A power transmission chain extending between driving and driven means, such as pulleys or sprockets to transfer torque wherein the chain is formed of a plurality of links having a substantially constant pitch and a plurality of serially arranged contact surfaces engaging contact surfaces of the driving and driven means. The links are designed with longitudinally spaced apertures providing centers of action that are located with respect to a reference line of the link to vary the chordal action of at least some of the links to alter the contact timing and duration between the chain and the driving and driven means to change the generated noise pattern.

BACKGROUND OF THE INVENTION 
Variable pulley transmissions for transferring torque from an input or 
drive shaft to an output or driven shaft have been used for some time. In 
these transmissions, a first pulley constructed of a pair of flanges is 
mounted on the input shaft such that at least one of its flanges is 
axially movable with respect to its other flange. A second, similarly 
constructed and adjustable pulley is mounted on the output shaft. A 
flexible belt connects the two pulleys to transfer torque therebetween 
when the input shaft is driven. As the effective diameter of one pulley is 
changed, the effective diameter of the other pulley is simultaneously 
changed in the opposite direction to adjust the speed ratio between the 
input and output shafts in a smooth, continuous manner. 
Automotive engineers have long recognized that the maximum operating 
efficiency of the engine could be achieved if the transmission could be 
controlled by adjusting to different loads and speed ratios, such that the 
engine is maintained and operated at its maximum efficiency operating 
conditions. This is not possible when a conventional geared transmission 
is teamed with an engine as the speed ratio is adjusted in discrete steps, 
rather than continuously. Accordingly efforts have been directed to the 
use of a continuously variable transmission (CVT) of the type described 
above, and have resulted in commercial production of passenger cars in 
which a flexible, continuous rubber belt is used to drivingly connect the 
pulleys. Rubber belts are subject to wear by reason of the loads they must 
handle and operation under severe temperature, vibration and other adverse 
environmental conditions. To improve belt life, flexible belts of metal 
have been used and considerable effort is being expended to produce 
inexpensive and durable metal belts. Many of these metal belts are 
described in the patent literature. 
Flexible metal belts for use with CVTs are generally of two varieties, 
those referred to as "push" belts and those referred to as "pull" belts. 
An example of a push belt is described in Van Doorne et al U.S. Pat. No. 
3,720,113 and an example of a pull belt is described in Cole, Jr. et al 
U.S. Pat. No. 4,313,730. The belt shown in U.S. Pat. No. 3,720,113 
comprises an endless carrier constructed of a plurality of nested metal 
bands and an endless array of load blocks longitudinally movable along the 
carrier. Each block has edge surfaces for engaging the pulley flanges of a 
pulley transmission to transmit torque between the pulleys. The push belt 
has been used in passenger cars on a limited basis and for some 
non-automotive, industrial applications. The pull belt of Cole, Jr. et al 
utilizes an endless chain as the carrier, the sets of links of which are 
pivotably connected by pivot means, shown as round pins. Generally 
trapezoidal (when viewed from the front) load blocks encircle the links; 
however the load blocks in the pull belt of Cole et al are constrained 
against longitudinal movement along the chain by the pivot means. The 
patent literature also describes a belt constructed of metal parts joined 
by pivot means in which the pivot means engage the pulleys of a CVT. 
The push belt as described in relatively expensive to manufacture. The pull 
belt offers a less expensive alternative to the push belt. There are fewer 
problems in the manufacture of the belt because the links and load blocks 
(a single member or an assembly of relatively thin plates) can be stamped 
from sheet metal and the pivot means can be cut from extruded stock. 
Aside from costs, a major concern of automotive engineers is noise 
generation by drive belts for pulley transmissions. Noise of a mixture of 
frequencies is less objectionable to humans than noise of pure 
frequencies. Currently an evaluation used by some automotive engineers is 
to rate noise generated by drive belts of the type described herein in a 
generally subjective manner by driving or riding in an automobile in which 
the belt is installed and listening to the generated noise. The noise is 
then rated on a numerical scale of 1 to 10 with the higher numbers 
indicating the less objectionable noise. Belts achieving a rating of about 
6 and above are usually acceptable for use in automotive drives, and can 
be classified as being of commercial quality. Of course such belts must 
also be durable, so as to have a reasonable operating life. 
Various ways have been suggested for constructing belts for use in a CVT 
which operate in such a manner to generate noise acceptable to humans, and 
a discussion of some of these ways will be found in the prior art. A 
description of some of the prior art follows. 
In copending application Ser. No. 344,679, filed Feb. 1, 1982, now U.S. 
Pat. No. 4,464,152, a chain-belt constructed in a manner similar to the 
Cole et al patent, supra, has sound damping means interleaved with load 
block laminations. 
Copending application Ser. No. 497,479, filed May 23, 1983, now U.S. Pat. 
No. 4,516,964, discloses load blocks of different transverse widths, all 
of which contact the pulley flanges, but some at a different radial 
location on the pulley flanges from others, thus modifying the generated 
noise pattern. 
In copending application, Ser. No. 497,480, filed May 23, 1983, now U.S. 
Pat. No. 4,516,965, some load blocks do not contact the pulley flanges, or 
some load blocks are missing or "skipped", to thus modify the generated 
noise pattern. 
Copending application, Ser. No. 497,478, filed May 23, 1983, now U.S. Pat. 
No. 4,516,963 discloses a random mixture of load block-pulley flange 
engaging areas to provide a pattern of random engagement thereof with the 
pulley flanges, and thus a modified generated noise pattern. 
A suggested way to modify the generated noise pattern in a chain in which 
the pivot means drivingly contact the pulley flanges is to provide a drive 
chain constructed of a mixture of links of different pitches, such as U.S. 
Pat. No. 4,344,761, issued Aug. 17, 1982. 
Morse U.S. Pat. No. 1,868,334, issued July 19, 1923, teaches constructing a 
chain for use with sprockets which provides a mixture of distances between 
adjacent centers of articulation or a mixture of "effective pitches" in 
order to "break up rythmic vibrations that sometimes cause trouble in 
chain drives". The patent is silent as to whether or not this "trouble" is 
noise related. 
The invention to be described herein relates to chain and chain-belts which 
are used to connect sprockets or pulleys of power transmissions. The 
invention finds particular use for connecting the pulleys of a 
continuously variable transmission, commonly known as a CVT. In the 
description which follows, reference will be made to chain, it being 
understood that this includes not only toothed chains, also known as 
silent chain, but also structures known as chain-belts, which comprise a 
carrier of connected chain links, pivot means connecting interleaved chain 
links and drive blocks each of which encircles a set of links. The 
invention is primarily applicable to that variety of chain-belt known as 
pull belts. 
In its broadest aspect, the chain is an endless loop and comprises a 
plurality of links, each defining a pair of longitudinally spaced 
apertures with one aperture in each link being transversely aligned with 
an aperture in the next adjacent link to thus form transverse rows of 
aligned apertures. Pivot means are received in each row of aligned 
apertures and the pivot means define spaced transverse articulation axes 
which are parallel to one another. The articulation axes for each link set 
are longitudinally spaced from each other. 
When a chain as thus described is used in a CVT, load blocks encircle the 
links between each pivot means, the load blocks being generally 
trapezoidal in shape, when viewed from the front, with the opposing side 
edges adapted to engage the flanges of the pulleys of the transmission. 
Preferably, the pivot means used in the chain comprise a pair of pins, each 
having the same cross-sectional configuration and differing, if at all, in 
length. If a clip is used for retaining the pivot means in the assembly of 
links and blocks, the pins can be substantially the same length. The pins 
as thus described are similar to that described and claimed in copending 
application, Ser. No. 442,386, filed Nov. 17, 1982, now U.S. Pat. No. 
4,507,106 and the disclosure therein is incorporated herein by reference. 
Basically, the pins each have a first, front rocking surface defined by a 
large radius and a back or link contact surface defined by a plurality of 
lesser radii. 
In chains of the type herein decribed, the links are arranged as sets. The 
number of links in a set (and of course the gauge of the metal from which 
the links are made) determines the ultimate width of the chain. For 
example, in a narrow chain, it is common to have a 7-8-7 etc. lacing or 
arrangement with load blocks constructed with a single window encircling 
each set of links. For a wider chain, a modified load block has been 
suggested, one with multiple windows, the adjacent windows being separated 
by a strut. It has been proposed to lace the chain in a 4-5, 5-4, 4-5 etc. 
pattern. Other lacing arrangements can be used within the purview of the 
invention. 
The inventive concepts disclosed herein can also be applied to chains 
usable to connect toothed sprockets, and especially to chains known in the 
art as "silent" chains in which the links are constructed with at least a 
pair of projecting toes defined by flanks separated by a crotch. At least 
some of the flanks contact the sprocket teeth. The problem of noise 
generation is present in the silent chain-sprocket drive arrangement and 
is subjectively rated in a manner similar to that described above. 
DEFINITIONS 
When used herein, the below listed terms have the following meaning: 
The pivot means--a single member. such as a round pin, or a pair of 
members, such as a pin and bushing, pin and rocker, or pair of pins, 
extending through a row of aligned link apertures in two interleaved sets 
of links, to join the links sets and permit articulation thereof. 
link--an elongated member having a pair of longitudinally spaced openings 
adjacent the opposite ends to receive a pivot means. 
articulation axis--an axis of rotation defined by the operation of the 
pivot means; in a rocker joint, the axis is defined by the contact point 
between a pin and rocker; and in a round pin or pin and bushing, the axis 
is the geometric center of the pin. 
axis of symmetry--in a rocking joint chain, an axis traversing an aperture 
or a joint member which divides the pin rocking face into two mirror image 
portions. 
center of action--in a round pin or pin and bushing, the geometric center 
of the pin and/or bushing; in a rocker joint, the geometric center of the 
rocking face. 
line of pull--a line joining the centers of action in a chain or chain-belt 
when that part is tensioned. 
sets of links--the links which are arranged transversely of one another 
with their apertures transversely aligned with one another. 
joint radius--the distance from the axis of articulation of a link to the 
center of the pulley or sprocket. 
load block--a one piece member or an assembly or laminate of a plurality of 
thin plates for encircling a set of links and shaped to engage the flanges 
of the pulleys of a pulley transmission to transfer radial load to the 
links and circumferential load to the pins. 
SUMMARY OF THE INVENTION 
In the present invention, the links of a chain belt are of a substantially 
constant pitch and arranged to insure a mixture of joint radii, so that 
tensions in the chain are not uniformly cyclical in nature, thus producing 
a noise pattern more acceptable to humans. As such the noise pattern is 
not as regular or repetitive as that produced by chains and/or chain belts 
of prior art constructions. 
The present invention comprehends the provision of a novel chain link 
having a reference line generally parallel to the direction of link 
motion, wherein the link has a pair of longitudinally spaced centers of 
action which are unequally spaced from the reference line. 
Various theories have been advanced as to the source of and reasons for 
noise or sound generation when a chain meshes with a sprocket or 
chain-belt engages the flanges of pulleys of a pulley transmission, and 
the prior art is replete with discussions of these theories. A way to 
explain the invention is to relate noise generation to "chordal action". 
The pitch line of a chain constructed of links and/or sets of links, the 
adjacent ones of which are joined by pivot means to permit the chain to 
articulate, on a driving means such as a sprocket or pulley, is polygonal 
rather than circular. This relationship results in that condition which is 
described in the prior art as chordal action. Chordal action manifests 
itself as a radial as well as a longitudinal component or motion in the 
chain as the chain enters the driving means. A cyclical tension occurs in 
the free strand beyond that of the mean tension providing the driving 
force, resulting in fluctuations in the bearing loads of the rotating 
body, i.e., the driving means. In a conventional chain in which the links 
are the same and the pitch of the links is the same (such as taught by the 
prior art), the tensions are uniformly cyclical in nature, so that the 
noise resulting from the cyclical action manifests itself in generated 
noise having rhythmic impulses or recognizable pure tones which can be 
objectionable to humans. The chain of the present invention provides a 
generated noise pattern that is changed or modified in such a way as to be 
more acceptable to humans even though the changed or modified noise 
pattern has the same loudness as the unmodified noise pattern. 
Each link of a chain belt is similarily shaped, although the orientation of 
the links in one set may differ from the orientation of the links in 
another set. Each link has apertures for a pivot means and each pivot 
means defines a center of action. The centers of action of the chain are 
parallel to and spaced from each other with at least one center of action 
transversely offset from a longitudinal reference line; such that one 
center of action in a link is "offset" or "translated" when compared to 
the other center of action in that link. Because of the various 
orientations of this link, a chain may be constructed in which: 
1. all links in the chain are similar to those described herein with 
differently oriented sets of links arranged either in a predetermined 
pattern or in a random pattern. 
2. all links in the chain are similar to those described herein with some 
sets of links having one orientation and other sets of links having a 
different orientation; or 
3. all links in the chain are similar to those described herein with all 
links in every set of links having the same orientation; or 
4. at least one set of links in a chain is constructed of links as 
described herein with the remainder of the links being similar to those 
taught by the prior art; 
In all forms as noted above, all links in a set of links have the same 
orientation. 
Also comprehended by the present invention is the provision of a chain link 
for a toothed or toed chain for use with sprockets, said link having at 
least one projecting toe and longitudinally spaced apertures with 
associated centers of action translated from a longitudinal reference 
line.

DETAILED DESCRIPTION 
FIGS. 1 and 2 of the drawings illustrate schematically a typical CVT in 
overdrive and underdrive ratios. The CVT comprises a first pulley 11 
connected to a shaft 13 and a second pulley 15 connected to a shaft 17, 
one shaft being a drive shaft and the other a driven shaft. The pulley 11 
comprises flanges 21 and 23 and the pulley 15 comprises flanges 25 and 27. 
At least one flange of each pulley is axially movable relative to its 
respective shaft, so as to change the effective diameter of the pulley and 
vary the drive ratio between the shafts. Generally, mechanical or 
hydraulic or electrical means, or mixtures thereof, are provided for 
axially moving one flange of a pulley relative to the other flange of the 
pulley, but such means are outside the purview of this invention and will 
not be described. The pulleys are connected by a power transmission belt 
29. 
FIG. 3 illustrates a straight pitch chain link 31 which may be used in 
conventional lacing patterns for a drive chain. This link consists of a 
metal member having substantially parallel longitudinal edges 33 and 35 
with shaped end edges 37 and 39 joined by rounded corners 41 and 43. Link 
31 includes a pair of longitudinally spaced generally symmetrical 
apertures 45 and 47 on a center line 48 adapted to receive a suitable 
pivot means 49, such as a symmetrical pin and rocker shown in FIG. 8, with 
each aperture having a plane of symmetry 49A and 49B. The planes of 
symmetry 49A and 49B for apertures 45 and 47 are rotated approximately 
3.5.degree. in opposite directions, and a reference line 51 extends 
longitudinally coincident with the bottom edge 35 of the link. Centers of 
action 53,53 for the rocking surfaces of the pins 49 are equally spaced 
from the reference line 51. 
As seen in FIG. 4, a straight pitch chain providing pitch line 55 having 
suitable load blocks, such a shown in FIG. 7, circumferentially engage a 
pulley, shown schematically, so that the joint radii 57 of the links are 
equal in a regular chordal action. Also the articulation angles 
.alpha..sub.1, .alpha..sub.2, .alpha..sub.3, etc. are equal. Thus, the 
regular engagement of the straight pitch chain on the pulley generates 
noise containing rhythmic impulses that are objectionable to humans. 
FIGS. 5 and 6 illustrate assembly details of a chain-belt constructed 
according to this invention. The chain-belt in FIG. 5 (only a segment of a 
continuous loop with only a few load blocks assembled therewith being 
shown) is generally identified as 61 and comprises a plurality of links 63 
arranged as sets of links 65 and 67 (a typical link 63 is illustrated in 
FIG. 8 in an enlarged scale and in FIGS. 9, 10, 11 and 12 in various 
orientations, the links being identified as 63A, 63B, 63C and 63D), each 
set being interleaved with the next adjacent set. The sets of links are 
divided into sub-sets 65A, 65B and 67A, 67B. The lacing of the chain 61 is 
in a 10-8-10-8 pattern, although for narrower chains, a 6-8-6 pattern may 
be used. Each link 63, (see also FIG. 8) defines a pair of longitudinally 
spaced symmetrical apertures 69 and 71. The apertures in a set of links 
are transversely aligned with one another to form rows of apertures and 
when interleaved, one row of apertures of a set of links is transversely 
aligned with a row of apertures in the interleaved adjacent set of links. 
Pivot means 73 received in the aligned apertures joins the interleaved 
sets of links together and permits articulation of one set of links with 
respect to the interleaved sets of links. Pivot means 73 are illustrated 
as rocker joints comprising a pair of symmetrical pins 75. The pins 75 (or 
pin and rocker) have the same cross-section and the apertures 69,71 have 
the same profile as described in the aforesaid copending application, Ser. 
No. 442,386, supra, although circular openings and round pins or pins and 
bushings could be utilized in this embodiment. In an aperture or group of 
apertures, pins 75, 75 are identical and, when installed, are reversed 
relative to each other. Each pin has a bisecting plane of symmetry which 
is coincident with a bisecting plane of symmetry of the aperture in which 
the pin is located. The planes of symmetry of the pins 75 in the apertures 
69 and 71 are indicated by one dimensional lines 75A and 75B in FIG. 8, 
and the lines 75A and 75B also represent, in a similar manner, the planes 
of symmetry of the apertures 69 and 71, respectively. 
A load block 79 encompasses each set of links between the next adjacent 
pivot means 73, and each load block 79 is constructed of one or more 
plates, illustrated as a pair of plates 79A, 79B, which can be stamped 
from strip or sheet stock. Load blocks 79 are generally trapezoidal in 
shape when viewed from the front and each defines a pair of windows 81, 
each window encircling a sub-set of links, with the windows 81 separated 
by a central strut 83 joining the top and bottom of the block. The blocks 
have opposed edges 85 adapted to engage the flanges of the pulleys in a 
CVT, and may be of a configuration such as shown in U.S. Pat. No. 
4,313,730 or copending application, Ser. No. 656,282, filed Oct. 1, 1984. 
It is to be understood that a complete chain-belt 61 comprises a 
continuous loop of joined sets of links constituting a tension member with 
a load block encircling each of the sets of links. 
Each link 63, (see especially FIGS. 8 to 12) defines a pair of 
longitudinally spaced apertures 69, 71 at least one of which is spaced 
from the longitudinal center line 77 of the link, each receiving pivot 
means 73 comprising a pair of pins 75, 75. Each pair of pins defines a 
center of action 87 or 89, as the case may be. The centers of action are 
perpendicular to the plane of the drawing. Each center of action, in the 
embodiment being described, lies in the plane of symmetry represented by 
line 75A or 75B of an aperture and the pivot means therein. The planes 
represented by lines 75A and 75B are also parallel to a longitudinal plane 
represented by reference line 95, see especially FIGS. 8 to 12, coinciding 
with the lower edge of the link. Lines 75A and 75B are parallel and spaced 
from each other, and in the embodiment being described, along with the 
centers of action are spaced unequal distances from reference line 95. 
Each link 63 in a set 65 or 67 of links has the same orientation, but each 
set can be composed of links oriented in a different way than the links in 
other sets. Four such link orientations are illustrated in FIGS. 9 to 12. 
Chains can be composed of conventional links i.e., those links in which 
the planes of symmetry of the apparatus and the pins therein coincide, and 
at least one set of links constructed as described herein, or in a mixture 
of sets of links, each set having a certain orientation. If constructed of 
sets each of differently oriented links, the sets of links can be 
connected in a random pattern or a predetermined pattern to form a 
complete chain of substantially constant pitch. 
In this embodiment, the chain-belt 61 is constructed with all links similar 
in shape to link 63, which can be oriented in four different ways, see 
FIGS. 9, 10, 11 and 12, identified as 63A, 63B, 63C and 63D. Each link 
comprises shaped longitudinally spaced end surfaces 99 and 101, and 
generally straight spaced longitudinal edge surfaces 103 and 105, which 
are substantially parallel to one another and generally perpendicular to 
surfaces 99 and 101, the reference line 95 coinciding with edge 105. 
Surface 99 is joined to surface 103 by a curved surface 107 and an angled 
surface 109, the latter serving as an indicator of the orientation of the 
links in a set (see FIGS. 5 and 8). Curved surface 111 joins surfaces 101 
and 103 while curved surfaces 113 and 115 join surfaces 101 and 99, 
respectively, to surface 105. The curves surfaces 107, 111, 113, and 115 
permit the chain-belt with the load blocks assembled thereon to articulate 
and engage the circumference of the pulleys of the pulley transmission. 
The end surfaces 99 and 101 may be flat and generally parallel to one 
another, so that they can abut other end surfaces during the assembly of 
the chain-belt; otherwise the end surfaces could be curved, if so desired. 
The surfaces 103 and 105 of the links 63 are generally parallel to the 
plane represented by reference line 95 which is also parallel to the 
planes represented by lines 75A and 75B. While a particular outside 
configuration of the links has been described, it is to be understood that 
important features of the invention are not completely dependent on this 
particular configuration; thus other outside configurations could be used 
without departing from the spirit of the invention. 
With reference to FIGS. 8 to 12, planes represented by lines 75A and 75B 
are parallel to the plane represented by reference line 95 and pass 
through the centers of action 87 and 89, respectively. Each center of 
action is spaced a different distance from the plane represented by line 
95 and, likewise, from the edge 105 of each link. Thus, the links may be 
said to have "translated" or "offset" apertures. While the planes 75A and 
75B are offset in different directions from the center line 77 of the 
link, it should be understood that only one plane (75A or 75B) need be so 
offset from the center line 77 to achieve the results of this invention. 
An imaginary line 123 perpendicular to the line 95 and also to the planes 
75A, 75B is essentially the vertical centerline of a load block of the 
chain-belt as constructed in accordance with the teachings herein. This is 
clearly shown in FIG. 13. 
Looking now at FIGS. 13 and 14, a segment 61 of chain constructed of sets 
of links 63 having differently oriented links is shown with the load 
blocks 79 engaging a sheave 121. When a chain is tensioned (and it is 
assumed that the chain or at least a segment thereof is essentially 
longitudinal), a straight line 125 joining the centers of action 87,89 
represents the "line of pull". The line of pull is also identified in FIG. 
6. Planes represented by lines 75A, 75B and 95 (see FIG. 13) define acute 
angles with the line of pull. The acute angle thus defined may be positive 
or negative (an angle is defined as the amount of rotation, in a fixed 
plane, by which a straight line may be changed from one direction to any 
other direction). If the rotation is counterclockwise, the angle is said 
to be positive; if the rotation is clockwise, the angle is said to be 
negative. As clearly shown in the drawings, (FIG. 14 as well as in FIGS. 5 
and 6), each load block is essentially perpendicular to the edge surfaces 
103 and 105 of the links encircled thereby and thus the angular 
disposition of the load blocks 79 to the line of pull is varied either by 
a positive angle "a" or a negative angle "b" depending upon the 
orientation of the links which are joined to form the chain. 
FIG. 15 illustrates how the link construction of this invention when 
assembled in a chain serves to randomize chordal action-induced cyclic 
effects by selectively changing the radius of the articulating, active 
pin. The pitch line--a line joining articulation axes--of a rigid link 
chain, such as the chain described herein for a drive pulley sprocket is 
polygonal rather than circular. This net effect is what is termed "chordal 
action" because there is a radial as well as a longitudinal component of 
motion as the chain encircles the pulley or sprocket. 
The joint radius is selectively changed using the link of this invention. 
There are four possible joint radii, depending upon the orientation of the 
links. Two of these radii are identified with the reference characters 97 
and 99 as seen in FIG. 15. In the system, it has been determined that the 
occurring cyclic noise pattern is changed and is more acceptable to 
humans. 
FIG. 16 is a graph with the sound pressure level in decibels plotted 
against the speed ratio for both a straight pitch chain and the improved 
chain. The solid line represents the sound levels recorded for the 
improved chain showing the dependency of the noise level on the chordal 
action of the links and the broken lines represent the sound levels for a 
straight pitch chain using blocks with multiple windows and links of equal 
pitch joined by pins similar to those illustrated herein. The same 
equipment was used to test the chain-belt and to record the sound level 
for the chain-belt of this invention and the one described immediately 
above. When the two graphs are compared, it is obvious that the sound 
level in decibels produced by the chain-belt of this invention is less 
than that produced by the immediately described multiple-window block 
chain-belt. The range of sound pressure levels for the prior art 
chain-belt is from approximately 72.5 decibels to approximately 94 
decibels whereas that for the chain-belt of this invention is from 
approximately 65 decibels to approximately 85 decibels. The reduction in 
sound levels for the chain-belt of this invention is readily apparent. 
Chains constructed according to this invention have been noise rated 7 and 
above on a 1 to 10 scale, with the more acceptable rating being higher 
numbers. 
The improved chain for which the graph of FIG. 16 was made had 78 sets of 
links arranged as follows: 
______________________________________ 
SET LINK ORIENTATION 
______________________________________ 
1 63D 
2 63B 
3 63A 
4 63C 
5 63D 
6 63B 
7 63A 
8 63C 
9 63D 
10 63B 
11 63A 
12 63C 
13 63D 
14 63B 
15 63A 
16 63C 
17 63A 
18 63C 
19 63A 
20 63C 
21 63A 
22 63C 
23 63D 
24 63B 
25 63D 
26 63B 
27 63D 
28 63B 
29 63D 
30 63B 
31 63A 
32 63C 
33 63A 
34 63C 
35 63A 
36 63C 
37 63A 
38 63C 
39 63A 
40-78 repeat of 1-39 
______________________________________ 
FIG. 17 of the drawings discloses an alternate form of chain link 163 
similar to the link 63 having a pair of longitudinally spaced apertures 
169 and 171 receiving suitable pivot means and adapted for interleaving in 
sets of links as previously described and permitting articulation of one 
set of links relative to an adjacent set. The pivot means comprises a pair 
of pins 175 having the same cross-section and opposite orientation. As in 
the previous embodiment, the articulation axes are perpendicular to the 
plane of the drawing. 
At least one, and preferably both of the apertures 169 and 171 are 
laterally offset from the center line 177 for the link, and thus unequally 
spaced from reference line 195, and both apertures are rotated 
approximately 3.degree. 16' in the same direction so that the lines 175A 
and 175B of aperture symmetry are again parallel to each other, although 
the apertures may be rotated by unequal angles. The outside shape and 
configuration of the link 163 is substantially identical to that of the 
link 63 seen in FIG. 8 with reference line 195 coinciding with the lower 
edge of the link. By rotating the apertures 169 and 171, the cross 
sections of the pivot members or pins 175 are also rotated to shift the 
centers of action 187 and 189 as shown relative to the reference line 195 
so as to be unequally spaced therefrom. As the centers of action have been 
shifted, the line of pull through these centers is altered as is the pin 
loading to decrease wear on the links and pins. The operation of the 
chain-belt incorporating the links 163 is essentially the same to that 
described for the first embodiment. 
Also, it can be seen that the link 163 has four possible orientations in 
the same manner as shown in FIGS. 9 to 12. Thus, the links in a 
chain-belt, depending on their orientation, will approach a pulley at 
different angles to the line of pull and at different joint radii relative 
to the pulley. The joint radius is selectively changed using the link 163, 
with four possible joint radii; two of which are larger and two of which 
are smaller than the joint radius of a straight pitch link. 
In FIG. 18 of the drawings, a third embodiment of chain link 263 is shown 
wherein the link has a pair of longitudinally spaced and laterally offset 
apertures 269 and 271; one or both apertures being offset from the center 
line 277 of the link. However, in this embodiment, the apertures are 
rotated in opposite directions for approximately 3.degree. 16', although 
unequal angles of rotation may be used. Thus, aperture 269 is rotated 
counterclockwise and aperture 271 is rotated clockwise. That orientation 
results in a shift of the centers of action 287 and 289 for the pins 275, 
or pin and rocker, relative to the reference line 295, but unequally 
spaced therefrom. This embodiment provides a line of pull 125 through the 
centers of action 287 and 289 and provides a top and a bottom orientation 
for the link; so that only two orientations of the link are practical from 
the standpoint of pin loading; i.e., the link can be rotated end-for-end 
about a vertical axis but not rotated about the horizontal longitudinal 
axis. Also, the lines of aperture symmetry 275A and 275B are not parallel 
but intersect in this link embodiment. 
In the alternative, the aperture 269 of this link may be rotated clockwise 
and the aperture 271 rotated counterclockwise. This rotation will reverse 
the top and bottom orientation of the link from that shown in FIG. 18. 
FIG. 19 relates to the utilization of the present invention with a chain 
link 363 of the toothed or toed type utilized with a sprocket or gear (not 
shown). This link includes an elongated body with a pair of longitudinally 
spaced apertures 369 and 371, and a pair of depending teeth or legs 378 
and 379 defined by curved inner flanks 381 and 383 separated by a crotch 
385 and outer flanks 391 and 393. A reference line 395 extends 
longitudinally through the teeth of the link, the line intersecting the 
outer surfaces 391, 393 of the teeth at equal angles .theta.; the 
apertures 369 and 371 being unequally vertically spaced from the reference 
line 395. The axes of articulation 375A and 375B of apertures 369 and 371, 
respectively, are parallel to the reference line and each other, and the 
centers of action 387 and 389 of the pairs of pins 375 are unequally 
spaced from reference line 395. 
The apertures may only be translated as shown in FIG. 19, or the apertures 
may also be rotated both in the same direction or in opposite directions 
of rotation in a similar fashion to that shown in FIG. 17 or 18, with 
attendant shifting of the centers of action. It is believed that this 
chain link will also effect noise reduction as that for the drive chain 
discussed previously. 
FIG. 20 illustrates a further embodiment of chain link 463 comprising an 
elongated link with longitudinally spaced apertures 469 and 471 on a 
longitudinally extending line 477 of the link parallel to the upper edge 
473. However, rather than translation of the apertures, the lower edge or 
reference line 495 is oriented at a small angle to the upper edge 473 so 
that the edges converge toward the right hand side and the apertures are 
unequally spaced from the line 495. Engagement of this link and load block 
with a drive pulley, the link being capable of four possible orientations, 
overcomes the objectionable noise problem in the same general manner as 
the previous link embodiments. 
Another embodiment of chain line 563 is shown in FIG. 21 wherein the link 
configuration is substantially as shown in FIG. 8, with the link having a 
pair of spaced symmetrical apertures 569 and 571 positioned on the 
longitudinal center line 577, with symmetrical pins 575,575 forming a pin 
and rocker arrangement. Rather than a vertical translation of the 
apertures to shift the centers of actions relative to the center line 577, 
the center of action 587 for opening 569 is located on the center line 577 
while the aperture 571 and pins 575,575 are rotated in a clockwise 
direction for a small angle of approximately 3.degree. to 4.degree.. This 
rotation shifts the center of action 589 away from the center line to 
provide unequal spacing of the centers of action relative to the reference 
line 595. The line of pull 125 passes through the centers of action at an 
acute angle to the reference line 595 through the link. 
The link 663 shown in FIG. 22 has the same general configuration as the 
link 63 shown in FIG. 8, except the longitudinally spaced apertures 669 
and 671 are circular openings and the pins 675 are cylindrical pins 
extending through the apertures. At least one opening is vertically offset 
from the longitudinal center line 677 of the link, which results in the 
apertures being unequally spaced from the reference line 695 coinciding 
with the lower edge of the link. This link will also provide the 
randomization that will act to reduce the noise problem for the chain. 
A chain-belt constructed of links such as those illustrated in FIGS. 8 to 
12 or in FIG. 17, 18, 20 21 or 22 will include load blocks as illustrated 
in FIGS. 5, 6 and 7. Where the apertures in links 163,263, 363 and 563 are 
rotated, it is apparent that the configuration of the aperture will be a 
non-circular symmetrical opening. The appended claims are intended to 
cover all reasonable equivalents of the claimed structure.