear
housing
follower
chamber
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US766169A
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David S Campbell
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Cardwell Westinghouse Co
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Cardwell Westinghouse Co
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B61—RAILWAYS
    • B61G—COUPLINGS; DRAUGHT AND BUFFING APPLIANCES
    • B61G9/00—Draw-gear
    • B61G9/04—Draw-gear combined with buffing appliances
    • B61G9/10—Draw-gear combined with buffing appliances with separate mechanical friction shock-absorbers

Definitions

  • This invention relates to draft gears for railroad cars and has for its principal object to provide a long travel, high capacity gear that may be employed in the newly contemplated longer draft gear pockets in connection with the usual types of draft gear attachments to achieve increased capacity over longer travel and thereby maintain reaction pressures on the car Within acceptable limits.
  • the invention utilizes a friction cushioning element in tandem with a coil spring cushioning element and longer gear travel is accommodated with a conventional type of coil spring cushioning element by utilizing a guide stem that is movable with the follower for the coil spring element to cooperate with the spring element and give it necessary columnar stability during compression.
  • the coil spring aligns the guide stem, which cooperates with an intermediate follower for preventing tipping of this follower, thereby avoiding binding or sticking of the gear.
  • Additional capacity is achieved through longer travel and through the use of corner coil springs mounted in individual spring chambers that extend parallel to the main coil spring chamber. The action of the friction system throughout the gear closure absorbs suicient energy to maintain reaction pressures on the car within required limits.
  • Fig. 1 is a horizontal section through familiar parts of a freight car showing the draft gear mounted in a draft gear pocket in association with the draft gear attaching devices;
  • Fig. 2 is a vertical section through the same
  • Fig. 3 is an enlarged 1horizontal section through a draft gear of increased capacity and travel made according to the invention with the draft gear being shown in full release;
  • Fig. 4 is a vertical section along the medial line of the draft gear in full release
  • Fig. 5 is a front end View of the draft gear
  • Fig. 6 and Fig. 7 are vertical sections taken respectively along the lines 6-6 and 7-7 of Fig. 3;
  • Fig. 8 is a perspective view of the draft gear housing
  • Fig. 9 is a perspective view of the friction plates and wedge shoes
  • FIG. 10 is a perspective view of the central plunger
  • Fig. 11 is a perspective View of the intermediate follower and wedge member
  • Fig. 12 is a perspective view of the guide stem
  • Fig. 13 is a perspective view of an auxiliary spring seat
  • Fig. 14 is a capacity drop test curve for the gear
  • Fig. l5 is a fragmentary horizontal section illustrating and are not intended to impose unnecessary limitations on the claims.
  • FIGs. 1 and 2 there are shown center sills 10, front y and rear draft gear lugs 11 and 12 respectively, a vertical yoke 13 connected to a coupler shank-14 by a draft key 15, in the positons they assume in full release, with a coupler horn 16 spaced from a striking plate 17 and with a front follower 18 Within the yoke 13 and against thel front lugs 11, all substantially in accord with convention-l al practice.
  • the coupler carrier iron is shown at 19 and the draft gear carrier irons are shown at 20, there being two required due to the length of the draft pocket.
  • the draft pocket is 36 intlength in accordance with recently revised specifications of the Association of American Railroadsr
  • the present gear when in its full release condition is 33% long and accommodates a nominal gear closure travel of 41/2".
  • the coupler horn 16 is spaced a full 5 in front of the striking plate 17. This 41/2 travel represents a significant increase over the former maximum travel of 2% and makes it possible to greatly increase draft gear capacity for better handling of the high energy bung shocks socommon in present day freight yard switching practice.
  • the present draft gear generally designated as 21,'includes a housing 22 having a rear chamber 23 for a spring cushioning mechanism, generally designated as 24, and a front chamber 25 for a friction cushioning mechanism, generally designated as 26, with the front chamber being in open communication with the rear chamber and having an opening 27 through the front of the housing.
  • the draft gear housing 22 (Figs. 6, 7 and 8) is an oblong, rectangular, hollow steel casting having top, bottom and side walls designated respectively 28, 29 and 30, with the portions of the top and bottom walls that define the rear chamber each being formed with a pair of laterally' spaced apart, parallel, longitudinally extending ribs 31 and 32.
  • the ribs 31 and 32 partially define a main spring chamber in which is mounted a conventional triple-coil spring arrangement consisting of helical springs 34, 35 and 36 which are adapted to be compressed against the rear wall 37 of the housing.
  • the ribs 31 partially dene an auxiliary spring chamber, the top and bottom portions of which receive individual corner coil springs 38, while the ribs 32 partially de- ⁇ fine a complementary auxiliary spring chamber, the top and bottom portions of which receive individual corner coil springs 39.
  • the auxiliary spring chambers are spaced apart laterally and extend parallel to the main .are stationary and 46 is movable.
  • coil Vsprings are also adapted to be compressed against the rear wall 37.
  • An intermediate follower and wedge member 40 (Fig. 1l) is located forwardly of the -cushioning mechanism in ⁇ the rear chamber and includes a base plate 41 that provides a spring seat for the triple-coil spring arrangement while auxiliary spring seats 42 (Fig. 13) are disposed in theV auxiliary spring chambers between the corner springs and the base plate 41.
  • each of the auxiliary spring seats cooperates with two corner springs; and while this arrangement takes optimum advantage of the guiding action of the ribs 31 and 32 and better Asynchronizes the operation of the parallel corner spring elements, it is recognized that individual auxiliary corner spring seats can be provided for each corner spring.
  • the friction mechanism 26 including groups of intercalated plates, of which 44 and 45 between the stationary plates 45 of each group are a pair of laterally spaced apart wedge shoes 47 having oppositely outwardly facing surfaces 43 cooperating with the inwardly facing friction "surfaces 49 of the stationary plates 45.
  • the wedge shoes 47 have forward wedge surfaces 50 cooperating with similar. wedge surfaces 51 on a central plunger 52 and rearward wedge surfaces 53 cooperating with like surfaces 54 formed on the forward end of a chambered box-shaped casting 55 that projects forwardly from base plate 41.
  • the wedge surfaces 54 are shown as being .carried integral with the intermediate follower 40 and to be separate.
  • the box-shaped casting 55 includes longitudinal reinforcing ribs 57 that define a central guiding chamber that is open; at both ends with its forward opening 58 being coaxial' with, but somewhat larger than, its rearward opening 59.
  • a stepped tubular guide stem 60 (Fig. 12), of preferably cylindrical form is disposed within the guide chamber with its larger front end portion 61 in guiding cooperation with the ribs 57 and with its smaller rear end portion 62 projecting through the opening 59 in base plate 41 and telescoped within the central coil spring 36.
  • the guide stem includes an intermediate transverse wall 63 that bears against the marginal wall portions surrounding opening 59.
  • a minimum design clearance is provided between the rear portion 62 of the stem and coil-spring 36 that normally avoids contact therebetween.
  • libs 31 and 32 in the rear chamber provide a similar stabilizing inuence onthe outer coil spring 34.
  • the central plunger 52 includes a pair of vertically spaced, rearwardly extending, parallel arms 64 that are bridged by a transverse wall 65 'which forms a spring seat 66 for one end of a coil spring 67, the other end of which seats against the transverse wall 63 of the guide stem 60.
  • the spring 67 thus reacts between the coil spring cushioning mechanism 23 and the plunger 52 to constantly urge the plunger 52 toward its release position.
  • the auxiliary spring seats 42 and the associated corner springs 38 and 39 are first located in place within the gear and then the triple-coil sprlngs andintermediate follower and wedge member 40 are inserted through the front end of the housing.
  • the housing 22 (Fig. 8) is provided with openings 68 through which assembly pins may' be inserted for engaging the intermediate follower and wedge member 40 after suitable compression of the coil spring cushioning mechanism, and this gives ample clearance for assembling the friction devices.
  • Stationary plates 44 are held by vertical ribs 7i) and 71 formed on the side walls 30 of the housing and stationary plates 45 are held by horizontal ribs 72 and 73 carried by the top and bottom walls of the housing.
  • the projections 69 are provided with pointed forward ends 74. After a few normal operations of the gear these pointed ends cut into the housK ing and allow full release of the gear between the lugs 11 and 12.
  • the bufiing shock is transmitted from the coupler 14 through the front follower 18 to the central plunger 52, forcing it to the right as viewed 1n Figs. 3 and 4, causing it to act through the wedge shoes 47 and the chambered casting 55 to transmit the travel to the intermediate follower plate 41 and compress all of the coil spring cushioning elements simultaneously.
  • These parts will furnish sufficient cushioning for light butiing shocks.
  • the follower will come against the outer ends of the movable plates 46 introducing energy-absorbing friction between the movable plates 46 and the stationary plates 44 and 45 which have been pressed together hy the action of the wedge shoes 47.
  • the present gear offers a huge increase in capacity over all known gears and as may be determined from the characteristic curve shown in Fig. 14, the capacity of this gear is on the order of 80,000 foot pounds. It is important to note that the action of the friction system permits this to be accomplished without exceding a 500,- 000 pound reaction pressure on the car sills and thus these high energy shocks are readily handled without upsetting the coupler shank.
  • the curve shown in Fig. 14 is based on the standard A.A.R. capacity drop-test and the cross-hatched area 75 between the closure curve 76 and the recoil curve 77 represents the amount of energy absorption.
  • the problem of columnar stability of the coil springs is an important one.
  • a maximum of cushioning capacity is achieved by means of the ribbed hous ing constructions which permit corner springs to be accommodated and vguided during their compression and expansion.
  • the guiding action is provided by the cooperation between the ribs 31 and 32 and the corner springs themselves and even more importantly by the cooperation between these ribs and the auxiliary spring seats for the corner springs.
  • the ribs 31 and 32 also .provide a guiding action to the outer spring 34 of the triple-coil group and, in conjunction with the action of the guide stem 60, provide necessary stability to the triple-coil group during compression of the gear.
  • the guide stem in turn cooperates with the chambered casting 55 of the intermediate follower 40 to insure that the guide stem is properly centered.
  • the guide stern itself forms a seat for release spring 67.
  • intermediate follower and guide stem structure may be variously embodied within the scope of the teachings of this invention, and two alternative embodiments of this structure are shown in Figs. and 16, respectively.
  • the general arrangement of these alternative embodiments is similar to that previously described, and corresponding parts are assigned identical reference char'- acters for convenience of disclosure.
  • the guide stem 60 may be essentially identical in form to that of the previously described embodiment; however, the rear surface 61S of the front end portion 61 now functions as a spring seat for the innermost coil spring 36 of the spring cushioning assembly 24.
  • This innermost coil spring 36 therefore urges the guide stem towards the open front end 58 of the box-shaped casting 55, which is formed with internal shoulders 55S for abutting coaction with the guide stern.
  • the guide stem cooperates with the internal ribs of the box-shaped casting for maintaining the stern and casting in properly centered relation within the draft gear housing such that the stem normally resists any tendency for the center coil spring 36 to deflect laterally under compression loading.
  • Fig. 16 illustrates the preferred commercially tested and approved structure of the present invention, and it employs a one-piece intermediate follower and guide stem structure 140 (see Fig. 17) having a transversely arranged base plate 141 providing a spring seat for the coils 134 and 135 of a double-coil main spring cushioning element.
  • integrally connected to the -base plate is a rearwardly extending stern portion 162 and a forwardly extending, box-shaped, chambered casting 155.
  • the corner regions of the base plate are again arranged to abut the auxiliary spring seats 42 for the sets of corner springs 38 and 39.
  • the base plate also extends inwardly of the periphery of the chambered casting 155 to provide a spring seat for the release spring 67.
  • the box-shaped chambered casting 155 is provided with lengthwise extending internal reinforcement walls 157; and at its forward end it again terminates in cooperating wedge-like surfaces 154, with the casting opening through these wedge surfaces as indicated at 158 to accommodate the release spring 67.
  • the rearwardly projecting guide stem 162 of this embodiment is of increased diameter when compared with the foregoing arrangements so that only a double-coil main spring cushioning element may be accommodated within the cross-sectional dimensions o'f the gear housing 22.
  • This stem extends a distance of approximately six inches from the transverse plane of the base plate 141 and is provided with inward end shoulders 1625 forming a seat for an additional spring 136 that is arranged to act between the rear housing wall 37 and the end of the stern 162.
  • This additional spring 136 makes effective use of the available space behind the stem and gives a measure of added capacity to the gear.
  • the one-piece follower and guide structure offers the advantages of inherently greater strength and a more secure and reliable guiding action, and it functions in essentially the same fashion as the two-piece follower and guide structures of the embodiments of Figs. 3 and l5.
  • the guide stem 162 cooperates with the innermost coil spring to insure desired columnar stability of this spring.
  • the spring 135 acts upon the stem 162 to maintain the longitudinal alignment of the follower and guide structure and resist any tendency for the follower to become cocked or tipped, a condition which could lead to binding or sticking of the gear.
  • the remaining components such as the friction system, the release spring 67, and the corner springs and associated auxiliary seats, function in the same manner as described previously.
  • Fig. 18 is a capacity curve and the shaded portion under the curve 176 is a measure of the energy absorbed during closure of the gear.
  • Fig. 19 shows a curve of the reaction force to which the car sill is subjected, together with the gear capacity curve for a range of gear closure travel, and the dot-dash lines on this curve illustrate that in tests made in accordance with the A.A.R. specification M901C-56, the gear of Fig. 16 tested to a capacity of 77,820 foot pounds over a 4.39 gear closure travel with a reaction force to the car sills of only 447,000 pounds.
  • a housing having a rear chamber and a front chamber in open communication with the rear chamber and open at its front end, said housing carrying laterally spaced opposed friction surfaces in said front chamber; a main spring cushioning element disposed centrally in said rear chamber and a plurality of corner spring cushioning elements spaced about and extending alongside said main element; auxiliary spring seats forwardly of said corner spring elements on opposite sides of said main spring element; an intermediate follower member overlying and disposed forwardly of and in abutting relation to said auxiliary spring seats and said main cushioning element and movable with said spring seats relative to said housing to compress or release all of said cushioning elements simultaneously; and an energy absorbing friction cushioning element mounted in said front chamber to react against said intermediate follower and including a thrust wedge acting between laterally spaced friction surfaces to urge said last-mentioned friction surfaces outwardly into cooperation with said opposed friction surfaces during compression of said gear.
  • a housing having a rear chamber of a generally rectangular cross section defined by top, bottom and side walls with longitudinally extending internal ribs carried by opposite ones of said walls and partially -defining a main cylindrical spring chamber and a plurality of corner sprinU chambers, said housing having a front chamber in open communication with the rear chamber and opened at its front end, said housing carrying laterally spaced opposed friction surfaces in said front chamber; a main spring cushioning element and a plurality of corner spring cushio g elements disposed in side-by-side relation in said spr Ag chambers; an intermediate follower member ov lying and disposed for wardly of all of said cushioning elements and movable relative to said housing to compress or release all of said cushioning elements simultaneously; and an energy absorbing friction cushionir7 element mounted in said front chamber to react aga ist said intermediate follower and including a thrust wedge acting between laterally ⁇ spaced friction surfaces to urge said last mentioned friction surfaces outwardly into cooperation with said opposed friction surfaces during compression of said gear.
  • a housing having a rear chamber of a generally rectangular cross section defined by top, bottom and side walls with longitudinally extending internal ribs carried in opposed relationship by said top and bottom walls and partially defining a main cylindrical spring chamber and lateral spring chambers on opposite sides of and alongside said main spring chamber, said housing having a font chamber in open communication with rear chamber and open at its front end, said housing carrying laterally spaced opposed friction surfaces in said front chamber; a main spring cushioning element in said main spring chamber and a pair of corner spring cushioning elements disposed in each of said lateral chambers; an au ary spring seat member for each of said lateral chambers forwardly of the corner spring elements therein and overlying both of the same; an intermediate follower member overlying and disposed forwardly of all of said cushioning elements and movable relative to said housing to compress or release all of said cushioning elements simultaneously; and an energy absorbing friction cushioning element mounted in said front chamber to react against said intermediate follower and including a thrust wedge acting between laterally spaced friction surfaces to urge said
  • a draft gear a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying laterally spaced opposed friction surfaces in said front chamber, coil spring cushioning means in the rear chamber, an in# termediate follower forwardly of said coil spring means and having a central passageway at least p rtially defined by guide surfaces carried by said follower, a unitary guide member having a forward portion cooperating with said guide surfaces and having a rearward portion extending through said central passageway into telescopic relationship with said coil spring means to cooperate therewith and provide columnar stability thereto, said guide member and follower having cooperating abutment surfaces preventing relative movement therebetween in one longitudinal directi n, an energy absorbing friction cushioning el t mounted in said front charnber to react against said follower ano including a thrust wedge acting between laterally spaced friction surfaces to urge said last mentioned friction surfaces outwardly into cooperation with said opposed frictionsurfaces during compression of said gear, and a release spring extending between said
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carryinJ laterally spaced opposed friction surfaces said front chamber, coil spring cushioning means in the rear chamber, an ntermediate follower'forwardly of said coil spring means and comprising a base plate having a central opening and a forwardly projecting box shaped member carrying inner guide surfaces defining a passageway open at the front and partially closed at its rear by portions of said base plate adjacent said opening, a stepped guide member having a larger forward portion cooperating with said guide surfaces and abutting said base plate portions and having a rearward portion connected to said forward portion by a transverse wall and extending through said central opening to telescope within said coil spring means to cooperate therewith and provide columnar stability thereto, and an energy absorbing friction cushioning element mounted in said front chamber to react against said front follower Vand including a plunger forming a thrust wedge and carrying a spring seat, said plunger acting between laterally spaced friction surfaces to urge said last-menti
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying laterally spaced opposed friction surfaces in said front chamber, a main spring cushioning element disposed centrally in said rear chamber and a plurality of corner spring cushioning elements spaced about said main element, auxiliary spring seats forwardly of said corner spring element, an intermediate follower overlying and disposed forwardly of said auxiliary spring seats and said main cushioning element and movable relative to said housing to compress and release all of said cushioning elements simultaneously, said follower having a central passageway at least partially defined by guide surfaces carried by said follower, a guide member having a forward portion cooperating with said guide surfaces and having a rearward portion extending through said central passageway into telescopic relationship with said main spring cushioning element to cooperate therewith and provide columnar stability thereto, said guide member and follower having cooperating abutment surfaces pre venting relative movement therebetween, an energy absorbing friction cushioning element mounted in said front chamber to react against said follower and including a
  • a draft gear housing said housing having a rear chamber of a generally rectangular cross section defined by top, bottom, and side walls with longitudinally extending internal ribs carried by opposite ones of said walls and partially defining a main cylindrical spring chamber and corner spring chambers on opposite sides of said main chamber, said housing having a front chamber in open communication with the rear chamber and open at its front end.
  • a draft gear a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced inwardly facing friction surfaces in said front chamber, spring cushioning means in the rear chamber, intermediate follower structure disposed forwardly of and overlying said spring means and including a transversely extending follower plate and a rearwardly extending guide stem movable therewith lengthwise in said housing, said guide stem and said spring means being disposed in adjacent telcscoping relationship to cooperably resist tipping of said plate, an
  • energy-absorbing friction-cushioning element mounted in said front chamber to react against said follower structure and including a plurality of transversely spaced wedge shoes having outwardly facing friction surfaces and a thrust wedge acting between said shoes to urge said outwardly facing friction surfaces into cooperation with said inwardly facing friction surfaces during compression of said gear, and 'a release spring extending between said intermediate follower structure and thrust wedge for continuously urging the same apart to release said friction cushioning element after compression of said gear.
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality ⁇ of transversely spaced inwardly facing friction surfaces vin said front chamber, a main spring cushioning element disposed centrally in the rear chamber and a plurality of auxiliary spring cushioning elements spaced about and extending alongside said main element, intermediate follower structure disposed forwardly of and overlying all of said spring elements and including a transversely extending follower plate and a rearwardly extending guide stem movable therewith lengthwise in said housing, said guide stem and said main spring cushioning element being disposed in adjacent telescoping relationship to cooperably resist tipping of said plate, an energy-absorbing friction-cushioning element mounted in said front chamber to react against said follower structure and including a plurality of transversely spaced wedge shoes having outwardly facing friction surfaces and a thrust wedge acting between said shoes to urge said outwardly facing friction surfaces into cooperation with said inwardly facing friction surfaces during compression of said gear, and
  • said main spring element comprises a plurality of concentric coil springs and said guide stem is in telescoping relation within the inner coil spring.
  • a housing having a rear chamber of a generally rectangular cross section defined by top, bottom and side Walls with longitudinally extending internal ribs carried by opposite ones of said walls and ,partially defining a main spring chamber and a plurality of corner spring chambers, said housing having a front chamber in open communication with the rear chamber and open at its front end, said housing carrying a plurality of transversely spacedv inwardly facing friction surfaces in said front chamber; a main spring cushioning element and a plurality of corner spring cushioning elements disposed in side-by-side relation in said spring chambers; intermediate follower structure disposed forwardly of and overlying all of said spring elements and including a transversely extending follower plate and a rearwardly extending guide stem movable therewith lengthwise in said housing, said guide stem extending into telescopic relationship with said annular spring cushioning element and cooperating therewith to resist tipping of said plate, an energy-absorbing friction-cushioning element mounted in said front chamber to react against said
  • a housing having a rear chamber ⁇ pf a generally rectangular cross section defined by top,
  • a draft gear that includes a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced, inwardly facing friction surfaces in said front chamber, spring cushioning means in the rear chamber, an energy-absorbing friction-cushioning element mounted in the front chamber and including a plurality of transversely spaced wedge shoes having outwardly facing friction surfaces and a thrust wedge acting between said shoes to urge said outwardly facing friction surfaces into cooperation with said inwardly facing friction surfaces during compression of the gear, and means for transmitting force and movement between said friction-cushioning element and said spring cushioning means; the improvement wherein said force-transmitting means comprises intermediate follower structure having a transversely extending follower plate disposed forwardly of said spring cushioning means to overlie and provide a seat therefor, a box-shaped portion rigid with and extending forwardly of said plate and providing corresponding wedge faces engageable with said wedge shoes, a rearwardly extending guide stem interlocked with the plate to resist
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front end, said housing carrying laterally spaced opposed friction surfaces in said front chamber, a main spring cushioning element disposed centrally in the rear chamber and a plurality of auxiliary spring cushioning elements spaced about and extending alongside said main element, and energy-absorbing friction-cushioning element mounted in the front chamber in tandem relation with said main and auxiliary -cushion- 'afilados IllA ing elements, intermediate follower structure located between said friction-cushioning element and said spring cushioning elements and including a transversely extending follower plate overlying all of said spring cushioning elements, a box-shaped portion rigid with and extending forwardly of said plate to provide forward wedge faces, a guide stem interlocked with the plate to resist lateral movement
  • Intermediate follower structure for a draft gear said follower structure comprising a transverse base plate portion having oppositely lengthwise directed front and rear surfaces with said rear surface constituting a spring seat, a box-shaped portion integral with and extending forwardly of said front surface and providing cooperating wedge faces at its forward end, and a guide stem integral with and extending rearwardly of said rear surface from a point centrally of said spring seat.
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced inwardly facing friction surfaces in said front chamber, spring cushioning means in the rear chamber, intermediate follower structure disposed fo-rwardly of and overlying said spring means and including a transversely extending follower plate, a box-shaped portion rigid with and extending forwardly of said plate and providing forward wedge faces, and a rearwardly extending guide stem rigid with said plate and disposed in adjacent telescoping relation with said spring cushioning means to cooperably resist tipping of said plate, and an energy-absorbing friction-cushioning element mounted in said front chamber to react against said intermediate follower structure and including a plurality of transversely spaced wedge shoes engageable with said wedge faces and having outwardly facing friction, surfaces, and a thrust wedge acting between said shoes and cooperating with said wedge faces to urge said outwardly facing friction surfaces of said shoes into cooperation with said inwardly facing friction surfaces during
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced inwardly facing friction surfaces in said front chamber, spring cushioning means in the rear chamber, intermediate follower structure disposed forwardly of and overlying said spring means and including a transversely extending follower plate having a central opening and a forwardly projecting box-shaped portion rigid with the plate and providing forward wedge faces, said box-shaped portion carrying Yinner lengthwise guide surfaces and internal ytransverse shoulders defining a passageway open at the rear and partially closed at its front by said shoulders, a guide member in said passageway cooperating with said guide surfaces to prevent lateral movement relative thereto and abutting said front portions of said box-shaped portion, said guide member having a stem extending rearwardly through said central opening into adjacent telescoping relation with said spring cushioning means to cooperably resist tipping of said plate, an energy-absorbing friction-cushioning element mounted in said front chamber to react against said
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced friction plates providing transversely inwardly facing friction surfaces extending in rearwardly converging relation in said front chamber, said housing having an integral rear wall; concentric multiple-coil spring-cushioning means in the rear chamber and seating against said rear wall; an energy-absorbing friction-cushioning element mounted in the front chamber and including a plurality of transversely spaced wedge shoes having transversely outwardly facing friction surfaces and a plunger including a thrust wedge acting between said shoes to urge said transversely outwardly facing friction surfaces into cooperation with said transversely inwardly facing friction surfaces during compression of the gear; said plungerl including a longitudinally rearwardly offset and rearwardly facing spring seat; intermediate follower structure having a transversely extending follower plate disposed forwardly of said concentric multiple-coil spring-cushioning means to overlie and provide a seat therefor;
  • a housing having a rear chamber and a front chamber in open communication therewith and open at the front, said housing carrying a plurality of transversely spaced friction plates providing transversely inwardly facing friction surfaces extending in rearwardly converging relation in said front chamber, said housing having an integral rear wall; concentric multiple-coil spring-cushioning means in the rear chamber and seating against said rear wall; and a plurality of corner spring cushioning elements spaced about and extending alongside said multiple-coil spring-cushioning means andseating against said rear wall; auxiliary spring seats forwardly of said corner spring elements on opposite sides of said multiple-coil spring-cushioning means; an energy-absorbing friction-cushioning element mounted in the front chamber and including a plurality of transversely spaced wedge shoes having transversely outwardly facing friction surfaces and a plunger including a thrust wedge acting between said shoes to urge said transversely outwardly facing friction surfaces into cooperation with said transversely inwardly facing friction surfaces during compression of the gear

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Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4076129A (en) * 1976-09-22 1978-02-28 Westinghouse Air Brake Company Friction mechanism for draft gear
FR2405850A1 (fr) * 1977-10-13 1979-05-11 Westinghouse Air Brake Co Carter d'attelage
US4296868A (en) * 1977-10-13 1981-10-27 Westinghouse Air Brake Company Housing for draft gear
US4645187A (en) * 1984-09-14 1987-02-24 American Standard Inc. Draft gear assembly
US5152409A (en) * 1990-12-21 1992-10-06 Westinghouse Air Brake Company Draft gear assembly
US5452814A (en) * 1993-01-11 1995-09-26 Westinghouse Air Brake Company Variable angle friction clutch mechanism for a draft gear assembly
US5590797A (en) * 1995-05-10 1997-01-07 Westinghouse Air Brake Company Friction clutch mechanism for high capacity draft gear assembly and method of reconditioning draft gear with such friction clutch mechanism
WO2005100119A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Taper lugs on draft gear plates
WO2005100118A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Taper under taper plate to increase side force on the movable plate
WO2005100120A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Long travel high capacity friction draft gear assembly
WO2007103087A1 (en) 2006-03-02 2007-09-13 Wabtec Holding Corp. Light weight high capacity friction draft gear assembly
US20080264890A1 (en) * 2004-04-08 2008-10-30 King Dennis W Taper under tapered plate to increase side force on the movable plate
US20090008352A1 (en) * 2003-12-11 2009-01-08 Howard Sommerfeld Draft gear assembly
US20090308829A1 (en) * 2007-05-01 2009-12-17 Wabtec Holding Corp. Elastomeric draft gear having a housing
US8672151B2 (en) 2011-09-15 2014-03-18 Wabtec Corp Elastomeric draft gear for a railcar
US11320020B2 (en) 2017-06-21 2022-05-03 Aleh Nicolaevich Halavach Friction shock absorber

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US1844197A (en) * 1928-03-02 1932-02-09 Cardwell Westinghouse Co Friction draft gear
US2121833A (en) * 1934-01-04 1938-06-28 Cardwell Westinghouse Co Draft gear

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Publication number Priority date Publication date Assignee Title
US1844197A (en) * 1928-03-02 1932-02-09 Cardwell Westinghouse Co Friction draft gear
US2121833A (en) * 1934-01-04 1938-06-28 Cardwell Westinghouse Co Draft gear

Cited By (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4076129A (en) * 1976-09-22 1978-02-28 Westinghouse Air Brake Company Friction mechanism for draft gear
FR2405850A1 (fr) * 1977-10-13 1979-05-11 Westinghouse Air Brake Co Carter d'attelage
US4296868A (en) * 1977-10-13 1981-10-27 Westinghouse Air Brake Company Housing for draft gear
US4645187A (en) * 1984-09-14 1987-02-24 American Standard Inc. Draft gear assembly
AU579891B2 (en) * 1984-09-14 1988-12-15 American Standard, Inc. Draft gear assembly
US5152409A (en) * 1990-12-21 1992-10-06 Westinghouse Air Brake Company Draft gear assembly
US5452814A (en) * 1993-01-11 1995-09-26 Westinghouse Air Brake Company Variable angle friction clutch mechanism for a draft gear assembly
US5495957A (en) * 1993-01-11 1996-03-05 Westinghouse Air Brake Company Variable angle friction clutch mechanism for a draft gear assembly
US5501347A (en) * 1993-01-11 1996-03-26 Westinghouse Air Brake Company Variable angle friction clutch mechanism for a draft gear assembly
US5529194A (en) * 1993-01-11 1996-06-25 Westinghouse Air Brake Company Variable angle friction clutch mechanism for a draft gear assembly
US5590797A (en) * 1995-05-10 1997-01-07 Westinghouse Air Brake Company Friction clutch mechanism for high capacity draft gear assembly and method of reconditioning draft gear with such friction clutch mechanism
US20090008352A1 (en) * 2003-12-11 2009-01-08 Howard Sommerfeld Draft gear assembly
WO2005100119A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Taper lugs on draft gear plates
WO2005100118A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Taper under taper plate to increase side force on the movable plate
WO2005100120A1 (en) 2004-04-08 2005-10-27 Wabtec Holding Corporation Long travel high capacity friction draft gear assembly
US20050252874A1 (en) * 2004-04-08 2005-11-17 King Dennis W Taper under taper plate to increase side force on the movable plate
US20080264890A1 (en) * 2004-04-08 2008-10-30 King Dennis W Taper under tapered plate to increase side force on the movable plate
US7900785B2 (en) * 2004-04-08 2011-03-08 Wabtec Holding Corp. Taper under tapered plate to increase side force on the movable plate
WO2007103087A1 (en) 2006-03-02 2007-09-13 Wabtec Holding Corp. Light weight high capacity friction draft gear assembly
US20090308829A1 (en) * 2007-05-01 2009-12-17 Wabtec Holding Corp. Elastomeric draft gear having a housing
US8096432B2 (en) 2007-05-01 2012-01-17 Wabtec Holding Corp Elastomeric draft gear having a housing
US8672151B2 (en) 2011-09-15 2014-03-18 Wabtec Corp Elastomeric draft gear for a railcar
US11320020B2 (en) 2017-06-21 2022-05-03 Aleh Nicolaevich Halavach Friction shock absorber

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