CA1082264A - Improvements in the construction of chainlinks of endless tracks for track vehicles - Google Patents
Improvements in the construction of chainlinks of endless tracks for track vehiclesInfo
- Publication number
- CA1082264A CA1082264A CA275,577A CA275577A CA1082264A CA 1082264 A CA1082264 A CA 1082264A CA 275577 A CA275577 A CA 275577A CA 1082264 A CA1082264 A CA 1082264A
- Authority
- CA
- Canada
- Prior art keywords
- bolt
- flat
- connector
- contact surfaces
- curved
- 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
Links
Classifications
-
- 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
- B62D55/21—Links connected by transverse pivot pins
- B62D55/211—Bitubular chain links assembled by pins and double connectors
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Clamps And Clips (AREA)
- Devices For Conveying Motion By Means Of Endless Flexible Members (AREA)
- Mutual Connection Of Rods And Tubes (AREA)
- Connector Housings Or Holding Contact Members (AREA)
- Details Of Connecting Devices For Male And Female Coupling (AREA)
- Apparatus For Radiation Diagnosis (AREA)
- Steroid Compounds (AREA)
- Saccharide Compounds (AREA)
Abstract
ABSTRACT OF THE DISCLOSURE
This invention provides a caterpillar track, of which the chain links comprise tubular bodies arranged transversely to the direction of movement. The bodies are connected to the adjacent chain links by connector links and also by bolts which extend through the connector links and through the tubular bodies. The tubular bodies are so dimensioned transversely of the running direction that they support each other laterally.
This invention provides a caterpillar track, of which the chain links comprise tubular bodies arranged transversely to the direction of movement. The bodies are connected to the adjacent chain links by connector links and also by bolts which extend through the connector links and through the tubular bodies. The tubular bodies are so dimensioned transversely of the running direction that they support each other laterally.
Description
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"Caterpillar (trade mark) Track"
The instant invention relates to a caterpillar ttrade mark) track, the chain links of which comprise tubular bodies arranged transversely of the direction of movement and connected to the adjacent chain links, as seen in the direction of movement, by connector links as well as bolts which extend through' the connec-tor links and through the tubular bodies.
In operation the bolts extending through the tubular bodies and connector links are subjected to bending stresses which may be caused by the traction drive force acting transversely of the bolts in the direction of movement of the chain but may also have their origin in weight load acting in vertical direction at driving conditions at which the chain is supported on the ground at its edges only, for example when driving over a rut\or groove in the ground.
It is a principal aspect o~ the present inven-tion to design a caterpillar track of the kind de~ined such that its elements, in particular the bolts may have smaller dimensions and weight than hereto~ore possible to withstand and endure a given bending load.
It is another aspect of the invention to provide a chain link of smaller overall dimensions for a caterpillar track, thus enabling savings of material, manufacture and storage expenditure.
It is still another aspect o~ the invention to prevent the ends of the bolts used in a caterpillar track from slipping with respect to the corresponding connector links by providing for form-lock or friction-lock engagenlent of the bolts end.
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. I ~ 2 Accordingl~, this invention provides connector means for connecting together the adjacent ends of successive chain links of an endless track, comprising:
~a) an end connector mem~er containing trans-versely extending through openings at its forward and rear ends, respectively, each of said through openings including (1) a curved first inner wall contact surface which comprises, in transverse cross-section, a segment of a circle, and
"Caterpillar (trade mark) Track"
The instant invention relates to a caterpillar ttrade mark) track, the chain links of which comprise tubular bodies arranged transversely of the direction of movement and connected to the adjacent chain links, as seen in the direction of movement, by connector links as well as bolts which extend through' the connec-tor links and through the tubular bodies.
In operation the bolts extending through the tubular bodies and connector links are subjected to bending stresses which may be caused by the traction drive force acting transversely of the bolts in the direction of movement of the chain but may also have their origin in weight load acting in vertical direction at driving conditions at which the chain is supported on the ground at its edges only, for example when driving over a rut\or groove in the ground.
It is a principal aspect o~ the present inven-tion to design a caterpillar track of the kind de~ined such that its elements, in particular the bolts may have smaller dimensions and weight than hereto~ore possible to withstand and endure a given bending load.
It is another aspect of the invention to provide a chain link of smaller overall dimensions for a caterpillar track, thus enabling savings of material, manufacture and storage expenditure.
It is still another aspect o~ the invention to prevent the ends of the bolts used in a caterpillar track from slipping with respect to the corresponding connector links by providing for form-lock or friction-lock engagenlent of the bolts end.
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. I ~ 2 Accordingl~, this invention provides connector means for connecting together the adjacent ends of successive chain links of an endless track, comprising:
~a) an end connector mem~er containing trans-versely extending through openings at its forward and rear ends, respectively, each of said through openings including (1) a curved first inner wall contact surface which comprises, in transverse cross-section, a segment of a circle, and
(2) a flat second inner wall contact surface, said contact surfaces extending the length of said through opening; and (b) a pair o~ cylindrical rod members extending at one end within said openings, respectively, each of said rod members having on its outer periphery (1) a curved first outer wall contact surface in contiguous frictional engagement with said first inner wall contact surface, and (2) a flat second outer wall contact surfàce in contiguous frictional engagement with said second inner wall contact surfacè, whereby said contact surfaces cooperate to prevent rotation of said rod mem~er relative to said end connector member;
(c) each of the cu~ved and flat contact surfaces of one of said members containing at least one groove, whereby when th~ corresponding curved and flat contact surfaces are pressed tightly together in tight frictional engagement foreign matter is removed from the contact surfaces to produce a large constant frictional force between the members for preventing axial displacement of the rod member relative to the connector link.
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~' ' ' ' -2a-In this manner overload protection of the bolts is obtained which permits the desired smaller dimensions to be applied at given permissible bending loads. With a caterpillar track according to the inven-tion, starting with the predetermined flexure causedespecially by vertical bending stress, for instance, by the weight of a vehicle equipped with the caterpillar track, it is no longer the bolts alone which accommo-date the bending load but, in addition, also the tubular bodies and, if desired, the connector links. Thus the bolts enjoy partial relief of the bending stress so that they may be designed weaker in diameter. In the same manner also the dimensions of the bores which receive the bolts in the tubular bodies and determine the dimen-sions of the tubular bodies and the bores in the connectorlinks may be made smaller. This permits a smaller overall size of the chain link and thus offers savings in material, manufacture, and storage expenditure. This is achieved simply by mutual fitting of the tubular bodies and/or connector links transversely of the direction of movement, i.e. in their longitudinal extension. In practice a clearance will be provided within such limits of tolerance between the tubular bodies and/or the connector links as will be taken up from the predeter-mined flexure on. In the critical case in which the predetermined flexure is zero, the tubular bodies and/or connector links already abut each other laterally even when not subjected to loading so that from the very beginning the bolts are subjected to less bending stress.
In a caterpillar track in which the tubular bodies and/or connector links include webs extending into spaces between adjacent elements oE a chain link or between two successive chain links, as seen in running direction, so as to enlarge the roll-off surface for the chain wheels and thus afford smoother running, the tubular bodies and/or connector links may support each other laterally through those webs which are dimensioned or fitted accurately in the direction of movement as well as transversely thereof. With known caterpillar tracks a retaining force between the bolt ends and the end connectors usually is obtained by clamping the two halves of an end connector of divided or integral structure against each other by means of a clamping bolt. Thereby the end connectors provided with recesses hold the bolt ends clamped, for instance, at flat sections of the bolt ends and connectors abutting each other and extending parallel with the axis. The frictional retaining force thus established is limited. Yet it is suffic-ient when it is not necessary to transmit axial forces betweenthe bolts and the end connectors. However, if also axial forces must be transmitted and if slipping of the bolts in their longitudinal direction with respect to the end connectors is to be prevented particularly with a caterpillar track provided with the above mentioned kind of lateral support of the tubular bodies and/or the connector links according to the invention, the retaining force generated in the known manner is not sufficient. This is so because, on the one hand, the axial forces between the bolts and the end conne ~ rs may become very large and, on the other hand, because the tighten-ing torque of the clamping bolt and the coefficient of friction between the bolts and the end connectors, which two parameters determine the magnitude of the retaining force, cannot be kept constant in practice.
Assembling is rendered difficult by the need for constant accurate adjustment according to specification of the tightening torque and is practically impossible under the rough actual conditions of replacement of chain elements in practice. Moreover, it cannot be avoided with the known design that lubricant or dirt particles enter between the frictionfaces when mounting or exchanging chain elementsO Consequently the coefficient of friction varies uncontrollably. Thus the tightening torque prescribed for a certain coefficient of friction does not correspond to the respective coefficients !
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of friction prevailing in actual practice. Undesired slipping of the bolts relative to the end connectors may be the result so that the end connectors and/or bolts will no longer have the proper operating positions. This may be the cause of uneven running and damages of the track.
Therefore, it is another aspect of a preferred form of the present invention to design a caterpillar track of the kind defined initially such that the bolt ends are prevented from slipping with respect to the end connectors which are disposed laterally of the caterpillar track to connect adjacent chain elements. This is particularly important with a cater-pillar track having the above described kind of lateral support devised by the invention because when a caterpillar track of such design bends, there is a strong tendency for the bolts to slip axially with respect to the end connectors. And this would entail all the disadvantageous consequences mentioned.
To solve this further problem it is-provided, in accordance with a preferred form of the invention, that in addition to being secured against rotation at least one bolt end of the two bolt ends associated with an end connector is further secured against uncontrolled axial slippage with respect to the corresponding end connector which is particularly advantageous with a caterpillar track having the lateral support described above between the tubular bodies and the end connectors, when this track is subjected to bending stress.
The embodiments below demonstrate the great variety of form-. : , ' . ' -' . , . . ,:
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and friction-lock connections which can be used -to realize the invention. In a preferred embodiment of a form-lock connection a bu3hing or sleeve functioning as fitting piece and having flat sections at two side~, especially flat section~
inclined in two directions, i9 pressed against corresponding flat sections at the bolt ends~ particulary by means o~ a clamping .bolt or screw con~ecting t~e bushing with the end conneotor.
The fitting piece may be a fitting part of a clamping bolt ~crewed into the end connector.
preferred embodiment In another/the fitting piece is a disc which fits into a slit between the halves or bridges of a conventional end connector and through which a screw passes centrally. ~y means of opposed pro~ections this disc engages in transverse grooves in the bolt ~nda. ~hi~ embod$m~ p~aiall~ ~oo~omic~l b~o~u~ per-mits the use o conventional end connectorsiwi.thout any alteration and merely requires the disc a~ an ad~it~pnal member.
., A form-loc~ connection advantageously may also be realized a9 a bayonet connection.
In th~ case of a friction-lock connection the structure is to be design~d suchlthat a defined ~riction force is generated which positively ~urpasse~ axial displacement and/or tor~ional f orces G
Such frictional force is realized, for example~ by u;8ing wedgi.ng action in that very great normal forces giving rise to corre~ponding frictional force~ are produced between circum-~erential sur~ace~ o$ ~he bolt~ and end connectors by way o cone ~urface~ at the end connector and a pres~ure bol-t or separate ring tension element~0 The re~uired great frictional force 9 however9 may also be applied by ~imple contac~ pressure between face~ in parallel .
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~ 6 --with the axisO
In accordance with an alternative embodiment of the invention at least one recess or depre~sion is provided for this purpose 7 distributed around the circumferential ~urface, in the area o~ contact of the bolt and/or connector link.
This recess or these recesses form spaces which will take up lubricant from between the contact faces or extraneous matter, such as dust and dirt ~queezed out by the clamping action so that any foreign matter will be removed from the contact surfaces.
This makes it possible to realize in reproducible manner the greatest possible coefficient or friction which is predetermined by the materials of the bolt and the connector link.. :. .
As the frictional force transmitted is proportional to the co-efficie~t of friction and to the clamping force, the design according to the i~vention afford~ the greatestpos~ible ~rictiona~
force at any g~ven olamping force.
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The recesses may be provided either at the bolt or in the respecti~e openings o~ the end connectorst or in both. r~hey may be embodied9 ~or instance~ by longitudinal or helical groo~es in the manner o~ a coarse thread~ the tip~ o~
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the flank~ of the thread being cut of~so as to provide the contact surface bet~een the courses of the thread. ~urthermore the recesses or depressions may be formed by milling or lunurling~
e.gO cross hatchingO If longitudinal grooves are chos~,they should pr~ferably be machined in the end connector opening3 since this allows simple and inexpensive manufacture by broaching or similar removal technique~O
Preferably either the bolt ends or the openings in the connector links should be provided with the receRses because this is ~implex .
in production, affords clear contact surfaces, and fulfills the purpose of keeping the contact surfaces free of lubricant and foreign matter9 respectivelyg to full satisfac~ionO
Overload protection against undue stressing of the bolts which may occur9 for instance9 when the bolts are bent by the chain traction or when driving over uneven ground, can be obtained in accordance with another modification of the invention by designing the æecuring means against axial slippage such that a defined axial slipping between bolt end and end connector ~ against.a defined force, e g. of a separate spring i~ permitted up to a stop or abutment.
~ ' The invention will be described further, by wa~ of example, :. with xeference to the accompa~ing drawings which show different embod~ment~ and in which: .
~'ig. 1 is a perspective elevational view of a piece of a ~ . connector link chain inoluding tubular bodies and - connector links dimensioned acoording to the invention, . fig. 2 is a sectional elevation~ to an enlarged scale, along line II-II o~ fig. 1 e~tending along a bolt and showing : the assem.bly in a condition not sub~ected to bending ~ ~tres~, fig. 3 is a view similar to ~ig. Z, yet not in section, of a chain link in a po~i-tion above a groove in the ground, fig~ 4 i8 an elevat~onal view, to an enlarged scale~ of a ,:
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connector link and parts of the chain link, a~ seenin the directio~ of arrow A of fig. 1~
fig~ 5 is a perspective view of a piece of a connector link chain according to another em~odiment of the invention, fig. 6 ~8 a longitudlnal ~ectional view of a bolt along lin~
VI VI of figo 5~
~igo 7 is a graph demonstrating the bending load P~~othet~heain vertical flexure ~ of the chain link, figo 8 is a sectional view of a connection between the bolt ends and an end connector according to the invention9 figo 9 is a top plan view of the connection shown in fig. 8, ~ig~ 10 i8 a sectional view taken along line X-X in figo 8 with a bolt omitted~
figo 11 is a sectional view similar to fig. 8 showing a modified connection according to the invention~
~;lg~ 12 i~ ~ p~l~pe~ve exploded view o;~ a~ end ~on~e~t~r ~nd.
-~ a wedge piece of another modified connection according to the in~ention,~ I
figo 13 is a top plan view of a connection using the elements shown in fig. 12, ~igo 14 is a sectional view ~imilar to fig~ 8 showing anothex connection according to the invention, figo 15 is a perspective view o~ a member of the connection shown in fig. 14~
fig. 16 is a ~ectional view similar to fig. 8 ~howing a further embodiment of connections according to the invention additionally illustrating a bolt end adapted to the respective connection, ~igs. 17 to 20 are sectional view~ of bolt ends Of further embodiments of connections according to the invention, fig. ~21 is a sectional view, tran~versely of the bolt ends, of a corresponding end connector, fig. 22 is a secti~nal view taken along line XXII-XXII in fig~ 23 of another connection according to the invention fi~. 23 is a 6ectional view taken along line XXIII-XXIII in fig. 2a, . ' ' ' '., . ' ~:' .
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fig. 24 is a part sectional view of a bolt end as example of a friction-lock connection according to the invention fig. 25 is an exploded view of the bolt end and a sectional view of the bore of an end connector of bayonet con-nection according to the invention9 figs. 26 and 27 are a sectional and top plan view, partly sectioned, of another connection according to the invention, fi~. 28 is a perspective exploded view of an end connector and two bolt ends of different design with recesse~
according to the invention, .. . : .
fig. 29 is a perspective exploded view of an end connector, the openings of which are provided with recesses according to the invention9 and of a corresponding bolt.
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In each chain link-the connector link chain shown ~n fi~. 1 comprises two tubular bodie~.1 with running pads 2 at their underside~ two end connector links 3 at either side of the chain, and an intermediate connector link 5 with a chain tooth 4 guiding the vehicle by means of the .~.read rollers 12 which roll-off the plane roll-off surfaces 11 of the tubular boaies 1.
~ach chain li~ generally designated 7 is connec.ted to the successi~e chain link 7 through the connector links ~, 5 by means of bolts ~ which extend through the connector links and the tubular bodiesO
In the axea in which bolt 8 passes through the tubular bodies 1 a plurality of rubber sleeve~ 9 which have an excess dimension as compared to through bores 10 in the tubular bodies 1 ar0 fixed on the bolts by vulcanization. ~ogether with their ~ubber sleeves 9 fixed by vulcanization the bolts ~ are pressed into the through bores 10, As the rubber ~leeves are capable of .twisting, they permit tilting of the bolts 8 in the through bores 10 by the angles neceesary for turning of the ch~in.
~he tubular bodie~ 1 and the connector link.s ~ 5 are accurately dimensioned in a direction transversely of the direction of movemènt C of the chain so that accurate clearance a within manufaoturing tolerances is obtained between the tubular bodies :
and the connec-tor links when the chain links are not ~ubjected to vertical bending load. . :
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When a ~ehicle equipped with the caterpillar,track according to fig~o 1 and 2 drive~ over a rut or groove H in the ground (fig. 3)9 the bolts.~ deflect in the manner shown exaggeratedly in fig. 3. Beginning with a degree of flexure which can be predetermined the clearance a i~ cancelled in the upper zone at/ ~ ;
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x because of the bending deformation so that upon further increase of the bending load the tubular bodie~ 1 and the connector links 3~ 5 constitute a supporting bridge which contributes to taking up the bending stress~ and relieves the bolts of bending. r~he end connector links 3 are retained on the ends 13, 1~ of bolt 8 not only against rotation but al~o against longitudinal displacement in order to prevent these ends 13 7 14 of the bolt 8 from slipping inwardly of the end connector link~ 3 in the loaded condition shown in fig. 3.
. For this purpose -the ende 13 9 14 of bolts 8 are provided with flat sections 15, 16 which cooperate with corresponding flat sections in the end connector links, as shown in figs. 2 and 4.
~t the left end, as seen in figure 2, these flat sections 15 extend obli~uely with respect to the longitudinal axis of the bol~ ~o ~ha~ ~h~ end aonne~.~o~ ar~ held under wedging ~ction i.e. in form lock against slipping of the bolts inwardly. ~his guarantees that the bolt ends are securely held, which are thus expanded in their longitudinal extension upon further increase of the bending stress, However~ it showed~ that even with flat section~ 16 extending parallel to the long~tudinal axis of the bolts, such as ~hown for the right end 14 of the bolt, as seen in the drawing, sufficient force can be applied merely by friction-lock establishing contact pressure of the corresponding flat section~
of the connector link 3 to prevent the bolts from slipping out, . .
provided corxesponding measures are taken, e.g..tho~e illustrated in figs. 28 and 29 and explained in the description of those . figure~O
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- In practice, of course, for reasons of economy preferably either the left or the right alternati~e shown in figure 2 or one of the other alternatives descrlbed belo~ is ~elected to xeal~ze the flat sectio~s at both bolt end~9 depending on . the respective use o~ the ~hain.
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_ 12 -~he one-piece end connector links 3 have a slit 17 merging a~ either end into through bores 18 which serve to recei~e the bolt ends 13 and 14 9 respectively~ and being enclosed all around~
As may be taken from ~igure 49 the two opposed material bridges 19 9 20 at ei*her side of ~lit 17 can be contracted by means of a screw 210 Hereby the contact pressure can be produced which is required to preas the flat sections in through bores 18 against the fla~ ~ections 15~ 16 of bolt ends 1~ 14.
The end connector links ~ may also be divided in longitudinal direction.
It is also possible to provide a greater even number of tubular bodie~ 1 for each chain link instead of only two~ In that case~
apart from the center which again contains an intermediate connecto~ k 5 pxovided with a chain taot~ 41 intermediatc connector links similar to the end connector links 3 are inserted between the individual tubular bodies. ~hese inter mediate connector links have surfaces which are flush with the sur~aces 11 of the tubular bodies to increase the roll-of surface for the correspondingly wider tread rollers, thus contributing to improve the smooth running. When it is desired to enlarge the chain, this type of structure i~ preferred in that it of~ers more convenient storage and savings of weight and mate~ial as compared to a structure employ~ng wider structural elements, especially wider tubular bodies. It is to be under-stood that even with such a wider chain having a correspondingly greater number of tubular bodies and connector links~ these elementæ are accurately dimensioned in a direction transversely of the running direction of the chain so that~ beginning with a predetermined ~le~ure~ the tubular bodies and the connector links support each other and again form a bridge protecting the bolts from excessi~e bending stress.
Figure 5 likewise ~hows an embodiment o~ a chain which is wider than the embodiment according to figure 1 but which comprises three tubular bodies~ in other word3 an uneven number o~ tubular bodies per chain linkO Just like the tubular bodie~
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22~9 _ 13 _ 1 the tubular bodie~, designated in general by reference numeral 41, have through bores 42 to receive boltr 44 provided with rubber sleeves 43 which are fixed on the bolts by vul-canization. In this case the rubber sleeves mentioned are also provided in a central tubular body 41 which carries a chain tooth 60. On principle the bOltsa 44 are of the same structure as bolts B of the embodiment shown in figures1 to4 .In thi3 case~ too~ measures are taken to secure the bolt ends 47 and the end connectors 48 against relative rotation and axial slipping~
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~he embodiment according to figure-a. 5,6 compr.ises divided intermediate connector links 55 o~ which only the upper part is to be seen. The lower p æt is adapted to be clamped agains~
the upper par~ and at the same time a~ain$t the bolts 44 by means o~ ~crews 56. ~he parts of the lntermed~ate connectors 55 together form recesses or openings which, in assembled condition, surround approximately three quarters of the total circumference of the bolts in the areas 54 in which they are free of the rubber sleeves 53. The intermediate connector links may have areas 57 which extend trans~er~ely of the running direction of the chain between adjacent tubular bodies 41 and form a flush surface with the surfaces 58 of the tubula~
bodies 41~ But satisfactory sm~thhr~nning can be obtained also without such area~ 57. ~ikewise ~ith these surfaces 58 i8. the surface of webs 59 which extend from the central tubular bodies 41 toward both sides to the ~acent tubular bodie~ 41 trans-ver~ely of the running direction of the chain~ These webs 59 do not reach as far a~ the overall dimension of the tubular bodie~
41 in the running direction of the chain but instead leave spaces into which extend webs 61 provided at intermediate connector links 55 and oriented in running direction and in a direction opposed to the same~ respectively~
~he dimensio~ o~ web~ 59 at central tubular body 41 and of web~ 57 and ~1 at intermecliate connectors 55 (to be seen only ~, . .
_ . ., ... , ., .. ... , . ~ . ... -in figure 5 bu-t not in figure 6) as well as the dimensions of the outer tubular bodies 41 and of the end connector link~ 48 in a direc-tion transversely of the running direction of the chain are ~o selected that again a predetermined clearance a is obtained which, in the present case, is zero~ By vir-tue o~
this arrangement, upon vertical de~lection the bolts 44 are partly relieved from the very beginning from bending stxess.
Structural elements such as sho~n in figure 5 can also be used to make wider chains with a greater uneven number o~ tubular -bodies per chain link.
Figure 7 shows the course o~ a bending load P of the chcin above t bending flexure f of a chain link such as shown in ~igures 1 to
(c) each of the cu~ved and flat contact surfaces of one of said members containing at least one groove, whereby when th~ corresponding curved and flat contact surfaces are pressed tightly together in tight frictional engagement foreign matter is removed from the contact surfaces to produce a large constant frictional force between the members for preventing axial displacement of the rod member relative to the connector link.
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~' ' ' ' -2a-In this manner overload protection of the bolts is obtained which permits the desired smaller dimensions to be applied at given permissible bending loads. With a caterpillar track according to the inven-tion, starting with the predetermined flexure causedespecially by vertical bending stress, for instance, by the weight of a vehicle equipped with the caterpillar track, it is no longer the bolts alone which accommo-date the bending load but, in addition, also the tubular bodies and, if desired, the connector links. Thus the bolts enjoy partial relief of the bending stress so that they may be designed weaker in diameter. In the same manner also the dimensions of the bores which receive the bolts in the tubular bodies and determine the dimen-sions of the tubular bodies and the bores in the connectorlinks may be made smaller. This permits a smaller overall size of the chain link and thus offers savings in material, manufacture, and storage expenditure. This is achieved simply by mutual fitting of the tubular bodies and/or connector links transversely of the direction of movement, i.e. in their longitudinal extension. In practice a clearance will be provided within such limits of tolerance between the tubular bodies and/or the connector links as will be taken up from the predeter-mined flexure on. In the critical case in which the predetermined flexure is zero, the tubular bodies and/or connector links already abut each other laterally even when not subjected to loading so that from the very beginning the bolts are subjected to less bending stress.
In a caterpillar track in which the tubular bodies and/or connector links include webs extending into spaces between adjacent elements oE a chain link or between two successive chain links, as seen in running direction, so as to enlarge the roll-off surface for the chain wheels and thus afford smoother running, the tubular bodies and/or connector links may support each other laterally through those webs which are dimensioned or fitted accurately in the direction of movement as well as transversely thereof. With known caterpillar tracks a retaining force between the bolt ends and the end connectors usually is obtained by clamping the two halves of an end connector of divided or integral structure against each other by means of a clamping bolt. Thereby the end connectors provided with recesses hold the bolt ends clamped, for instance, at flat sections of the bolt ends and connectors abutting each other and extending parallel with the axis. The frictional retaining force thus established is limited. Yet it is suffic-ient when it is not necessary to transmit axial forces betweenthe bolts and the end connectors. However, if also axial forces must be transmitted and if slipping of the bolts in their longitudinal direction with respect to the end connectors is to be prevented particularly with a caterpillar track provided with the above mentioned kind of lateral support of the tubular bodies and/or the connector links according to the invention, the retaining force generated in the known manner is not sufficient. This is so because, on the one hand, the axial forces between the bolts and the end conne ~ rs may become very large and, on the other hand, because the tighten-ing torque of the clamping bolt and the coefficient of friction between the bolts and the end connectors, which two parameters determine the magnitude of the retaining force, cannot be kept constant in practice.
Assembling is rendered difficult by the need for constant accurate adjustment according to specification of the tightening torque and is practically impossible under the rough actual conditions of replacement of chain elements in practice. Moreover, it cannot be avoided with the known design that lubricant or dirt particles enter between the frictionfaces when mounting or exchanging chain elementsO Consequently the coefficient of friction varies uncontrollably. Thus the tightening torque prescribed for a certain coefficient of friction does not correspond to the respective coefficients !
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of friction prevailing in actual practice. Undesired slipping of the bolts relative to the end connectors may be the result so that the end connectors and/or bolts will no longer have the proper operating positions. This may be the cause of uneven running and damages of the track.
Therefore, it is another aspect of a preferred form of the present invention to design a caterpillar track of the kind defined initially such that the bolt ends are prevented from slipping with respect to the end connectors which are disposed laterally of the caterpillar track to connect adjacent chain elements. This is particularly important with a cater-pillar track having the above described kind of lateral support devised by the invention because when a caterpillar track of such design bends, there is a strong tendency for the bolts to slip axially with respect to the end connectors. And this would entail all the disadvantageous consequences mentioned.
To solve this further problem it is-provided, in accordance with a preferred form of the invention, that in addition to being secured against rotation at least one bolt end of the two bolt ends associated with an end connector is further secured against uncontrolled axial slippage with respect to the corresponding end connector which is particularly advantageous with a caterpillar track having the lateral support described above between the tubular bodies and the end connectors, when this track is subjected to bending stress.
The embodiments below demonstrate the great variety of form-. : , ' . ' -' . , . . ,:
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and friction-lock connections which can be used -to realize the invention. In a preferred embodiment of a form-lock connection a bu3hing or sleeve functioning as fitting piece and having flat sections at two side~, especially flat section~
inclined in two directions, i9 pressed against corresponding flat sections at the bolt ends~ particulary by means o~ a clamping .bolt or screw con~ecting t~e bushing with the end conneotor.
The fitting piece may be a fitting part of a clamping bolt ~crewed into the end connector.
preferred embodiment In another/the fitting piece is a disc which fits into a slit between the halves or bridges of a conventional end connector and through which a screw passes centrally. ~y means of opposed pro~ections this disc engages in transverse grooves in the bolt ~nda. ~hi~ embod$m~ p~aiall~ ~oo~omic~l b~o~u~ per-mits the use o conventional end connectorsiwi.thout any alteration and merely requires the disc a~ an ad~it~pnal member.
., A form-loc~ connection advantageously may also be realized a9 a bayonet connection.
In th~ case of a friction-lock connection the structure is to be design~d suchlthat a defined ~riction force is generated which positively ~urpasse~ axial displacement and/or tor~ional f orces G
Such frictional force is realized, for example~ by u;8ing wedgi.ng action in that very great normal forces giving rise to corre~ponding frictional force~ are produced between circum-~erential sur~ace~ o$ ~he bolt~ and end connectors by way o cone ~urface~ at the end connector and a pres~ure bol-t or separate ring tension element~0 The re~uired great frictional force 9 however9 may also be applied by ~imple contac~ pressure between face~ in parallel .
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~ 6 --with the axisO
In accordance with an alternative embodiment of the invention at least one recess or depre~sion is provided for this purpose 7 distributed around the circumferential ~urface, in the area o~ contact of the bolt and/or connector link.
This recess or these recesses form spaces which will take up lubricant from between the contact faces or extraneous matter, such as dust and dirt ~queezed out by the clamping action so that any foreign matter will be removed from the contact surfaces.
This makes it possible to realize in reproducible manner the greatest possible coefficient or friction which is predetermined by the materials of the bolt and the connector link.. :. .
As the frictional force transmitted is proportional to the co-efficie~t of friction and to the clamping force, the design according to the i~vention afford~ the greatestpos~ible ~rictiona~
force at any g~ven olamping force.
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The recesses may be provided either at the bolt or in the respecti~e openings o~ the end connectorst or in both. r~hey may be embodied9 ~or instance~ by longitudinal or helical groo~es in the manner o~ a coarse thread~ the tip~ o~
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the flank~ of the thread being cut of~so as to provide the contact surface bet~een the courses of the thread. ~urthermore the recesses or depressions may be formed by milling or lunurling~
e.gO cross hatchingO If longitudinal grooves are chos~,they should pr~ferably be machined in the end connector opening3 since this allows simple and inexpensive manufacture by broaching or similar removal technique~O
Preferably either the bolt ends or the openings in the connector links should be provided with the receRses because this is ~implex .
in production, affords clear contact surfaces, and fulfills the purpose of keeping the contact surfaces free of lubricant and foreign matter9 respectivelyg to full satisfac~ionO
Overload protection against undue stressing of the bolts which may occur9 for instance9 when the bolts are bent by the chain traction or when driving over uneven ground, can be obtained in accordance with another modification of the invention by designing the æecuring means against axial slippage such that a defined axial slipping between bolt end and end connector ~ against.a defined force, e g. of a separate spring i~ permitted up to a stop or abutment.
~ ' The invention will be described further, by wa~ of example, :. with xeference to the accompa~ing drawings which show different embod~ment~ and in which: .
~'ig. 1 is a perspective elevational view of a piece of a ~ . connector link chain inoluding tubular bodies and - connector links dimensioned acoording to the invention, . fig. 2 is a sectional elevation~ to an enlarged scale, along line II-II o~ fig. 1 e~tending along a bolt and showing : the assem.bly in a condition not sub~ected to bending ~ ~tres~, fig. 3 is a view similar to ~ig. Z, yet not in section, of a chain link in a po~i-tion above a groove in the ground, fig~ 4 i8 an elevat~onal view, to an enlarged scale~ of a ,:
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connector link and parts of the chain link, a~ seenin the directio~ of arrow A of fig. 1~
fig~ 5 is a perspective view of a piece of a connector link chain according to another em~odiment of the invention, fig. 6 ~8 a longitudlnal ~ectional view of a bolt along lin~
VI VI of figo 5~
~igo 7 is a graph demonstrating the bending load P~~othet~heain vertical flexure ~ of the chain link, figo 8 is a sectional view of a connection between the bolt ends and an end connector according to the invention9 figo 9 is a top plan view of the connection shown in fig. 8, ~ig~ 10 i8 a sectional view taken along line X-X in figo 8 with a bolt omitted~
figo 11 is a sectional view similar to fig. 8 showing a modified connection according to the invention~
~;lg~ 12 i~ ~ p~l~pe~ve exploded view o;~ a~ end ~on~e~t~r ~nd.
-~ a wedge piece of another modified connection according to the in~ention,~ I
figo 13 is a top plan view of a connection using the elements shown in fig. 12, ~igo 14 is a sectional view ~imilar to fig~ 8 showing anothex connection according to the invention, figo 15 is a perspective view o~ a member of the connection shown in fig. 14~
fig. 16 is a ~ectional view similar to fig. 8 ~howing a further embodiment of connections according to the invention additionally illustrating a bolt end adapted to the respective connection, ~igs. 17 to 20 are sectional view~ of bolt ends Of further embodiments of connections according to the invention, fig. ~21 is a sectional view, tran~versely of the bolt ends, of a corresponding end connector, fig. 22 is a secti~nal view taken along line XXII-XXII in fig~ 23 of another connection according to the invention fi~. 23 is a 6ectional view taken along line XXIII-XXIII in fig. 2a, . ' ' ' '., . ' ~:' .
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fig. 24 is a part sectional view of a bolt end as example of a friction-lock connection according to the invention fig. 25 is an exploded view of the bolt end and a sectional view of the bore of an end connector of bayonet con-nection according to the invention9 figs. 26 and 27 are a sectional and top plan view, partly sectioned, of another connection according to the invention, fi~. 28 is a perspective exploded view of an end connector and two bolt ends of different design with recesse~
according to the invention, .. . : .
fig. 29 is a perspective exploded view of an end connector, the openings of which are provided with recesses according to the invention9 and of a corresponding bolt.
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In each chain link-the connector link chain shown ~n fi~. 1 comprises two tubular bodie~.1 with running pads 2 at their underside~ two end connector links 3 at either side of the chain, and an intermediate connector link 5 with a chain tooth 4 guiding the vehicle by means of the .~.read rollers 12 which roll-off the plane roll-off surfaces 11 of the tubular boaies 1.
~ach chain li~ generally designated 7 is connec.ted to the successi~e chain link 7 through the connector links ~, 5 by means of bolts ~ which extend through the connector links and the tubular bodiesO
In the axea in which bolt 8 passes through the tubular bodies 1 a plurality of rubber sleeve~ 9 which have an excess dimension as compared to through bores 10 in the tubular bodies 1 ar0 fixed on the bolts by vulcanization. ~ogether with their ~ubber sleeves 9 fixed by vulcanization the bolts ~ are pressed into the through bores 10, As the rubber ~leeves are capable of .twisting, they permit tilting of the bolts 8 in the through bores 10 by the angles neceesary for turning of the ch~in.
~he tubular bodie~ 1 and the connector link.s ~ 5 are accurately dimensioned in a direction transversely of the direction of movemènt C of the chain so that accurate clearance a within manufaoturing tolerances is obtained between the tubular bodies :
and the connec-tor links when the chain links are not ~ubjected to vertical bending load. . :
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When a ~ehicle equipped with the caterpillar,track according to fig~o 1 and 2 drive~ over a rut or groove H in the ground (fig. 3)9 the bolts.~ deflect in the manner shown exaggeratedly in fig. 3. Beginning with a degree of flexure which can be predetermined the clearance a i~ cancelled in the upper zone at/ ~ ;
locations : .
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x because of the bending deformation so that upon further increase of the bending load the tubular bodie~ 1 and the connector links 3~ 5 constitute a supporting bridge which contributes to taking up the bending stress~ and relieves the bolts of bending. r~he end connector links 3 are retained on the ends 13, 1~ of bolt 8 not only against rotation but al~o against longitudinal displacement in order to prevent these ends 13 7 14 of the bolt 8 from slipping inwardly of the end connector link~ 3 in the loaded condition shown in fig. 3.
. For this purpose -the ende 13 9 14 of bolts 8 are provided with flat sections 15, 16 which cooperate with corresponding flat sections in the end connector links, as shown in figs. 2 and 4.
~t the left end, as seen in figure 2, these flat sections 15 extend obli~uely with respect to the longitudinal axis of the bol~ ~o ~ha~ ~h~ end aonne~.~o~ ar~ held under wedging ~ction i.e. in form lock against slipping of the bolts inwardly. ~his guarantees that the bolt ends are securely held, which are thus expanded in their longitudinal extension upon further increase of the bending stress, However~ it showed~ that even with flat section~ 16 extending parallel to the long~tudinal axis of the bolts, such as ~hown for the right end 14 of the bolt, as seen in the drawing, sufficient force can be applied merely by friction-lock establishing contact pressure of the corresponding flat section~
of the connector link 3 to prevent the bolts from slipping out, . .
provided corxesponding measures are taken, e.g..tho~e illustrated in figs. 28 and 29 and explained in the description of those . figure~O
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- In practice, of course, for reasons of economy preferably either the left or the right alternati~e shown in figure 2 or one of the other alternatives descrlbed belo~ is ~elected to xeal~ze the flat sectio~s at both bolt end~9 depending on . the respective use o~ the ~hain.
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_ 12 -~he one-piece end connector links 3 have a slit 17 merging a~ either end into through bores 18 which serve to recei~e the bolt ends 13 and 14 9 respectively~ and being enclosed all around~
As may be taken from ~igure 49 the two opposed material bridges 19 9 20 at ei*her side of ~lit 17 can be contracted by means of a screw 210 Hereby the contact pressure can be produced which is required to preas the flat sections in through bores 18 against the fla~ ~ections 15~ 16 of bolt ends 1~ 14.
The end connector links ~ may also be divided in longitudinal direction.
It is also possible to provide a greater even number of tubular bodie~ 1 for each chain link instead of only two~ In that case~
apart from the center which again contains an intermediate connecto~ k 5 pxovided with a chain taot~ 41 intermediatc connector links similar to the end connector links 3 are inserted between the individual tubular bodies. ~hese inter mediate connector links have surfaces which are flush with the sur~aces 11 of the tubular bodies to increase the roll-of surface for the correspondingly wider tread rollers, thus contributing to improve the smooth running. When it is desired to enlarge the chain, this type of structure i~ preferred in that it of~ers more convenient storage and savings of weight and mate~ial as compared to a structure employ~ng wider structural elements, especially wider tubular bodies. It is to be under-stood that even with such a wider chain having a correspondingly greater number of tubular bodies and connector links~ these elementæ are accurately dimensioned in a direction transversely of the running direction of the chain so that~ beginning with a predetermined ~le~ure~ the tubular bodies and the connector links support each other and again form a bridge protecting the bolts from excessi~e bending stress.
Figure 5 likewise ~hows an embodiment o~ a chain which is wider than the embodiment according to figure 1 but which comprises three tubular bodies~ in other word3 an uneven number o~ tubular bodies per chain linkO Just like the tubular bodie~
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22~9 _ 13 _ 1 the tubular bodie~, designated in general by reference numeral 41, have through bores 42 to receive boltr 44 provided with rubber sleeves 43 which are fixed on the bolts by vul-canization. In this case the rubber sleeves mentioned are also provided in a central tubular body 41 which carries a chain tooth 60. On principle the bOltsa 44 are of the same structure as bolts B of the embodiment shown in figures1 to4 .In thi3 case~ too~ measures are taken to secure the bolt ends 47 and the end connectors 48 against relative rotation and axial slipping~
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~he embodiment according to figure-a. 5,6 compr.ises divided intermediate connector links 55 o~ which only the upper part is to be seen. The lower p æt is adapted to be clamped agains~
the upper par~ and at the same time a~ain$t the bolts 44 by means o~ ~crews 56. ~he parts of the lntermed~ate connectors 55 together form recesses or openings which, in assembled condition, surround approximately three quarters of the total circumference of the bolts in the areas 54 in which they are free of the rubber sleeves 53. The intermediate connector links may have areas 57 which extend trans~er~ely of the running direction of the chain between adjacent tubular bodies 41 and form a flush surface with the surfaces 58 of the tubula~
bodies 41~ But satisfactory sm~thhr~nning can be obtained also without such area~ 57. ~ikewise ~ith these surfaces 58 i8. the surface of webs 59 which extend from the central tubular bodies 41 toward both sides to the ~acent tubular bodie~ 41 trans-ver~ely of the running direction of the chain~ These webs 59 do not reach as far a~ the overall dimension of the tubular bodie~
41 in the running direction of the chain but instead leave spaces into which extend webs 61 provided at intermediate connector links 55 and oriented in running direction and in a direction opposed to the same~ respectively~
~he dimensio~ o~ web~ 59 at central tubular body 41 and of web~ 57 and ~1 at intermecliate connectors 55 (to be seen only ~, . .
_ . ., ... , ., .. ... , . ~ . ... -in figure 5 bu-t not in figure 6) as well as the dimensions of the outer tubular bodies 41 and of the end connector link~ 48 in a direc-tion transversely of the running direction of the chain are ~o selected that again a predetermined clearance a is obtained which, in the present case, is zero~ By vir-tue o~
this arrangement, upon vertical de~lection the bolts 44 are partly relieved from the very beginning from bending stxess.
Structural elements such as sho~n in figure 5 can also be used to make wider chains with a greater uneven number o~ tubular -bodies per chain link.
Figure 7 shows the course o~ a bending load P of the chcin above t bending flexure f of a chain link such as shown in ~igures 1 to
3 or 5 and 6. ;
The continuous curve k represents-the course of the loading above the deformation, starting from a finite clearance a (figure 2). When a flexure fl or a bending load Pl is reached, the tubular bodies have come to abut each other or the intermediate connector links and form a stif~ening bridge~ ~he `-continuous curve k then bends at k1 and continues more steeply.
~his means that a greater bending force must be applied to obtain the same deformation, in other words that the chain link as a whole has become stiffer. Curve ko is a discontimlous line showing how the load-deformation-characteristic would continue i~ the bolt were deformed alone without support by the elements of the chain linkO Curve ko would soon get into ranges where the deformation would be too great. If one considers that in the range of higher load it is predominantly the tubular bodies and the connector links~ and only partly the bolts~ which have to withstand bending stress, it is evident that the bolt may be made to smaller dimensions at the same ~otàl load than i~ the bolt alone also had to endure maximum bending stresse~. Accordingly, also the through bores 10 and ~29 respeotively~ in the tubular bod~es and the bolt recei~ing .... .. . .. . ........ .... . . . . .. . . .
~ 15 -bores 18 in the end connector links may be made to smallerdimensions, which in turn entails a reduction in ~ize and weight of thetubul~.r bodies ~s well as the co~mector links.
The dash-dotted line in figure 7 shows the course of a curve l which is obtained when the clearance a is ~ero from the very beginning (figure 6). In this case the tubular bodies and the connector links support bending loads together with the bolt from the very beginning~
, In figures 8 to 27 a one-piec~end connector is designated 1000 The end connector 100 has two essentially circular through bores 101, 102 which are connected by a slit 10~ This slit 103 ~ubdivides the end connector,which is either made in one .
piece (fiK.12)or divided ~fi~.16),into twn bridges 106,1074 In the embodiments shown in figures 8to1.3a central hole or opening 108 of the end connector receives a fitting pieceO
This fitting piece is embo~ed by a round bushing 109 in figures 8.to11.The bushing 109 has flat sections 110 at its two opposed sides ~acing the bolt ends 104~ 1050 These flat sections are inclined in two directions (s~ figure~ 8 and 9) and co-operate with corresponding flat sections 1 l 1 at the bolt ends.
~he bushing 109 is pressed against the flat sections 111 of the bolt ends b~means of a central screw or bolt 1120 The flat sections may also be inclined in one direction onl.y or may not be inclined at all, iOe. they may extend completely parallel to the axis~ The mai~ difference between the embodiments shown in figures~to1Oand 11 resides in the fact that figure 8 shows the bushing 109 to have a threaded bore 113 into which enters screw 112, whereas with the embodiment shown in figure 11 screw i12 is inserted in a plain hole 114 and screwed into a threaded bore 115 in the bridge 106 of the end connector.
The contours of the flat 6ection 110 (discontinuous line,) of bushing 109 and of flat ~ection 111 at the bolt end ,:
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_ 16 -(continuous line ~ are sho~m in figure 10~ q'he two 1at sections contact each other in the cross-hatched area of profile 110, The embodiment according to figure 12 dif~er~ only by an an-gular~ fitting piece 116 instead o~ the round bushing 109 fitted in a corresponding angular hole 117 in -the end connec-tor 100. The angular fitting piece also has flat sections 110 at both sides 9 inclined in two directions and facing the.bolt ends 104, 105. ~y these 1at sections it is pressed against corresponding flat sections at the bolt end~, using a screw 112 not shown in figure 12. ~he flat sections may also be inclined in one.direction only (see figure 11)o In a view similar to figure 13 this fitting piece would look re.ctangular, having edges 110 in parallel with ~he axis (figure 5).
A form-lock connection between the bolt ends 104, 105 and the end connectors 100 i~ achieved with the ~itting piece 109 and 1 116, re~pectivelyO ~his connection prevents axial displacement as well as rotation.
In the case of a connection according to figure 14 the two bridges 106, 107 of the end connector are tightened against each other by means of a central screw 120. A disc 122 is arranged between the head 121 of the scr~3and the surface of the bridge 107. Cylindrical ~itting pins/extend do~nwardly from the disc (figure 15). These cylindrical fitting pins are arran~ed such that they extend through corresponding recesses 124 in the bolt end~O
It is also possible to provide conical pins instead of cylindrical fitting pins 12'~. ~urthermore~ the disc 122 need not be firml~ connected with the fitting pins but instead may form a ~eparate element which merely cooperates in ~orce-lock with the end faces o~ the fitting pinsO
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Also only one fitting pin per connector 100 may be T1rovided.
Instead of providing a separate fitting pin the clamping bolt itself may h~ve a fitJting portion fulfilling the function of a fitting pin for one or both bolts.
Figure 1f, shows the end connector in divided form, the two parts 133,134 thereof being pressed against each other and against the bolt ends by means of a central screw 120. The bolt ends ~gain are provided with flat sections 135, either at diametrically opposed locations or in V-shape at one side (not shown). Corre~ponding flat sections 136 provided at the end connector parts cooperate in form-lock with those flat sections.
r~he screw connections of the embodiments according to fi~llres 17 and 18 comprise ~crew connections in the direction of t~le longi-tudinal axi9 of bolt ends 104 and/or 105 to secure the bol1s ag~ln~t axiAl di~pl~cemen~. 'l'he conne¢~ion accor~ing to rlgure 17 shows a screw 137 which is screwed into a threaded bore in t'ne bolt end coaxial with the longitudinal axis of the bolt, the head 138 of this screw being ~ported on the end connector 100 -, through a disc 139. The disc 139 may be replaced by a spring, e.g~
a pile of ~elleville washers which permits a defined axial dis-placement of the bolt end 104 with respect to the end connector 1~0. The defined axial displacement is determined by the maxi.~um deflection of the spring. Instead of separat~ sprîngs the elastic expansion of the screw 137 itself may slso be utilized. For this purpose the screw may also be designed a's a highly deformable bolt having a weakened shaft.
With the modification according to figure 18 a threaded pin 140 which is coaxial with the bolt axis projects ~rom the, front face of thebolt end 104. A nut 141 i9 screwed on this pin 140 and its axial force is supported at the end connector 1~0 by way of a spring or disc 139. No mean~ ~ seauring the connection ~ainst rotation is shown in figures 17 and 18. It may be obtained in the usual manner by flat sectlons parallel to the axis at the ~2~4 end~ and bol~ end connectors. In thi~, case, however, the flat sections at the bolt ends extend up to the front faces of the bolts.
'~he form-lock connections according to figures 19 and 20 are obtained by ~ressing end connector material into depressions of the bolt ends.
The connection according to figure 19 shows the bolt end to have two hollow fillets 142, 143 inclined in opposite directions, between which a web 144 was left. Material of opposite areas of the recess for the bolt ends or of the bridge members 10~),107, ' respectively, is pressed under elastic deformation into the hollow fillets 142, 143 by the central screw 120 clamping the ' bridge-members 106,107 so th~t a form-lock connection is e~tab-lished. '~hen screw 120 is unscrewed the material ela~tically re-turns in its undeformed shape which renders possible disassembl- ' in~ ~f th~ bol~ from th~ oonn~tor.
The embodiment accordintg to figure 2~ shows three hollow fillets 145 having saw-tooth profile at the bolt ends~ Projections 146 of corresponding outline are formed in the openings in the end connectors 1000 The gap 147 between the hollow fillets 145~and the projections 146 is shown exaggeratedO In an actual embodiment it is in the range ~rom one to two hundredths of the bolt diameter and so dimensioned that in unloaded condition of the connector the bolt may be pushed into the opening. Then the screw 120 is tightened so that the projections 146 are pressed into the depressions of the hollow fillets 145 9 thus providing'a form-lock connection~
~he end connector used for the connection according to figures 19 and 2~ has a cross sectional shape such as shown in figure 21.
With the connection shown in figures ~? and 2~ axial fixing ~ ;
in one direction and rotatory ~ixing .i6 provided by a clamp ; ' '' 180 a~sociated with each bolt end. The legs 181 of the clamp ~ngage in diametrically oppo~ed flat sections 182 at the respective bolt. ~he clamp 180 supports an axial force on the bolt in inward direct~on (in figure 23 directed up~vardly) at the front face 183 of a tubular body 184 of the track facing the end connectorO Rotation of the clamps 180 and thus of the .. , . . - , ., ~ . .
_ connector bolts is prevented by projec-ting wall portions 185 of the end/
If a similar connection is provided at the upper bolt end~ 9 axial slipping of the bolts with respect to the tubular bodies :.
184 and thue the end co~nectors i~ prevented in both directions.
With the embodiment.. according to figure. 24 the connection between the end connector 100 and the bolt end~ 104 and 105 respectively~ is realized by friction lock at a ~ery great frictional forceO . . Wedging action i8 utilized for this purpose~ a relati~ely small ~oxce produced by a screwed connection in axial direction being converted by a wedge surface into a great normal force which in turn produces a great frictional force. . -~
~onical ~urYaces 195~ 196 at. the end connector and at the inner - .
end, réspectively, of a hollow screw 197 cooperate to produce contact pressure between a bore fitting piece 198 and the bolt circumference along a circumferential area shown by cross hatching~
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h~igure 25 shows an example of a bayonet connection between a bolt end and an end connector.
, The bolt shown in fig. 25 has axially directed wedge teeth 204 at its end. ~orresponding wedge teeth 206 are formed in the .opening in the end connector to fit into the wed~e ~aps 205 : between the wedge teeth 20~. Axially adjacent the wedge teeth 204 the bolt has a portion 207 of reduced diameter which is separated . ~y a shoulder 208 from the`main portion 209 of the bolt having ~a diameter corresponding to the diameter of the tops of teeth 204.
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By inserting the bolt in the direction of the arrow against shoulder 208 and subsequent rotation the wedge teeth 206 are caused to engage behind the wedge teeth 204 so as to secure the bolt against axial displacement in both directions.
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In the embodiment according to Iigures 26 and 27 the bolt end~
104, 105 are provided at opposed circwnferential area~ with - transverse grooves 2209 221 into which enter opposed pro~ections 223~ 224 of a disc 225. The disc is so dimensioned that it ~, ~its into the slit 103 in the end connector 1000 The disc 225 has a central aperture 226 for insertion of the central screw 120 which ser~es to clamp the bridges 106, 107 of the end connector 1000 ~he dash-dot line at 227 show~ a tongue which may be pro~ided additionall;y at the disc 225 to facilitate the sliding on of the - end connector 100. ~his provides a form-lock connection which affords rotary securing as well as axial fixing in both directions without any measures being taken at the end connector 1000 Thus a conventional end connec tor can be usedO
In addition, only the diso 225 and the grooving of the bolt , end~ a~ quix~d. F~ thi~ r~a~on th~ ,emb~di~nt ~ocordin~5 to figures 2~ and 27 is especially economicalO
~he end connector 301 shovm in figure 28, is made in one pieceO
It has a~ elongat,ed through opening 302 , the end~ of ~r~hich .
are widened to form recesse~ or opening~3 ~03 to receive bolts 304.... The rece'~ses are adapted in shape to the bolt ends in that ,,' they have a hollow cylindricali portion 305 extending over the major pisxt of the circum~erence and a flattened portion 3060 The bolts are formed accordingly with a cylindrical portion ' "',''3059 and a flattened por~ion 306'. ~he recesses are machined to .correspond to the bolt ends.
~he two bridge members 307~ 308 in the central portion of ~he , - ' :
connector may.be forced. against each other by a clamping screw which-i~ not shown and adapted to be in~erted in through holes 3,09, 310 in the two bridge members and tightened by a lock nut ',likewi'sè not showIl. Alternatively the hole 310 ln bridge membex 308 mi~y be designed a8 a threaded hole"
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. - 21 _ While t~le openin~s 303 of the connector 301 have a ~moot}.
surface~ longitudinal grooves 312 of a length extendlng acros~
the width of the connector are machined into the ~l~ shown on the left in figure ~,Surface portions or lands 313 remain between the longitudinal grooves, 312 and with the bolt installed they are in contact with the smooth surface ~05, 306 of the opening 303O
Instead o~ longitudinal grooves the bolt shown on the right hand side in figure 28has a plurality of helical grooves 314 ~-at the bolt end cooperating with the opening~ Again contac-t surfaces 315 between the grooves 314 cooperate with the smooth surface 305, ~06 of the opening. It is also possible to provide a single.groove 314 which will have a corrsspondingly low pitcho In the embodiment ~hown i~ figure 29 the bolt ends have ~
smooth ~ylindrical surface 316' and smooth flattened portion~ 317' !
whereas the openings 30~ have longitudinal grooves 322 and raised contact surfaces 323 between the grooves ~22 as well in their cylindrical portions 316 as in their flattened portions 317 for cooperation with the bolt surface. ~he longitudinal grooves 322 can be produced by broaching in easier and less expensive' manner than longitudinal grooves 312 on the Quter surface o~
the bolt 304 in fiq. 28.
In the case o the connections a`ccording to figures 28 and 2g the tightening of the screw produces a clamping force which acts vertically of the contact surfaces and has a higher specific surface loading than with smooth contact surfacesO ~his clamping force presses residual lubricant and any possible foreign matter from be,tween the contact surfaces into the grooves 312, 314 or 322 so ~hat the greatest possible coefficient of friction determined by the pairing of material of the bolt and the connector 301 prevails between the contact surfaces~ If the grooves were not provided~ it would be una~oidable that lubricant or foreign part~cles remain between the~con~act surfaces thus changing the coefficient of friction; and ~onse-quently the required clamping force in un~redictable mannerO
This i~ notonly due to the lacking space for evasion of undesired matter but also to the fact that the specific surface loading obtained by the same 9crew tlghtening torque is smaller~
... . .. . ..... I . .. . - . . . - -~ S4 It is convenient to select the width of the longitudinal grooves 312, 322. or of the helical grooves 314 and the spacin~
defin.ing their contact surfaces ~1~ an3d 315~ respectively7 such that the specific pressura at the contact surfaceis is sl~ghtly below the flow limit of the materials of bolts and end connectorsO
Axial displacement between the bolts and the end connectors is prevented by a connection according to figures 8to 29 or9at the mQst9 possible in controlled manner against spring force up to an abutment. Thiis type of connection permitting controlled displacement between the end connector~ and the bolt endis has`
been explained only in connection with figuresl7 and 18,Yet it is obvious to anyone 6killed in the art that all other embodi- :
ments may also comprise additional springs or may have sufficient inherent resiliency of the boltis to permit controlled axial relative movement between the bolt ends and the end connectorsO
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It is also evident that. a connection according to figures 8 to ..29, may also be useful with a caterpillar track in which the support of the tubular bodies 1 and the connector links 3~ 5 :~ explained with the aid of figures 1to7. iB not embodied or~ in -other words~ in which the parts 1, ~ and 5 may shift in undefined manner transversely of the direction of mo~ement of the caterpillar trackO.
The pre~ent embodiments are to be considered as in all respects illu~trati~e and not restrictive; the scope of the invention . .
being indicated by the appended claImsO
, !
r, .1'. 1 . . ~.
r ' :' -- -; - , , .... -.-- -- - - - - - - :
.
The continuous curve k represents-the course of the loading above the deformation, starting from a finite clearance a (figure 2). When a flexure fl or a bending load Pl is reached, the tubular bodies have come to abut each other or the intermediate connector links and form a stif~ening bridge~ ~he `-continuous curve k then bends at k1 and continues more steeply.
~his means that a greater bending force must be applied to obtain the same deformation, in other words that the chain link as a whole has become stiffer. Curve ko is a discontimlous line showing how the load-deformation-characteristic would continue i~ the bolt were deformed alone without support by the elements of the chain linkO Curve ko would soon get into ranges where the deformation would be too great. If one considers that in the range of higher load it is predominantly the tubular bodies and the connector links~ and only partly the bolts~ which have to withstand bending stress, it is evident that the bolt may be made to smaller dimensions at the same ~otàl load than i~ the bolt alone also had to endure maximum bending stresse~. Accordingly, also the through bores 10 and ~29 respeotively~ in the tubular bod~es and the bolt recei~ing .... .. . .. . ........ .... . . . . .. . . .
~ 15 -bores 18 in the end connector links may be made to smallerdimensions, which in turn entails a reduction in ~ize and weight of thetubul~.r bodies ~s well as the co~mector links.
The dash-dotted line in figure 7 shows the course of a curve l which is obtained when the clearance a is ~ero from the very beginning (figure 6). In this case the tubular bodies and the connector links support bending loads together with the bolt from the very beginning~
, In figures 8 to 27 a one-piec~end connector is designated 1000 The end connector 100 has two essentially circular through bores 101, 102 which are connected by a slit 10~ This slit 103 ~ubdivides the end connector,which is either made in one .
piece (fiK.12)or divided ~fi~.16),into twn bridges 106,1074 In the embodiments shown in figures 8to1.3a central hole or opening 108 of the end connector receives a fitting pieceO
This fitting piece is embo~ed by a round bushing 109 in figures 8.to11.The bushing 109 has flat sections 110 at its two opposed sides ~acing the bolt ends 104~ 1050 These flat sections are inclined in two directions (s~ figure~ 8 and 9) and co-operate with corresponding flat sections 1 l 1 at the bolt ends.
~he bushing 109 is pressed against the flat sections 111 of the bolt ends b~means of a central screw or bolt 1120 The flat sections may also be inclined in one direction onl.y or may not be inclined at all, iOe. they may extend completely parallel to the axis~ The mai~ difference between the embodiments shown in figures~to1Oand 11 resides in the fact that figure 8 shows the bushing 109 to have a threaded bore 113 into which enters screw 112, whereas with the embodiment shown in figure 11 screw i12 is inserted in a plain hole 114 and screwed into a threaded bore 115 in the bridge 106 of the end connector.
The contours of the flat 6ection 110 (discontinuous line,) of bushing 109 and of flat ~ection 111 at the bolt end ,:
-- . . . . . . .. .. .... . . .. .. ., ....... .. .. .. ~ . . . . .. . . .... .
_ 16 -(continuous line ~ are sho~m in figure 10~ q'he two 1at sections contact each other in the cross-hatched area of profile 110, The embodiment according to figure 12 dif~er~ only by an an-gular~ fitting piece 116 instead o~ the round bushing 109 fitted in a corresponding angular hole 117 in -the end connec-tor 100. The angular fitting piece also has flat sections 110 at both sides 9 inclined in two directions and facing the.bolt ends 104, 105. ~y these 1at sections it is pressed against corresponding flat sections at the bolt end~, using a screw 112 not shown in figure 12. ~he flat sections may also be inclined in one.direction only (see figure 11)o In a view similar to figure 13 this fitting piece would look re.ctangular, having edges 110 in parallel with ~he axis (figure 5).
A form-lock connection between the bolt ends 104, 105 and the end connectors 100 i~ achieved with the ~itting piece 109 and 1 116, re~pectivelyO ~his connection prevents axial displacement as well as rotation.
In the case of a connection according to figure 14 the two bridges 106, 107 of the end connector are tightened against each other by means of a central screw 120. A disc 122 is arranged between the head 121 of the scr~3and the surface of the bridge 107. Cylindrical ~itting pins/extend do~nwardly from the disc (figure 15). These cylindrical fitting pins are arran~ed such that they extend through corresponding recesses 124 in the bolt end~O
It is also possible to provide conical pins instead of cylindrical fitting pins 12'~. ~urthermore~ the disc 122 need not be firml~ connected with the fitting pins but instead may form a ~eparate element which merely cooperates in ~orce-lock with the end faces o~ the fitting pinsO
. ~
' - . ~., , . .. . . ~ .
Also only one fitting pin per connector 100 may be T1rovided.
Instead of providing a separate fitting pin the clamping bolt itself may h~ve a fitJting portion fulfilling the function of a fitting pin for one or both bolts.
Figure 1f, shows the end connector in divided form, the two parts 133,134 thereof being pressed against each other and against the bolt ends by means of a central screw 120. The bolt ends ~gain are provided with flat sections 135, either at diametrically opposed locations or in V-shape at one side (not shown). Corre~ponding flat sections 136 provided at the end connector parts cooperate in form-lock with those flat sections.
r~he screw connections of the embodiments according to fi~llres 17 and 18 comprise ~crew connections in the direction of t~le longi-tudinal axi9 of bolt ends 104 and/or 105 to secure the bol1s ag~ln~t axiAl di~pl~cemen~. 'l'he conne¢~ion accor~ing to rlgure 17 shows a screw 137 which is screwed into a threaded bore in t'ne bolt end coaxial with the longitudinal axis of the bolt, the head 138 of this screw being ~ported on the end connector 100 -, through a disc 139. The disc 139 may be replaced by a spring, e.g~
a pile of ~elleville washers which permits a defined axial dis-placement of the bolt end 104 with respect to the end connector 1~0. The defined axial displacement is determined by the maxi.~um deflection of the spring. Instead of separat~ sprîngs the elastic expansion of the screw 137 itself may slso be utilized. For this purpose the screw may also be designed a's a highly deformable bolt having a weakened shaft.
With the modification according to figure 18 a threaded pin 140 which is coaxial with the bolt axis projects ~rom the, front face of thebolt end 104. A nut 141 i9 screwed on this pin 140 and its axial force is supported at the end connector 1~0 by way of a spring or disc 139. No mean~ ~ seauring the connection ~ainst rotation is shown in figures 17 and 18. It may be obtained in the usual manner by flat sectlons parallel to the axis at the ~2~4 end~ and bol~ end connectors. In thi~, case, however, the flat sections at the bolt ends extend up to the front faces of the bolts.
'~he form-lock connections according to figures 19 and 20 are obtained by ~ressing end connector material into depressions of the bolt ends.
The connection according to figure 19 shows the bolt end to have two hollow fillets 142, 143 inclined in opposite directions, between which a web 144 was left. Material of opposite areas of the recess for the bolt ends or of the bridge members 10~),107, ' respectively, is pressed under elastic deformation into the hollow fillets 142, 143 by the central screw 120 clamping the ' bridge-members 106,107 so th~t a form-lock connection is e~tab-lished. '~hen screw 120 is unscrewed the material ela~tically re-turns in its undeformed shape which renders possible disassembl- ' in~ ~f th~ bol~ from th~ oonn~tor.
The embodiment accordintg to figure 2~ shows three hollow fillets 145 having saw-tooth profile at the bolt ends~ Projections 146 of corresponding outline are formed in the openings in the end connectors 1000 The gap 147 between the hollow fillets 145~and the projections 146 is shown exaggeratedO In an actual embodiment it is in the range ~rom one to two hundredths of the bolt diameter and so dimensioned that in unloaded condition of the connector the bolt may be pushed into the opening. Then the screw 120 is tightened so that the projections 146 are pressed into the depressions of the hollow fillets 145 9 thus providing'a form-lock connection~
~he end connector used for the connection according to figures 19 and 2~ has a cross sectional shape such as shown in figure 21.
With the connection shown in figures ~? and 2~ axial fixing ~ ;
in one direction and rotatory ~ixing .i6 provided by a clamp ; ' '' 180 a~sociated with each bolt end. The legs 181 of the clamp ~ngage in diametrically oppo~ed flat sections 182 at the respective bolt. ~he clamp 180 supports an axial force on the bolt in inward direct~on (in figure 23 directed up~vardly) at the front face 183 of a tubular body 184 of the track facing the end connectorO Rotation of the clamps 180 and thus of the .. , . . - , ., ~ . .
_ connector bolts is prevented by projec-ting wall portions 185 of the end/
If a similar connection is provided at the upper bolt end~ 9 axial slipping of the bolts with respect to the tubular bodies :.
184 and thue the end co~nectors i~ prevented in both directions.
With the embodiment.. according to figure. 24 the connection between the end connector 100 and the bolt end~ 104 and 105 respectively~ is realized by friction lock at a ~ery great frictional forceO . . Wedging action i8 utilized for this purpose~ a relati~ely small ~oxce produced by a screwed connection in axial direction being converted by a wedge surface into a great normal force which in turn produces a great frictional force. . -~
~onical ~urYaces 195~ 196 at. the end connector and at the inner - .
end, réspectively, of a hollow screw 197 cooperate to produce contact pressure between a bore fitting piece 198 and the bolt circumference along a circumferential area shown by cross hatching~
.: ' ;
h~igure 25 shows an example of a bayonet connection between a bolt end and an end connector.
, The bolt shown in fig. 25 has axially directed wedge teeth 204 at its end. ~orresponding wedge teeth 206 are formed in the .opening in the end connector to fit into the wed~e ~aps 205 : between the wedge teeth 20~. Axially adjacent the wedge teeth 204 the bolt has a portion 207 of reduced diameter which is separated . ~y a shoulder 208 from the`main portion 209 of the bolt having ~a diameter corresponding to the diameter of the tops of teeth 204.
.
By inserting the bolt in the direction of the arrow against shoulder 208 and subsequent rotation the wedge teeth 206 are caused to engage behind the wedge teeth 204 so as to secure the bolt against axial displacement in both directions.
, .. . . . . .. . .. .. . . . . . . .
In the embodiment according to Iigures 26 and 27 the bolt end~
104, 105 are provided at opposed circwnferential area~ with - transverse grooves 2209 221 into which enter opposed pro~ections 223~ 224 of a disc 225. The disc is so dimensioned that it ~, ~its into the slit 103 in the end connector 1000 The disc 225 has a central aperture 226 for insertion of the central screw 120 which ser~es to clamp the bridges 106, 107 of the end connector 1000 ~he dash-dot line at 227 show~ a tongue which may be pro~ided additionall;y at the disc 225 to facilitate the sliding on of the - end connector 100. ~his provides a form-lock connection which affords rotary securing as well as axial fixing in both directions without any measures being taken at the end connector 1000 Thus a conventional end connec tor can be usedO
In addition, only the diso 225 and the grooving of the bolt , end~ a~ quix~d. F~ thi~ r~a~on th~ ,emb~di~nt ~ocordin~5 to figures 2~ and 27 is especially economicalO
~he end connector 301 shovm in figure 28, is made in one pieceO
It has a~ elongat,ed through opening 302 , the end~ of ~r~hich .
are widened to form recesse~ or opening~3 ~03 to receive bolts 304.... The rece'~ses are adapted in shape to the bolt ends in that ,,' they have a hollow cylindricali portion 305 extending over the major pisxt of the circum~erence and a flattened portion 3060 The bolts are formed accordingly with a cylindrical portion ' "',''3059 and a flattened por~ion 306'. ~he recesses are machined to .correspond to the bolt ends.
~he two bridge members 307~ 308 in the central portion of ~he , - ' :
connector may.be forced. against each other by a clamping screw which-i~ not shown and adapted to be in~erted in through holes 3,09, 310 in the two bridge members and tightened by a lock nut ',likewi'sè not showIl. Alternatively the hole 310 ln bridge membex 308 mi~y be designed a8 a threaded hole"
.. j .
. i . ; , , .
.. ,... . ~ . .. . . . . ........ .. . .. . . . . .
.
. - 21 _ While t~le openin~s 303 of the connector 301 have a ~moot}.
surface~ longitudinal grooves 312 of a length extendlng acros~
the width of the connector are machined into the ~l~ shown on the left in figure ~,Surface portions or lands 313 remain between the longitudinal grooves, 312 and with the bolt installed they are in contact with the smooth surface ~05, 306 of the opening 303O
Instead o~ longitudinal grooves the bolt shown on the right hand side in figure 28has a plurality of helical grooves 314 ~-at the bolt end cooperating with the opening~ Again contac-t surfaces 315 between the grooves 314 cooperate with the smooth surface 305, ~06 of the opening. It is also possible to provide a single.groove 314 which will have a corrsspondingly low pitcho In the embodiment ~hown i~ figure 29 the bolt ends have ~
smooth ~ylindrical surface 316' and smooth flattened portion~ 317' !
whereas the openings 30~ have longitudinal grooves 322 and raised contact surfaces 323 between the grooves ~22 as well in their cylindrical portions 316 as in their flattened portions 317 for cooperation with the bolt surface. ~he longitudinal grooves 322 can be produced by broaching in easier and less expensive' manner than longitudinal grooves 312 on the Quter surface o~
the bolt 304 in fiq. 28.
In the case o the connections a`ccording to figures 28 and 2g the tightening of the screw produces a clamping force which acts vertically of the contact surfaces and has a higher specific surface loading than with smooth contact surfacesO ~his clamping force presses residual lubricant and any possible foreign matter from be,tween the contact surfaces into the grooves 312, 314 or 322 so ~hat the greatest possible coefficient of friction determined by the pairing of material of the bolt and the connector 301 prevails between the contact surfaces~ If the grooves were not provided~ it would be una~oidable that lubricant or foreign part~cles remain between the~con~act surfaces thus changing the coefficient of friction; and ~onse-quently the required clamping force in un~redictable mannerO
This i~ notonly due to the lacking space for evasion of undesired matter but also to the fact that the specific surface loading obtained by the same 9crew tlghtening torque is smaller~
... . .. . ..... I . .. . - . . . - -~ S4 It is convenient to select the width of the longitudinal grooves 312, 322. or of the helical grooves 314 and the spacin~
defin.ing their contact surfaces ~1~ an3d 315~ respectively7 such that the specific pressura at the contact surfaceis is sl~ghtly below the flow limit of the materials of bolts and end connectorsO
Axial displacement between the bolts and the end connectors is prevented by a connection according to figures 8to 29 or9at the mQst9 possible in controlled manner against spring force up to an abutment. Thiis type of connection permitting controlled displacement between the end connector~ and the bolt endis has`
been explained only in connection with figuresl7 and 18,Yet it is obvious to anyone 6killed in the art that all other embodi- :
ments may also comprise additional springs or may have sufficient inherent resiliency of the boltis to permit controlled axial relative movement between the bolt ends and the end connectorsO
' , I ,. .....
It is also evident that. a connection according to figures 8 to ..29, may also be useful with a caterpillar track in which the support of the tubular bodies 1 and the connector links 3~ 5 :~ explained with the aid of figures 1to7. iB not embodied or~ in -other words~ in which the parts 1, ~ and 5 may shift in undefined manner transversely of the direction of mo~ement of the caterpillar trackO.
The pre~ent embodiments are to be considered as in all respects illu~trati~e and not restrictive; the scope of the invention . .
being indicated by the appended claImsO
, !
r, .1'. 1 . . ~.
r ' :' -- -; - , , .... -.-- -- - - - - - - :
.
Claims (6)
1. Connector means for connecting together the adjacent ends of successive chain links of an endless track, comprising:
(a) an end connector member containing trans-versely extending through openings at its forward and rear ends, respectively, each of said through openings including (1) a curved first inner wall contact surface which comprises, in transverse cross-section, a segment of a circle, and (2) a flat second inner wall contact surface, said contact surfaces extending the length of said through opening; and (b) a pair of cylindrical rod members extending at one end within said openings, respectively, each of said rod members having on its outer periphery (1) a curved first outer wall contact surface in contiguous frictional engagement with said first inner wall contact surface, and (2) a flat second outer wall contact surface in contiguous frictional engagement with said second inner wall contact surface, whereby said contact surfaces cooperate to prevent rotation of said rod member relative to said end connector member;
(c) each of the curved and flat contact surfaces of one of said members containing at least one groove, whereby when the corresponding curved and flat contact surfaces are pressed tightly together in tight frictional engagement foreign matter is removed from the contact surfaces to produce a large constant frictional force between the members for preventing axial displacement of the rod member relative to the connector link.
(a) an end connector member containing trans-versely extending through openings at its forward and rear ends, respectively, each of said through openings including (1) a curved first inner wall contact surface which comprises, in transverse cross-section, a segment of a circle, and (2) a flat second inner wall contact surface, said contact surfaces extending the length of said through opening; and (b) a pair of cylindrical rod members extending at one end within said openings, respectively, each of said rod members having on its outer periphery (1) a curved first outer wall contact surface in contiguous frictional engagement with said first inner wall contact surface, and (2) a flat second outer wall contact surface in contiguous frictional engagement with said second inner wall contact surface, whereby said contact surfaces cooperate to prevent rotation of said rod member relative to said end connector member;
(c) each of the curved and flat contact surfaces of one of said members containing at least one groove, whereby when the corresponding curved and flat contact surfaces are pressed tightly together in tight frictional engagement foreign matter is removed from the contact surfaces to produce a large constant frictional force between the members for preventing axial displacement of the rod member relative to the connector link.
2. Apparatus as defined in claim 1, wherein the flat second inner wall contact surfaces of said end connector member through openings are arranged in wedge-defining relation on a chord of the circle a segment of which is defined by said curved first inner wall contact surface, and further includ-ing bolt means connected with said end connector member for forcing the flat inner wall contact surfaces in wedging engagement with said flat outer wall contact surfaces.
3. Apparatus as defined in claim 1, wherein the grooves defined in the flat and curved wall surfaces of said member extend longitudinally of the associated through opening.
4. Apparatus as defined in claim 3, wherein said grooves are formed by broaching.
5. Apparatus as defined in claim 1, wherein the grooves are formed in the curved and flat outer wall portions of said rod member by a helical groove extending continuously about the outer periphery of said rod member.
6. Apparatus as defined in claim 2, wherein the dimension of each of said grooves is such relative to the compressional stress applied to said contact surfaces that the stress is below the yield point of the material from which said one member is found, whereby deformation of the member which would cause flow of the material into the groove is prevented.
Applications Claiming Priority (6)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE2614691A DE2614691C3 (en) | 1976-04-05 | 1976-04-05 | Caterpillar |
| DEP2614691.8 | 1976-04-05 | ||
| DEP2657905.5 | 1976-12-21 | ||
| DE2657905A DE2657905C3 (en) | 1976-12-21 | 1976-12-21 | Connection between the chain links of a crawler belt |
| DEP2708538.7 | 1977-02-28 | ||
| DE19772708538 DE2708538C3 (en) | 1977-02-28 | 1977-02-28 | Connection between the chain links of a crawler belt |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1082264A true CA1082264A (en) | 1980-07-22 |
Family
ID=27186819
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA275,577A Expired CA1082264A (en) | 1976-04-05 | 1977-04-05 | Improvements in the construction of chainlinks of endless tracks for track vehicles |
Country Status (15)
| Country | Link |
|---|---|
| JP (1) | JPS52145929A (en) |
| AR (1) | AR213637A1 (en) |
| AU (1) | AU510969B2 (en) |
| BR (1) | BR7702133A (en) |
| CA (1) | CA1082264A (en) |
| CH (2) | CH616892A5 (en) |
| DK (1) | DK142648C (en) |
| ES (1) | ES457533A1 (en) |
| FR (1) | FR2347253A1 (en) |
| GB (1) | GB1575368A (en) |
| IT (1) | IT1082547B (en) |
| NL (1) | NL183449C (en) |
| NO (1) | NO151034C (en) |
| SE (1) | SE424173B (en) |
| TR (1) | TR19750A (en) |
Families Citing this family (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| FR2450505A1 (en) * | 1979-03-02 | 1980-09-26 | Thomson Csf | SEMICONDUCTOR DEVICE COMPRISING A DIFFUSED GUARD RING AND MANUFACTURING METHOD THEREOF |
| DE3043874A1 (en) * | 1980-11-21 | 1982-06-24 | Rheinmetall GmbH, 4000 Düsseldorf | TRACK CHAIN |
| JPS58126286U (en) * | 1982-02-22 | 1983-08-27 | 株式会社小松製作所 | Track linkage device for tracked vehicles |
| DE3405699C2 (en) * | 1983-04-22 | 1985-08-01 | Diehl GmbH & Co, 8500 Nürnberg | Device as an assembly aid on caterpillars for tracked vehicles |
| FR2623767A1 (en) * | 1987-11-30 | 1989-06-02 | Hutchinson | Articulation spindle for a vehicle caterpillar track connector, connector and caterpillar track including such spindles |
| US5201171A (en) * | 1991-11-26 | 1993-04-13 | Caterpillar Inc. | Method and apparatus for retaining a track chain joint |
| FR2703017B1 (en) * | 1993-03-24 | 1995-06-02 | Giat Ind Sa | Connection device for vehicle track. |
| FR2766450B1 (en) | 1997-07-22 | 1999-09-17 | Giat Ind Sa | DEVICE FOR CONNECTING TRACK LINKS |
| CN100361857C (en) * | 2002-11-20 | 2008-01-16 | 株式会社普利司通 | Rubber track |
| JP4963128B2 (en) * | 2009-11-25 | 2012-06-27 | 三菱重工業株式会社 | Crawler connection structure |
| US10518829B2 (en) | 2017-06-26 | 2019-12-31 | Caterpillar Inc. | Lobed track pin |
| GB2567464A (en) * | 2017-10-12 | 2019-04-17 | Clark Tracks Ltd | Improvements in or relating to track apparatus |
| US11230334B2 (en) * | 2019-05-24 | 2022-01-25 | Caterpillar Inc. | Master link for a track chain |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US2113018A (en) * | 1933-02-27 | 1938-04-05 | James Cunningham Son & Company | Vehicle track |
| DE1605585A1 (en) * | 1966-07-22 | 1971-03-11 | Diehl Kg Zweigwerk Der Fa Dieh | Connector caterpillar |
| DE1680325C3 (en) * | 1968-03-16 | 1974-04-25 | Gerlach-Werke Gmbh, 6650 Homburg | Track for all-terrain vehicles, especially armored vehicles |
| DE1950947C3 (en) * | 1969-10-09 | 1973-11-22 | Ruf, Walter, Dipl.-Ing., Bottighofen, Thurgau (Schweiz) | Caterpillar |
-
1977
- 1977-03-21 SE SE7703221A patent/SE424173B/en not_active IP Right Cessation
- 1977-03-22 CH CH360977A patent/CH616892A5/en not_active IP Right Cessation
- 1977-04-01 DK DK143977A patent/DK142648C/en not_active IP Right Cessation
- 1977-04-04 BR BR7702133A patent/BR7702133A/en unknown
- 1977-04-04 AU AU23945/77A patent/AU510969B2/en not_active Expired
- 1977-04-04 NO NO77771179A patent/NO151034C/en unknown
- 1977-04-04 IT IT67736/77A patent/IT1082547B/en active
- 1977-04-05 ES ES457533A patent/ES457533A1/en not_active Expired
- 1977-04-05 TR TR19750A patent/TR19750A/en unknown
- 1977-04-05 GB GB14348/77A patent/GB1575368A/en not_active Expired
- 1977-04-05 AR AR267126A patent/AR213637A1/en active
- 1977-04-05 CA CA275,577A patent/CA1082264A/en not_active Expired
- 1977-04-05 JP JP3896477A patent/JPS52145929A/en active Pending
- 1977-04-05 NL NLAANVRAGE7703746,A patent/NL183449C/en not_active IP Right Cessation
- 1977-04-05 FR FR7710325A patent/FR2347253A1/en active Granted
-
1979
- 1979-11-19 CH CH1031379A patent/CH626022A5/en not_active IP Right Cessation
Also Published As
| Publication number | Publication date |
|---|---|
| DK143977A (en) | 1977-10-06 |
| NL183449B (en) | 1988-06-01 |
| NO771179L (en) | 1977-10-06 |
| JPS52145929A (en) | 1977-12-05 |
| BR7702133A (en) | 1977-12-20 |
| NO151034B (en) | 1984-10-22 |
| AU2394577A (en) | 1978-10-12 |
| GB1575368A (en) | 1980-09-17 |
| FR2347253B1 (en) | 1982-05-21 |
| CH616892A5 (en) | 1980-04-30 |
| AU510969B2 (en) | 1980-07-24 |
| SE424173B (en) | 1982-07-05 |
| SE7703221L (en) | 1977-10-06 |
| DK142648B (en) | 1980-12-08 |
| NL183449C (en) | 1988-11-01 |
| TR19750A (en) | 1979-11-28 |
| NL7703746A (en) | 1977-10-07 |
| DK142648C (en) | 1981-08-10 |
| IT1082547B (en) | 1985-05-21 |
| FR2347253A1 (en) | 1977-11-04 |
| AR213637A1 (en) | 1979-02-28 |
| NO151034C (en) | 1985-01-30 |
| CH626022A5 (en) | 1981-10-30 |
| ES457533A1 (en) | 1978-08-16 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| MKEX | Expiry |