US3567294A - Articulated chain assembly - Google Patents

Articulated chain assembly Download PDF

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Publication number
US3567294A
US3567294A US669218A US3567294DA US3567294A US 3567294 A US3567294 A US 3567294A US 669218 A US669218 A US 669218A US 3567294D A US3567294D A US 3567294DA US 3567294 A US3567294 A US 3567294A
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US
United States
Prior art keywords
sprocket
mid
pitch
lug
articulated
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.)
Expired - Lifetime
Application number
US669218A
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English (en)
Inventor
Fred E Simpson
Eugene J Hnilicka
Roy E Mayo
John S Ricca Jr
Gail G Avery
Charles E Wagaman
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Caterpillar Inc
Original Assignee
Caterpillar Tractor Co
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Caterpillar Tractor Co filed Critical Caterpillar Tractor Co
Application granted granted Critical
Publication of US3567294A publication Critical patent/US3567294A/en
Assigned to CATERPILLAR INC., A CORP. OF DE. reassignment CATERPILLAR INC., A CORP. OF DE. ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: CATERPILLAR TRACTOR CO., A CORP. OF CALIF.
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • 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
    • B62D55/202—Wheel engaging parts; Wheel guides on links
    • 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
    • B62D55/096—Endless track units; Parts thereof with noise reducing means

Definitions

  • This invention relates to an improved articulated drive chain assembly for a track-type vehicle, such as a crawler tractor. More particularly, the invention relates to an articulated drive chain assembly having a driving lug located substantially equidistant the centers of the articulated joints, referred to as mid-pitch, wherein the lug is formed to cooperate with a chain driving sprocket or sprockets to permit limited rocking of the assembly on the sprocket to thereby reduce horsepower losses in the chain drive and to simultaneously limit external wear at the articulated joints.
  • Prior art articulated chain drive assemblies are in general constructed such that the articulated joints provide fo two important functions. Firstly, the articulated joints provide hinged connections between adjacent chain sections so that the chain, under driving conditions, may conform to either a linear path or a curvilinear path (i.e. when traveling on the sprocket or over rough terrain). Secondly, the aticulated joints of prior art structures provide a drive means for co-action wtih the sprocket teeth whereby the chain is forcefully driven by rotational move ment of the sprocket.
  • Another advantage of the invention resides in the power savings realized from the present mid-pitch construction which permits the chain link to rock as it enters upon the drive sprocket.
  • the construction of the present invention reduces the distance through which the incoming chain link must 3,567,294 Patented Mar. 2, 1971 travel. Such a reduction results in a decrease in acceleration and deceleration of the incoming chain which in turn results in a power savings.
  • a further advantage of the mid-pitch drive construction of the present invention over prior art structures relates to a power savings effected after impact of the chain With the driving sprocket.
  • conventional prior art chain drive constructions the articulated joints are prevented from rocking upon the drive spocket because the pins and bushings forming the articulated joints are the driven members and are engaged in the notched portions of the sprocket such that they are in effect held against movement.
  • such conventional structures are subjected to frictional power losses due to the scrubbing action of the articulating bushings against the sprocket.
  • the present invention provides a mid-pitch drive construction which allows for a limited amount of rocking of the chain link upon the sprocket to keep the articulated joint out of engagement with the sprocket during the initial portion of the driving cycle, which substantially eliminates external bushing wear caused by scrubbing of the bushing upon the sprocket and also reduces power losses caused by the scrubbing action.
  • the articulating bushing may eventually bottom out on the sprocket, but only after articulation is substantially completed and when it is not subjected to the driving load.
  • FIG. 1 is a plan view illustrating one preferred embodiment of the invention
  • FIG. 2 is a side elevation of the embodiment illustrated in FIG. 1;
  • FIG. 3 is a schematic illustration of a typical prior art construction
  • FIG. 4 is a schematic illustration of an embodiment of the present invention for comparison with FIG. 3 relative to power loss caused by impact with a driving sprocket;
  • FIG. 5 is a schematic illustration of a typical prior art construction
  • FIGS. 69 schematically illustrate an embodiment of the present invention for comparison with FIG. 5 relative to power loss caused by chordal action of articulated chain members as they enter upon a driving sprocket;
  • FIG. 10 schematically illustrates a prior art construction with regard to wear and power loss caused by scrubbing action
  • FIG. 11 schematically illustrates an embodiment of the present invention for comparison with FIG. 10;
  • FIG. 12 schematically illustrates another embodiment of the present invention.
  • FIG. 13 illustrates the manner in which the rocking angle or degrees of rocking may be calculated for the various embodiments of the invention.
  • FIGS. l4l9 illustrate various embodiments of midpitch drive lug construction.
  • FIGS. 1 and 2 there is shown one preferred embodiment of an improved articulated chain assembly employing a mid-pitch drive pin or lug constructed in accordance with the present invention.
  • the track link section generally shown at 11 is somewhat conventional and comprises a pair of links 12 which are retained in spaced relationship by a pair of track bushings 14 fitted about the outer diameter of a pair of track pins 16, which are received in bores 17 of the links 12.
  • a track shoe 18, provided with the usual grouser 19 extends across the bottom of the links 12 and is secured to each of the links by a plurality of bolts 20.
  • the mid-pitch drive pin or lug is shown at 22 and is disposed at a central point midway between the track pin bushings 14.
  • the mid-pitch drive lug 22 is rigidly secured to the track shoe 18 by a plurality of bolts shown at 23.
  • FIG. 2 also illustrates a portion of a driving sprocket 26 and the manner in which the mid-pitch lug co-acts with the sprocket 26 which will be more fully explained hereinafter.
  • FIG. 3 illustrates a typical prior art construction which may be compared with the mid-pitch drive construction of FIG. 4 to illustrate how the construction of FIG. 4 results in a reduction of impact energy loss caused when the driven member strikes the sprocket.
  • FIG. 3 a section of track (track link) denoted by the articulating bushing connections A and B is shown entering upon a driving sprocket.
  • the trailing bushing portion B moves inwardly toward the sprocket center at a given velocity.
  • impact of the trailing bushing B (schematically shown in phantom lines) with the driving sprocket takes place through a radius R emanating from the center of the leading bushing A of the articulated joint. Since the radius R is relatively large, the impact velocity of the bushing B with the driving sprocket is also relatively large depending upon the rotative speed of the sprocket.
  • FIG. 4 depicts a mid-pitch drive construction according to the present invention schematically showing the point of impact (in phantom lines) of an articulated track section as it enters upon a driving sprocket.
  • the driven element of the articulated track section comprising bushings A and B is the mid-pitch lug member C located midway between the bushings A and B.
  • Another advantage of the invention resides in the power savings realized from the present mid-pitch construction which permits a special type of rocking action by the chain link as it enters upon the drive sprocket.
  • the particular type of rocking action produced by the present mid-pitch construction produces a horsepower savings over conventional structures by reducing the chordal action or the total distance through which the incoming chain link must travel as it enters upon the driving sprocket.
  • FIG. 5 a conventional prior art section of track denoted by the articulating bushing connection A, B and D, is shown entering upon a driving sprocket.
  • Bushing B has just seated on the sprocket, and as the sprocket rotates the center line of bushing B follows the are described by the pitch radius. After the bushing B seats on the sprocket and the sprocket continues to rotate the bushing B assumes the phantom line position 0 and the effective pitch radius for purposes of calculating the velocity of the bushing increases from P to P.
  • the incoming chain must accelerate and decelerate with each engagement of a new section of chain and the amount of acceleration and deceleration is related to the change in effective pitch radius as each bushing travels the path from B to O to A. It will, therefore, be appreciated that the incoming track in such prior art constructions is accelerated and decelerated with each bushing engagement with concomitant power loss due to the energy expended during such acceleration and deceleration.
  • FIG. 6 a mid-pitch drive construction according to the present invention is schematically shown an instant after the mid-pitch drive lug C thereof has contacted the driving sprocket. Summation of moments about the center of mid-pitch lug C shows a sizable applied clockwise moment caused by the chain load as shown. A resistive counterclockwise moment must occur for equilibrium and the bushing A moves until it bottoms out against the sprocket.
  • FIG. 7 The actual position of an entering mid-pitch drive section of the preferred construction is shown in FIG. 7. That portion of the track already on the driving sprocket will adjust itself accordingly. As the sprocket rotates through the articulation angle which is approximately 28 to 30, bushing B takes the position formerly occupied by bushing A. In order for this change of position to take place, some rocking action must occur. This rocking is compatible with the applied moment throughout the articulation angle. For approximately the first 7 of articulation a clockwise moment caused by the chain load keeps the bushing B away from the sprocket.
  • FIG. 9 shows by way of comparison the distance E which represents the chordal movement of conventional prior art articulated track link sections as compared with the distance F which represents the chordal action of mid-pitch drive constructions according to the present invention.
  • the net savings or reduction in chordal action of the mid-pitch drive construction over conventional track link constructions is shown by reference letter G.
  • FIG. 10 illustrates a prior art construction entering upon a driving sprocket when the tractor is in reverse.
  • the articulated joints of conventional prior art chain constructions are subjected to a high degree of bushing wear, especially when the tractor moves in reverse, due to a phenomenon generally referred to as scrubbing.
  • This scrubbing action consists of relative rotation between the bushing and the notched portion of the driving sprocket as will now be described with respect to FIG. 10.
  • Bushing A has just seated on the sprocket and its motion now starts to leave a linear path and enter into a curvilinear path. Note that the reference marks between bushing A and the sprocket are in line.
  • FIG. 11 It can be readily observed from FIG. 11 that this scrubbing action is substantially reduced, if not almost entirely eliminated, in the mid-pitch drive construction of the present invention.
  • lug C has just seated on the sprocket. Note that the reference marks between lug C and the sprocket are in line. As the sprocket rotates in reverse through the angle 0, lug C moves to the position of lug K. Even though the lug C undergoes a limited amount of rocking, the reference marks at the lug K location are still substantially in line indicating the substantial elimination of scrubbing action.
  • the articulating bushings A and B experience little or no external wear because these articulating bushings contact the sprocket for only a brief period during the critical portion of the driving cycle when detrimental scrubbing action occurs.
  • the mid-pitch drive construction of the instant invention drastically reduces external wear on the articulating bushings and results in a minimal amount of wear on the easily replaced mid-pitch drive lug member. This is accomplished notwithstanding a slight amount of rocking action which rocking action results in track horsepower saving due to a reduction of power losses through impact, reduced chordal action, and power saved through the elimination of scrubbing action.
  • mid-pitch drive can be designed, however, as will be noted from the subsequent description, some configurations have definite advantages over others.
  • the most important factors in mid-pitch drive constructions relate to (l) the relationship of the mid-pitch drive lug center point to the centers of the articulated joints, and (2) the degree of clearance or degrees of rocking provided between the driving sprocket and the articulating bushings. Either or both of these factors can alter the performance of mid-pitch drive construction.
  • the preferred constructrons are those depicted in FIGS. 2 and 6 wherein the center point of the mid-pitch drive lug is located either on or radially outwardly of a straight line drawn between the centers of the articulating bushings (bushings 14 in FIG. 2 and bushings A and B in FIG. 6).
  • the center of curvature of the cylindrical top portion of the mid-pitch lugs should be located on or below a straight line drawn between the centers of the pins at the articulated joints on each side of the lugs.
  • the incoming bushing B is prevented from having a significant counterclockwise moment about the center point of midpitch drive lug C, caused by the force of the chain load, from engaging with the sprocket during the portion of the driving cycle when detrimental scrubbing action would occur.
  • FIG. 12 illustrates a mid-pitch drive lug construction wherein the center point of the drive lug C is located radially inwardly of a straight line drawn between the centers of the articulating bushings A and B".
  • summation of forces at the center point of mid-pitch drive lug C results in an applied counterclockwise moment thereabout due to the force of the chain load.
  • This applied counterclockwise moment exists throughout the articulation angle and causes scrubbing action or external wear on the articulating bushing B". This scrubbing action occurs especially in reverse because the trailing bushing bottoms out against the sprocket near the beginning of the articulation angle and stays in this position until it reaches the position formerly occupied by the leading bushing.
  • midpitch drive construction of FIG. 12 possesses advantages over conventional prior art constructions due to a reduction in power losses caused by impact and reduced chordal action, it is nonetheless not as advantageous as those mid-pitch drive constructions wherein the center point of the mid-pitch drive lug is located at or radially outwardly of a straight line drawn between the centers of the articulating bushings as previously described.
  • FIG. 13 shows a mid-pitch drive construction in accordance with the present invention wherein the particular articulated connection in question is shown in a neutral position with respect to the driving sprocket.
  • the rocking angle is measured between a line drawn between the center point of the lug C and the center of the trailing bushing B when the bushing is at its maximum outward position and a line drawn between the center points of lug C and bushing B after the bushing has rocked to a bottomed out position with respect to the sprocket.
  • This rocking angle is denoted oz in FIG. 13. Studies have indicated that the rocking angle should not exceed approximately 20 and preferably should be about 12 for best results.
  • FIG. 14 illustrates a modified embodiment of the invention which is similar to that shown in FIGS. 1 and 2.
  • the mid-pitch driving lug is bolted as at 31 across the track links 32 rather than directly to the track shoe 34.
  • FIG. 15 illustrates another embodiment wherein a removable mid-pitch driving lug 36 is provided with a projection 38 which fits in a slot 40 formed in the track shoe 42.
  • the tongue or projection could be formed on the track shoe rather than the lug and could be of any suitable shape to lend rigidity to the structure.
  • FIG. 16 illustrates a driving lug embodiment wherein a mid-pitch driving lug 44 is provided with a removable wear tip portion 46.
  • the tip portion 46 may be formed of harder material than the base portion 44.
  • FIG. 17 illustrates an embodiment wherein the midpitch driving lug comprises two driving elements 48 one of which is shown for attachment to link 50 as by bolts 52.
  • This embodiment allows for the provision of a gap between the driving elements 48 whereby dirt may escape from between the two driving elements.
  • the track shoe is provided with an aperture to allow the dirt to pass outwardly through the assembly.
  • FIG. 18 illustrates an embodiment wherein the midpitch driving lug 54 is hollow and is attached to a raised portion 56 of the track shoe by bolts 58.
  • FIG. 19 illustrates an embodiment wherein the midpitch driving lug takes the form of a pin 60 press fitted into bores formed in the track links 62.
  • This embodiment has excellent rigidity due to the nature of the press fits. It is also possible to retain the pin 60 by suitable hinged joints to permit the pin to be rotated as wear occurs and then tightened again without disassembling the chain.
  • each articulated element of said track comprises a pair of laterally spaced apart links having a track shoe connected thereto and extending across the bottom thereof, and wherein said articulated elements are hingeably connected to adjacent elements by a cylindrical pin fitted through aligned bores in said links, said pin having an external cylindrical bushing fitted thereabout, the improvement comprising, a mid-pitch driving lug for each articulated element located centrally of said track shoe and generally equidistant the centers of said track pins, said mid-pitch lug having a cylindrical top portion shaped to cooperate with the correspondingly configured notches in the driving sprocket so that relative rocking movement may occur when the mid-pitch lug enters and leaves the notches of the driving sprocket; and wherein the cylindrical bushings at the articulated joints have an outside diameter which
  • each articulated element of said track comprises a pair of laterally spaced apart links having a track shoe connected thereto and extending across the bottom thereof, and wherein said articulated elements are hingeably connected to adjacent elements by a cylindrical pin fitted through aligned bores in said links, said pin having an external cylindrical bushing fitted thereabout, the improvement comprising, a mid-pitch driving lug for each articulated element located centrally of said track shoe and generally equidistant the centers of said track pins, said mid-pitch lug having a cylindrical top portion shaped to cooperate with the correspondingly configured notches in the driving sprocket, said top portion of the mid-pitch lug extending upwardly from the track shoe to a height greater than the height of the cylindrical bushings, said cylindrical bushings having a smaller outside diameter than the diameter
  • each said link comprising: a pair of laterally spaced and vertically disposed side bars each presenting an upper rail portion, parallel pin and cylindrical bushing elements secured to and interconnecting corresponding opposite ends, respectively, of said side bars, a track shoe, connecting means releasably securing said shoe to the bottoms of said side bars, and a drive lug releasably secured to said shoe independently of said side bars and elements and disposed laterally between said side bars and intermediate the axes of said pin and bushing elements, said drive lug having front and rear convexly curved sprocket engaging surfaces facing in diverging d1- rections and extending laterally substantially the full distance between said side bars, the top of said drive lug being of less height than said rail portions and lying substantially above the plane formed by said parallel axes, said sprocket engaging surfaces of said drive lugs being more gradually curved than said bushing
  • tongue and groove means are provided between said mid-pitch driving lug and said track shoe for providing a more rigid connection therebetween.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
  • Gears, Cams (AREA)
  • Agricultural Machines (AREA)
  • Chain Conveyers (AREA)
US669218A 1967-09-20 1967-09-20 Articulated chain assembly Expired - Lifetime US3567294A (en)

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US66921867A 1967-09-20 1967-09-20

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US669218A Expired - Lifetime US3567294A (en) 1967-09-20 1967-09-20 Articulated chain assembly

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US (1) US3567294A (es)
BE (1) BE720995A (es)
CA (1) CA926451A (es)
DE (1) DE1780484C3 (es)
ES (1) ES358286A1 (es)
FR (1) FR1580717A (es)
GB (1) GB1229874A (es)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3680929A (en) * 1970-09-02 1972-08-01 Caterpillar Tractor Co Mid-pitch drive lug for track link of endless track
US3897980A (en) * 1974-04-05 1975-08-05 Caterpillar Tractor Co Sprocket tooth engaging track noise suppression means
US4030782A (en) * 1976-06-25 1977-06-21 J. I. Case Company Crawler tractor track chain drive assembly
USRE29718E (en) * 1973-11-30 1978-08-01 Caterpillar Tractor Co. Resilient mid-pitch lug for an endless track
US4159857A (en) * 1978-05-30 1979-07-03 Caterpillar Tractor Co. Track assembly with mid-pitch drive lug and replaceable rail
WO1981000544A1 (en) * 1979-08-27 1981-03-05 R Livesay Chain with mid-pitch drive and replaceable bushing
US4449758A (en) * 1982-02-01 1984-05-22 Deere & Company Sprocket receptacle cleaner embodied in a track section
US5853233A (en) * 1988-03-18 1998-12-29 Turner; Robert John Crawler track assembly
US6139121A (en) * 1995-05-10 2000-10-31 Bridgestone/Firestone, Inc. Positive drive rubber track
US6536853B2 (en) * 2001-04-20 2003-03-25 Caterpillar Inc Arrangement for supporting a track chain of a track type work machine
US20030141760A1 (en) * 2002-01-31 2003-07-31 Teiji Yamamoto Rotary bushing type crawler track
US20030151305A1 (en) * 2002-02-12 2003-08-14 Komatsu Ltd. Travel driving apparatus for a track-type vehicle
US20100146925A1 (en) * 2008-12-12 2010-06-17 Eric James Johannsen Master link for a track chain

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6354679B1 (en) * 2000-04-20 2002-03-12 Caterpillar Inc. Off-set symmetrical link and an associated subassembly for a track chain assembly
CN108974414B (zh) * 2018-01-30 2024-04-26 湘潭大学 一种药品包装盒封底盒装置

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3680929A (en) * 1970-09-02 1972-08-01 Caterpillar Tractor Co Mid-pitch drive lug for track link of endless track
USRE29718E (en) * 1973-11-30 1978-08-01 Caterpillar Tractor Co. Resilient mid-pitch lug for an endless track
USRE29723E (en) * 1973-11-30 1978-08-08 Caterpillar Tractor Co. Resilient mid-pitch lug for an endless track
US3897980A (en) * 1974-04-05 1975-08-05 Caterpillar Tractor Co Sprocket tooth engaging track noise suppression means
US4030782A (en) * 1976-06-25 1977-06-21 J. I. Case Company Crawler tractor track chain drive assembly
US4159857A (en) * 1978-05-30 1979-07-03 Caterpillar Tractor Co. Track assembly with mid-pitch drive lug and replaceable rail
EP0005895A1 (en) * 1978-05-30 1979-12-12 Caterpillar Tractor Co. Track assembly element for a crawler vehicle
US4306753A (en) * 1979-08-27 1981-12-22 Caterpillar Tractor Co. Articulated chain with mid-pitch drive and replaceable drive bushing
WO1981000544A1 (en) * 1979-08-27 1981-03-05 R Livesay Chain with mid-pitch drive and replaceable bushing
US4449758A (en) * 1982-02-01 1984-05-22 Deere & Company Sprocket receptacle cleaner embodied in a track section
US5853233A (en) * 1988-03-18 1998-12-29 Turner; Robert John Crawler track assembly
US6139121A (en) * 1995-05-10 2000-10-31 Bridgestone/Firestone, Inc. Positive drive rubber track
US6536853B2 (en) * 2001-04-20 2003-03-25 Caterpillar Inc Arrangement for supporting a track chain of a track type work machine
US20030141760A1 (en) * 2002-01-31 2003-07-31 Teiji Yamamoto Rotary bushing type crawler track
US6866351B2 (en) * 2002-01-31 2005-03-15 Komatsu, Ltd. Rotary bushing type crawler track
US20030151305A1 (en) * 2002-02-12 2003-08-14 Komatsu Ltd. Travel driving apparatus for a track-type vehicle
US6733092B2 (en) * 2002-02-12 2004-05-11 Komatsu Ltd. Travel driving apparatus for a track-type vehicle
US20100146925A1 (en) * 2008-12-12 2010-06-17 Eric James Johannsen Master link for a track chain
US7877977B2 (en) 2008-12-12 2011-02-01 Caterpillar Inc. Master link for a track chain

Also Published As

Publication number Publication date
FR1580717A (es) 1969-09-05
ES358286A1 (es) 1970-04-16
DE1780484C3 (de) 1979-06-21
GB1229874A (es) 1971-04-28
CA926451A (en) 1973-05-15
DE1780484A1 (de) 1972-02-03
BE720995A (es) 1969-03-17
DE1780484B2 (de) 1978-10-26

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Owner name: CATERPILLAR INC., A CORP. OF DE.,ILLINOIS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515

Owner name: CATERPILLAR INC., 100 N.E. ADAMS STREET, PEORIA, I

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST.;ASSIGNOR:CATERPILLAR TRACTOR CO., A CORP. OF CALIF.;REEL/FRAME:004669/0905

Effective date: 19860515