Classifications

• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C11/00—Pivots; Pivotal connections
  • F16C11/04—Pivotal connections
  • F16C11/045—Pivotal connections with at least a pair of arms pivoting relatively to at least one other arm, all arms being mounted on one pin
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
  • B62D—MOTOR VEHICLES; TRAILERS
  • B62D55/00—Endless track vehicles
  • B62D55/08—Endless track units; Parts thereof
  • B62D55/18—Tracks
  • B62D55/20—Tracks of articulated type, e.g. chains
  • B62D55/205—Connections between track links
• • E—FIXED CONSTRUCTIONS
  • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
  • E02F—DREDGING; SOIL-SHIFTING
  • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
  • E02F9/006—Pivot joint assemblies
• • 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
  • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
  • F16C2350/00—Machines or articles related to building
  • F16C2350/26—Excavators

Definitions

• the present invention relates to -a keeper assembly wherein a plurality of replaceable keeper members provide a shoulder which functions to secure a first member against axial displacement with respect to a second member, and particularly to a retaining device for holding the keeper members in place.
• Retaining rings having either a rectangular or circular cross sectional shape are conventionally used by the industry to prevent axial displacement of a bushing, for example, on a cylindrical shaft. Those rings having a circular cross section and mating with shallow semicircular grooves can only resist moderate axial forces, while those rings having a rectangular cross section can resist substantially higher axial forces. Although the rectangular retaining rings provide a more positive shoulder in a plane transverse the central axis of the shaft for resisting higher axial forces, the opposite sharp edged groove root corner causes high stresses in the shaft and a limi- tation on the load carrying capability of the assembly.
• a plurality of arcuate keeper segments having a preselected cross sectional shape are positioned in a correspondingly profiled groove. Failure can occur at only very high loads in the end of the shaft by a shear failure cone eminating about halfway up the side of the groove. Actual use of the referenced keeper assembly is in the environment of an endless track chain joint, where space is at a premium. Unfortunately, the arcuate keeper segments must be inserted radially into the groove in the track pin shaft within a counterbore in a link prior to the installation of a retaining cap in the counterbore.
• a keeper assembly having a plurality of arcuate keeper segments located in an annular groove of a first member for receiving axial loads from a force trans ⁇ mitting surface of a second member.
• each keeper segment has an axially outwardly opening side seat, and a retaining member is releasably con ⁇ nected to the side seats for holding the keeper segments positively in the groove.
• Fig. 1 is a diagrammatic, fragmentary, cross sectional view of a track chain joint illustrating a pair of keeper assemblies constructed in accordance with the present invention
• Fig. 2 is an enlarged, fragmentary, diagram ⁇ matic, perspective end view of one end of the track chain joint illustrated in Fig. 1 showing one of the keeper assemblies including a retaining member, with a portion of the joint shown in cross section for clarity;
• Fig. 3 is an elevational side view- of the retaining member of Fig. 2;
• Fig. 4 is an enlarged, fragmentary, diagram ⁇ matic cross sectional view of the keeper assembly illustrated in Figs. 1 and 2;
• Fig. 5 is a fragmentary view, comparable to Fig. 4, showing a second embodiment retaining member.
• a first keeper assembly 10 and a second identical keeper assembly 12 are shown in connection with the opposite sides of a representative one of a plurality of interconnected endless track chain joints 14.
• Each of the joints 14 includes a track pin 16 having a central axis 18, a cylindrical outer surface 20 and a pair of opposite end surfaces 22.
• a lubricant reservoir 24 is formed within the pin and one or more radial passages 26 communicate fluid in the reservoir to the outer surface centrally of the pin.
• a first pair of track links 28 is mounted as by a press fit on the opposite ends of a hollow cylindrical track bushing 30, and a second pair of track links 32 is mounted as by a press fit on the opposite ends of the track pin.
• a pair of spacer rings 34 transmit axial loads between the bushing and the outer track links and to define the minumuirt spacing the rebetween for axial dimensional control of a pair of end face seal ring assemblies 36 circumscribing the spacer rings and disposed in a respective one of a pair of counterbores 38 in the outer track links.
• first keeper assembly 10 As best illustrated in Figs. 2-4, it may be noted that a plurality of arcuate keeper segments 40 of preselected construction are included and received in an annular groove 42 in the track pin
• First and second retaining means 44,46 are provide for containing the keeper segments in plac"e in.the groove, and for protecting the keeper assembly and track chain joint 14.
• three identical arcuate keeper segments 40 are utilized which are substantially adjacent segments of an interrupted annular ring.
• Each of these keeper segments has a pair of opposite end surfaces 48 as representatively indi- cated in Fig. 2 and as shown best in Fig. 4, a radially outer cylindrical surface 50, a planar side surface or thrust surface 52, a radially inner contoured surface 54, and an axially outwardly opening side seat or bench 56.
• side seat it is meant that a recess is defined in each of the keeper segments for sub ⁇ stantially solely axially receiving the first retaining means 44 and simplifying assembly.
• the side seat 56 is defined by an axially outwardly facing surface 58 oriented in use in a plane transverse to the central axis 18, and by an arcuate, radially outwardly facing surface or cylindrical surface portion 60.
• the cylindrical surface portion 60 of the side seat is disposed radially inwardly of the cylindrical outer surface 20 by a preselected radial depth "d" as indicated in Fig. 4.
• the annular groove 42 opens radially out ⁇ wardly on the cylindrical outer surface 20 of the pin 16 and extends continuously peripherally around the pin in the instant example.
• the groove is defined by a planar sidewall 62 and a concave sidewall 64 connected to each other, and is located at a preselected minimum axial distance "D" from the end surface 22 of the pin as shown in Fig. 4. - •
• the instant embodiment has three similar arcuate keeper segments 40 of about 120° span each for ease of insertion in the groove 42. But it is necessary to insert these keeper segments within the restrictive confines of an axially outwardly facing counterbore 66 in each of the track links 32.
• Each counterbore is defined by an annular end wall or force transmitting surface 68 and a cylin ⁇ drical interval surface 70. In operation, the planar side surface 52 axially receives the force from the end wall 68.
• the first retaining means 44 is seen to include an external retaining ring 72 having a substantially cylindrical internal surface 74 in the free state, a radially outer surface 75, and
• the retaining ring 72 is of the usual C-shaped steel type having a gradual and symmetrical change of radial thickness around its periphery as is illustrated.
• the 5 retaining ring is positionable on the side seat 56 of the individual keeper segments 40 to hold them in place before installation of the second retaining means 46.
• the second retaining means 46 is substan ⁇ tially a retaining cap or cup 78 having an external 10 cylindrical surface 80 and an axially inwardly facing counterbore 82 including an internal cylindrical surface 84.
• the three arcuate keeper segments 40 are installed fully within the pin groove 42 and are preferably temporarily held in place by a sticking agent applied to the radially inner contoured surface 54 thereof. Thereafter the small tangs of a
• 25 plier-like tool of the usual type are placed in the eyes 76 of the retaining ring 72 and the eyes forcefully separated so that the ring is elastically deformed, permitting it to be inserted axially over the cylin ⁇ drical surface 20 of the track pin 16 and into engage-
• O PI of the retaining ring is positioned against the cylin ⁇ drical surface portions 60 of the keeper segments. Since this occurs radially down into the pin groove by the preselected distance "d" the retaining ring is held positively in place.
• the retaining cap 78 is press fitted into the internal surface 70 of the link counter ⁇ bore 66 such that the cap's internal surface 84 is disposed in preselected relatively close radial proximity to the outer cylindrical surfaces 50 of the keeper segments and to the outer surface 75 of the retaining ring.
• a second embodiment keeper assembly 86 is illustrated having elements corresponding to those of the first embodiment indi ⁇ cated by the same reference ' numerals with a prime marking.
• the second embodiment differs only in that the keeper segment's contoured surface 54' is a semi ⁇ circle in cross section rather than a quarter of a circle, and in that the retaining ring 72' is of different construction than the retaining ring 72.
• the retaining ring '72' is a spiral wrap ring of relatively thin steel and of substantially radially elongate rectangular cross sectional configur- ation.
• the retaining ring 72' is installed axially over the cylindrical surface 20' of the pin 16' and snapped radially into a positive engagement with the individual keeper segments 40' at the depressed side seats 56' .
• the preselected cross sectional construction of the keeper segments 40,40' and the mating groove 42,42' has greatly- extended the load to failure capabilities of the keeper assemblies 10 and 86 when compared with conventional retaining ring arrangements with, for example, a groove having a sharp edged rectangular configuration.
• the dual retaining means 44,46 provide the way to assure positive assembly of the keeper segments and positive containment and protection thereof in the severe service environment of a track chain joint.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Chemical & Material Sciences (AREA)
• Combustion & Propulsion (AREA)
• Transportation (AREA)
• Mining & Mineral Resources (AREA)
• Civil Engineering (AREA)
• Structural Engineering (AREA)
• Snaps, Bayonet Connections, Set Pins, And Snap Rings (AREA)
• Pivots And Pivotal Connections (AREA)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=22147549

Family Applications (1)

Country Status (2)

Cited By (9)

Families Citing this family (1)

Citations (9)

• 1979
  • 1979-03-23 JP JP50167379A patent/JPS56500266A/ja active Pending
  • 1979-03-23 WO PCT/US1979/000187 patent/WO1980002059A1/en unknown

Patent Citations (9)

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