KR20060047559A - High-performance silent chain - Google Patents

Abstract

The hybrid roller / silent chain of the present invention has the wear resistance of the roller chain combined with the noise performance of the silent chain. This is achieved by the use of transverse load support elements that allow increased load area for the articulated members of the chain by allowing loads to be transferred through both the inner and outer diameters of the elements in the same plane. In some embodiments, the transverse load bearing element is a bushing. In another embodiment, the element is a protrusion extending from the non-guiding row internal link.

Silent Chain, Load-bearing Element, Cylindrical Pin, Guide Link, Wear Resistant, Joint Member

Description

High-Performance Silent Chain

1 is a cross-sectional view of a bush-type roller chain of the prior art.

2A is a top view of a typical prior art silent chain.

FIG. 2B is a side view of the prior art silent chain of FIG. 2A; FIG.

3 is a cross-sectional view of an embodiment of the present invention.

4 is a cross-sectional view of another embodiment of the present invention.

5A is a cross-sectional view of another embodiment of the present invention.

5B is a side view of the guide link of FIG. 5A.

5C is a side view of the toothed link of FIG. 5A.

6 is a cross-sectional view of another embodiment of the present invention.

7 is a cross-sectional view of an embodiment of the present invention using both the inner and outer surfaces of a bushing as a support area.

8 is a side view of the chain link with a cutaway view of the pin and bushing along cut line 8-8 of FIG.

9A is a cross-sectional view of the double width version of FIG. 3A.

9B is a sectional view of a modification of FIG. 9A.

10 is a cross-sectional view of an embodiment of the present invention without a guiding link in the center of the chain racing.

11 is a sectional view of a modification of the embodiment of FIG. 10.

12 is a cross-sectional view of an embodiment composed of fewer types of components.

13A is a cross-sectional view of an embodiment of the present invention without a bushing.

FIG. 13B is a cross sectional view of the non-guiding rows of internal links of FIG. 13A with the protrusion traveling to the right;

FIG. 13C is a cross sectional view of the non-guiding rows of internal links of FIG. 13A with the projections proceeding to the left;

14 is a cross-sectional view of the double width version of FIG. 13.

* Description of the symbols for the main parts of the drawings *

22, 32, 34: guide link 24: internal link

26: outer surface 28: load bearing element

30: pin 40: inner surface

100: centerline

This application is part of a series of pending US application Ser. No. 10 / 650,539, filed August 28, 2003, entitled "IMPROVED SILENT CHAIN". Claimed under 35 USC §120 of the US patent application is claimed herein, the above application is incorporated herein by reference.

The present invention relates to the field of silent chains. Specifically, the present invention relates to improvements in silent chains that are commonly available. More specifically, the present invention relates to a modification of a commonly available silent chain having a transverse load bearing element that allows for increased support area for the articulating member of the chain.

Roller chains and silent chains are known in the art. Both types of chains have known applications in the automotive industry.

U. S. Patent No. 6,450, 911 discloses an outer circumferential surface of a silent chain comprising a plurality of rows of insertions of link plates articulated together by joint pins. The link plate further has a tubular portion that projects continuously from one surface of the link plate and defines each outer circumferential surface of the pin hole. The tubular portion has a height substantially equal to the thickness of the link plate. The tubular part weights the contact area between the plate and the joint pin. The tubular portion also allows the plate to maintain sufficient stiffness and strength without narrowing the web width between the outer or inner flanks of each pin hole and the corresponding tooth. Silent chains are relatively lightweight as a whole. However, the outer circumferential surface of US Pat. No. 6,450,911 has the disadvantage of including an increased width of each strand of the chain. In addition, more complex manufacturing procedures may be inherently needed to form chain links.

U. S. Patent No. 6,485, 385 discloses three structural components that together form a single guiding link of a silent chain. Two guide plates, at least one guide link plate disposed between the guide plates, and two circular connector pins press-fitted to the guide plates are given by the formula (P _m + D _m -D _p ') -P _g ' = Configured to satisfy zero. P _m is the link plate pitch expressed by the distance between the pin hole centers in the guide link plate. D _m is the inner diameter of the pin hole in the guide link plate. D _p ′ is the outer diameter between the circular connector pins that are press fit in each guide plate. P _g ′ is the post-press-fitting guide plate pitch represented by the distance between the pin hole centers in each guide plate press-fitted by circular connector pins. In the assembled silent chain, each circular connector pin extension has its outer circumferential surface in contact with the inner circumferential surface of the mating pin hole of the articulated link and the guide link plate. The articulated link moves relative to the pin and forms a support area. However, the pin outer circumferential surface in contact with the inner circumferential surface of the mating pin hole of the articulated link and guide link plate has the disadvantage of including the limitation of the support surface area for the above-mentioned contact.

The chain industry continues to study better performance in silent chains. There is a need in the art for silent chains with increased contact or support surfaces of the articulated parts of the chain.

A bush-type roller chain is shown in cross section in FIG. 1. Roller chains generally have very good wear performance due to the full length support between the pin 14 and the bushing 12. As the pin 14 rotates in the bushing 12, the pin 14 is well supported along the entire length of the bushing 12. The interference fit between the pin 14 and the bushing 12 provides good wear resistance. The roller chain further comprises two types of links 16 and links 18. One type 16 is known as a bush row link. Another type of link 18 is known as a pin row link.

Noise produced by the chain drive results from various sources. In the roller chain drive, noise is generated, in part, by the collision between the chain and the sprocket at the start of the linkage. The amount of noise or noise level of the impact is influenced, among other things, by the speed of the collision between the chain and the sprocket that engages it. The mass of the chain roller in contact with the sprocket at a specific moment or time increment likewise affects the noise level.

A number of efforts have been made to reduce the overall noise level and pitch frequency noise distribution of the automobile chain drive and thereby minimize the undesirable effects of pure sonic tones. Silent chains are typically used in automotive applications where noise generation should be minimized. Modifications of the link flank shape and profile to significantly reduce the noise level are known.

Roller chains are used in automotive applications. However, roller chains are generally limited to applications where noise generation is not the main issue. Roller chains are characterized by abrasion resistance exhibited by these parts.

A typical silent chain is shown in Figures 2A and 2B. The silent chain includes a guide link string and a non-guidance link string that are alternately connected together in an unauthorized manner. Typically, the guide link strings each have a pair of guide plates 15 and at least one inner link plate 13 disposed between the guide plates. The guide plate 15 and the inner link plate 13 each have a pair of pin holes or openings 19 spaced apart in the direction of movement of the silent chain. The non-guiding link string generally has two or more inner link plates 11. Like the non-guiding row inner link plate 11, the guide plate 15 and the guiding row inner link plate 13 each have a pair of spaced apart pin holes 19. The guide plate 15, the guide row inner link plate 13 and the non-guide row inner link plate 11 are lateral alignment pin holes 19 of the non-guide row inner link plate 11 and the guide row inner link plate 13. It is articulated together by a connector pin 17 inserted through it. The connector pin 17 may be a round pin or a pair of rocker joint pins.

Silent chains generally have poor wear resistance due to the relatively short and poor quality support area between the non-guiding row inner link plate and the pins. The available support length is considerably smaller than roller chains with the same total width. In addition, in a silent chain, the support surface generally consists of a plurality of inner link openings rather than the continuous bushing bores used in the roller chain.

One exemplary use of the silent chain is to transfer power between the drive sprocket and the driven sprocket through the interlocking engagement of the sprocket and the chain. As a practical example, the silent chain is wound around the crankshaft sprocket or camshaft sprocket of the motor vehicle engine or around the sprocket of the transmission unit. When the silent chain begins to interlock with the sprockets, noise occurs due to events such as collisions between the flank surfaces of each link plate and the toothed flanks of the sprockets.

One known advantage of silent chains is the improved NVH (noise-vibration-noise) properties due to the coupling of the silent chain toothed flanks on the sprockets. On the other hand, the roller chains have their inherent advantageous properties as described above. As can be appreciated, it is desirable to combine the useful properties of the roller chain and the silent chain in a unique manner to provide a silent chain that is adapted to combine the wear characteristics of the roller chain with the NVH properties of the silent chain. It is also desirable to provide excellent wear characteristics to the roller chain by providing increased total support area between the articulated parts of the chain.

An improved silent chain is provided that has better wear characteristics than roller chains and much better wear characteristics than conventional silent chains. An improved silent chain is provided that has the noise-vibration-noise (NVH) of a conventional silent chain. An improved silent chain is provided having a weight similar to a conventional silent chain.

The chain of the present invention includes a plurality of links. Each link includes a pair of link openings, each link opening having an opening diameter and an inner opening surface. The chain also includes a plurality of transverse load bearing elements. Each element has an outer element surface having an outer element diameter and an element opening having an inner element surface and an inner element diameter. Each element passes through at least one link opening. The chain also includes a plurality of cylindrical pins. Each pin includes an outer fin surface and an outer fin diameter and passes through at least one link opening and through at least one element opening. The outer pin diameter is smaller than the inner element diameter such that the outer pin surface is movable relative to the inner element surface. The opening diameter of the at least one link is larger than the outer element diameter such that the outer element surface is movable relative to the inner opening surface of the link. The arrangement is such that the outer fin surface is supported and articulated with respect to the inner element surface and the inner opening surface, through which the element passes, is supported and articulated with respect to the outer element surface. The use of both inner and outer element surfaces to support loads in the plane of the link allows for increased support area for a given chain width.

In an embodiment of the invention, the plurality of links further comprises a plurality of first links, a plurality of second links and a plurality of external links. Each transverse load bearing element passes through at least one second link opening. Each pin passes through at least one outer link opening. The links are arranged in rows alternately between a first column comprising at least one first link and a second column comprising at least one outer link and at least one second link at each edge of the chain. The first link and the transverse load bearing element are fixed such that no relative motion occurs between the first link and the transverse load bearing element. The second link opening diameter is larger than the outer element diameter such that the outer element surface is movable relative to the second link inner opening surface. The outer link opening diameter and the pin diameter are hermetically fitted such that relative motion does not occur between the outer link inner opening surface and the outer pin surface. The arrangement consists of alternating a first row of first links with the chain rigidly attached to the transverse load bearing elements, and a second row of movable links on the transverse load bearing elements and a second row of external links attached to the pins, The first row and the second row are articulated together along the direction of travel.

It is preferable that a 1st row is a non-guided row. Preferably, the first link is an inverted toothed link. The outer link is preferably an inverted toothed link. The external link is preferably a guide link. Preferably, the second link is an inverted toothed link. In some embodiments, the second link is located along the centerline of the chain. In one embodiment of the invention, the second link is a non-inverted center guide link.

In some embodiments of the invention, the transverse load bearing element is a bushing. In another embodiment, the first link further comprises a first link body comprising a pair of first link openings. Each first link opening has a first link opening diameter and a first link inner opening surface. The first link further comprises a transverse load bearing element, each element comprising a pair of protrusions. Each protrusion extends laterally from the first link body, respectively, in each first link opening, thereby increasing the width of the first link inner opening surface and including an outer protrusion diameter and an outer protrusion surface.

Various embodiments of the present invention have various lacings of links. In some embodiments, each pin passes through the link in a sequential order of an outer link, at least one first link, at least one second link, at least one first link, and an outer link. In one embodiment, each at least one first link in sequential order includes two first links. In one embodiment, at least one second link in sequential order includes two second links. In one embodiment, each at least one first link in sequential order includes two first links and at least one second link in sequential order includes two second links. In another embodiment of the present invention, the sequential order further includes a third link between two second links, wherein the third link is in the first column and is a non-inverted link.

In another embodiment, the inner element surface is discontinuous on each pin such that each pin passes through two transverse load bearing elements. In one embodiment, each pin has an outer link, at least one first link, at least one second link, at least one first link, at least one outer link, at least one first link, at least one first Pass the links in a sequential order of two links, at least one first link and an outer link. In another embodiment, the two transverse load bearing elements are spaced on the pin by at least one outer link.

In another embodiment of the invention, the two transverse load bearing elements are separated by at least one third link, each third link being in a second row and comprising a pair of third link openings, each of The third link opening has a third link opening diameter and a third link inner opening surface. In one embodiment, the third link opening diameter is larger than the pin diameter such that the outer pin surface is movable relative to the third link inner opening surface. In another embodiment, the third link opening diameter and the pin diameter are hermetically fitted such that relative motion does not occur between the third link inner opening surface and the outer pin surface. In one embodiment, each pin has an outer link, at least one first link, at least one second link, at least one first link, at least one third link, at least one first link, at least one Pass the links in a sequential order of a second link, at least one first link, and an outer link. In another embodiment, each pin has an outer link, at least one first link, at least one second link, at least one first link, at least one second link, at least one first link, at least one Pass the links in a sequential order of a second link, at least one first link, and an outer link. In another embodiment, each at least one second link in sequential order includes two second links.

The present invention combines the characteristics of the roller chain and the silent chain of the prior art in a unique manner in that the wear characteristics of the roller chain and the NVH characteristics of the silent chain are combined in a unique whole. The combined integral of the present invention provides an increased total support area between the articulated parts of the chain, thereby providing excellent wear characteristics to the roller chain. In all embodiments of the invention, the outer and inner surfaces of the transverse load bearing elements are used to increase the load bearing area for a given chain width. In a first set of embodiments, the load bearing bearing comprises a bushing. In a second set of embodiments, the load bearing bearings comprise protrusions on the non-guiding row internal links.

An embodiment of the present invention that discloses a basic concept is shown in FIG. 3. In this embodiment, two pairs of inner links 32 are provided on the non-guided row. Two internal links 34 on the guide train are also provided. In addition, a pair of external guide links 22 are provided. The guide row inner rank 34 is located at the center of the endless chain having a centerline 100 that defines two links 34. Centerline 100 also partitions guiding link 22 and non-guiding row internal link 32.

In FIG. 3, the chain is guided on a sprocket (not shown) by a pair of outer guide links 22. Each link comprising guide link 22 has a pair of holes or annular openings at each end. Within each hole there is a surface. Each hole also receives a connection member, such as a pin 30 or bushing 28 for connecting various links to an endless chain. Each non-guided row inner link 32 has a pair of holes or annular openings at each end. Within each hole of these links 32 there is a pressure fit surface on the bushing 28 such that relative movement does not occur between them. Each guide row inner link 34 has a pair of holes or annular openings at each end. Within each hole of these links 34 is a surface 33 used as a support area above the bushing 28 where relative movement between them occurs.

3 illustrates a portion of the inventive concept in which a set of transverse load bearing elements 28 is interposed between a portion of the link and the pin 30. In FIG. 3, the transverse load bearing element is a bushing 28. Specifically, the non-guided rows 32 and guided row internal links 34 have bushings 28 interposed between their holes and the pins 30. Each bushing 28 includes an outer surface 26 and an inner surface 40. The outer surface 26 is defined by a set of points distributed in the O.D. (outer diameter) of the bushing 28. The inner surface 40 is defined by a set of points distributed in the I.D. (inner diameter) of the bushing 28. Two links 34 are provided across the chain in this embodiment. In each hole of these links 34, the inner surface is defined as the support region 33 which comes into contact with the outer surface 26 of the bushing 28. This contact is not firmly attached and allows relative movement of the two contact surfaces. Four additional links 32 across the chain are provided in the non-guided string interposed between the guide string link 34 and the outer guide link 22. Both guide row 34 and non-guided row links 32 have inverted teeth. However, each hole of the non-guiding row link 32 is firmly attached on the outer surface 26 of the bushing 28 in contact with it.

As can be appreciated, the present invention provides a link 34 having a hole having an inner surface that fits on the outer surface 26 of the bushing 28, thereby reducing the load on the chain assembly as a whole. It provides an additional support area for supporting. The total support area of the present invention is the support area of the fan 30 versus the bushing 28, which is an area arranged for contact between the inner surface 40 of the bushing 28 and the outer surface of the fin 30, and the bushing ( It is the sum of the bushing 28 to the support region 33 of the link 34, which is an area arranged for contact between the outer surface 26 of 28 and the inner surface of the annular opening of the link 34. A portion of the tensile load in the chain can be supported by the interface of the bushing 28 with respect to the pin 30, and the rest of the tensile load is supported by the bushing 28 outer diameter (OD) interface to the link 34. By making it possible, the overall unit load between the pin 30 and the bushing 28 is reduced in comparison with conventional roller chains, thereby resulting in reduced wear of the relevant part of the final endless chain. The torque transmission contact between the chain and the sprocket is through inverted toothed links 32, 34, thereby providing the NVH performance of the silent chain.

A second embodiment is shown in FIG. Similar to FIG. 3, an endless chain with links 22, 32, 34 is provided. Bushing 28 and pin 30 are likewise provided. In this embodiment, only two links 32 are used as non-guided strings. Each non-guideline link 32 is interposed between an external guide link 22 and a guide string link 34. The pair of links is substantially symmetric about the centerline 100 of the chain.

5A to 5C, a third embodiment of the present invention is shown. In this embodiment, the endless chain is guided on the sprocket (also not shown) by the center link 20 on the guide train which fits in the groove (not shown) of the sprocket. The center link 20 is non-inverted in shape as shown in FIG. 5B. The remaining links of this embodiment have inverted teeth. The inner links 24 of FIGS. 5A and 5C are functionally identical, but in most cases are wider than the non-guiding links shown in other embodiments. The inner link 24 is firmly fixed to the bushing 28. By way of example, the link 24 may be interference fit on the bushing 28. Thus, no relative movement occurs between O.D. of the bushing 28 and the inner surface of the link 24. The use of the center guide link in a silent chain is well known in the art, but the present invention provides a center guide link 20 to fit over the outer surface 26 of the bushing 28, thereby supporting the load. Provide additional support area. The total support area of this design is the pin 30 to bushing 28 support area and the bushing 28, which is an area arranged for contact between the outer surface 40 of the bushing 28 and the outer surface of the fin 30. It is the sum of the bushing 28 to the link 20 support area, which is the area disposed for the contact between the outer surface 26 of the inner surface of the hole of the center link guide 20. By supporting a portion of the tensile load at the pin 30 to bushing 28 interface and the remainder of the tensile load at the center guide link 20 to bushing 28 outer diameter (OD) interface, the chain is connected to the pin 30. And a reduced net unit load between the bushing 28 and thereby causing reduced wear of the relevant part of the chain. The torque transfer contact between the chain and the sprocket passes through links 22 and 24 that are inverted tooth shapes, thereby providing the NVH performance of the silent chain.

A fourth embodiment is shown in FIG. This embodiment includes a wider chain with more link elements. A single center guide link 20 is provided along the center line 100 in the first column. In addition, two pairs of parallel inner links 32 are provided for higher strength. In this case, the center guide link 20 and the inner link 32 do not move relative to the bushing 28 O.D. A support region 33 is provided which has an inner opening surface in which the guide row link 34 is articulated against the bushing 28 O.D. The holes in these links 34 are supported against the O.D. of the bushing 28. Again, the pin 30 has the entire support area within the inner diameter I.D. of the bushing 28. As in the previous embodiment, by utilizing the O.D. of the bushing 28 to support the contact with one or more links 34 in the guide row, additional support area between the joint members is provided. The links 22, 32, 34 are in the inverted tooth shape and engage the sprocket teeth, thereby providing the NVH performance of the silent chain.

In any of the above embodiments, the provision of an additional link supported against the O.D. of the bushing reduces the load supported by the pin 30 compared to the roller chain. The reduction of the load supported by the pin 30 reduces the wear between the pin 30 and the bushing 28 and provides the NVH performance of the silent chain by utilizing inverted toothed links to contact the sprockets. This results in a design with superior wear performance compared to the roller chain.

In operation, if there is any imbalance in the load sharing between the links, the part wears and tends to improve the load sharing. For example, if the outer link 22 supports more than ideal loads, the pin 30 wears more quickly at first, and the center link or other links 34 or 20 in the same row until natural balance is achieved. ) To support increased loads. This natural tendency to "wear" into a balanced situation helps to reduce the effect of dimensional tolerances on the performance of the chain.

There are many embodiments of the present invention. The embodiment of the present invention shown in FIGS. 7 and 8 uses both the outer surface 26 and the inner surface 40 of the bushing 28 to support the load, and thus the silent chain links 32 and 34 for NVH. It provides a large support area for wear resistance while enabling the use of. The chain provides at least as much support area as the roller chain. The load is transmitted to both the inner surface 40 and the outer surface 26 of the bushing 28 to distribute the load. In addition, the present invention allows for an increased amount of support area within relatively limited chain widths. The foregoing is shown in FIG. 7, which shows a cross section of the chain using the link of FIG. 8 and in FIG. 8, which is an enlarged side cross-sectional view of the chain employing an embodiment of the invention.

Referring to FIG. 8, which is a partially enlarged side view of a chain employing an embodiment of the present invention, an endless chain link formation, such as guide string link 34, is shown. The link 34 has a pair of openings 38. Each opening 38 possesses a support region 33, which, at its outer surface 26, contacts the bushing. The pin 30 is in contact with the inner surface 40 of the bushing 26. As can be appreciated, the support area 33 increases the total support area to share the load of the endless chain.

More specifically, referring to the cross section shown in FIG. 8, the outer surface of the pin is supported relative to the inner surface of the bushing and articulated by them. The inner surface of the holes in the guide row inner link 34 is supported against the outer surface of the bushing and articulated against them. The use of both the inner and outer surfaces of the bushing in the same plane to support the load allows for an increased support area for a given chain width.

In any of these embodiments, the thickness and number of the various links can be adjusted to optimize the strength and wear resistance of the chain. Diameter of pin, bushing I.D. And bushing O.D. can also be optimized to provide the best combination of strength and wear resistance. By providing a maximum total support area between the joint members of the chain, wear resistance is optimized.

The present invention is an improvement on roller chains with reduced wear by providing a new support surface between the outside of the bushing and one or more load bearing links and allowing for a reduced load through the pins. Also, in a typical roller chain, all tensile loads must pass through the pins, and pin strength limitations can limit the load bearing performance of the chain. The chain of the present invention reduces the pin bending stress and provides increased strength by transferring a portion of the tensile force through the O.D. of the bushing to the load-supporting link. The present invention further improves the roller chain by reducing the noise by providing the inverted toothed links to some links that engage the silent chained sprocket tooth profile.

It should be noted that the present invention also contemplates a double-engaged silent chain that can engage a sprocket or toothed pulley mounted on each driven shaft located inside and outside the chain. As an example, a double-engaged silent chain is used as a timing chain for transmitting rotational motion from the crankshaft of the engine with respect to the shaft of an auxiliary device such as an oil pump, or with respect to the camshaft of the engine. As can be appreciated, a double-engaged silent chain is used when a driven shaft located inside and outside the chain is rotated in the opposite direction.

9-14 show additional embodiments of the present invention that are wider and stronger chains, comparable to double row roller chains. These variants are suitable when higher strength is required for the chain. Any of these chain racing may be suitable for a particular chain design depending on the requirements of that design. Other variations are possible. In all the variants shown, different amounts or thicknesses of links are substituted at arbitrary locations as needed to obtain the required strength and width.

In FIG. 9A, the “guide” link 22 does not engage the sprocket teeth. The inner links 32, 34 are inverted tooth shapes and engage with the sprocket teeth. Some of these internal links 32 are in non-guided rows and other links 34 are in the guide rows of the chain. The pins 30 extend through the width of the chain and two bushings 28 are mounted to each pin 30. This embodiment is a substantially double row or double width version of the embodiment shown in FIG. 3. This type of "double row" racing is where more strength is needed than can be achieved with a "single row" design. FIG. 9B is identical to FIG. 9A, except that a pair of thinner inner links 32 than the thicker link 32 shown in FIG. 9A is used.

10 shows a preferred embodiment where there is no guide link 22 at the center of the chain racing. The chain has a nonguided internal link 32, as in FIG. 9A. The chain also has a guide train inner link 34 as also in FIG. 9A. The center link 36 is in the guide row but consists of an inverted tooth shape. This design operates on simple sprockets because only the guiding link is on the outside of the chain. In this design, the non-guiding string internal link 32 is connected to the O.D. Firmly seated above, the guide row inner link 34 is mounted to the O.D. It is loosely fitted above, articulated with respect to the bushing 28, and the central link 36 is fitted over the pin 30. The center guide train inner link 36 is forcibly fit or slip fit into the pin 30, depending on the particular design requirements. More or fewer arbitrary internal links 32, 34, 36 may also be used depending on the specific design and performance requirements for the chain assembly.

FIG. 11 shows a racing similar to that shown in FIG. 10 with fewer central guideline inner links 36 and fewer non-guideline inner links 32.

FIG. 12 shows a racing in which the bushing 28 consists of a cantilevered structure towards the center 100 of the racing. This design has advantages over the embodiment shown in FIGS. 9A-11 in that only three different link types are required: guide link 22, non-guided inner link 32 and guided inner link 34. Have All guide string internal links 34 are O.D. Fitted on top, which provides an additional support area for wear resistance. This variant provides the maximum support area for a given chain width. Again, the number of links varies as needed for any particular design.

In the final set of embodiments of the invention, the transverse load bearing element comprises a protrusion, which is attached to the non-guiding row inner link. These embodiments do not have a bushing as a separate element.

FIG. 13A removes the bushing as a separate component and provides the function of the bushing 28 by providing a protrusion 43 on the inner link 42. The link protrusion 43 is easier to see in FIGS. 13B and 13C. This is an improvement over Saito (US Pat. No. 6,540,911), since both the outer diameter and the inner diameter of the protrusion 43 are used for the support area. Bushing 28 O.D. for support areas, except that protrusion 43 provides the function of bushing 28. And I.D. All of the same advantages of using all apply to this embodiment. The non-guided internal link 42 may be oriented in either direction, as shown in FIGS. 13B and 13C.

FIG. 14 shows the “double row” racing of the variant of FIG. 13A. The center guide link 22 shown in this embodiment may also be replaced by the inner link 36, similar to the modification made from FIGS. 9A-10.

In summary, the present invention provides a wider and stronger chain. In one embodiment, the chain has a guide link at the center of the racing. In another embodiment of the invention, the chain has an inner link at the center of the racing. In one embodiment of the invention, the bushing O.D. A bushing with a cantilever structure that is asymmetrical with respect to the interference fit link is used. Finally, projections I.D. for the support area to resist wear. And O.D. While still utilizing all, the concept of using link projections is shown to replace the bushings.

The present invention is an improvement on roller chains with reduced wear by providing a new support surface between the outside of the bushing and one or more load bearing links and allowing for a reduced load through the pins. Also, in a typical roller chain, all tensile loads must pass through the pins, and pin strength limitations can limit the load bearing performance of the chain. The chain of the present invention reduces the pin bending stress and provides increased strength by transferring a portion of the tensile force through the O.D. of the bushing to the load-supporting link. The present invention further improves the roller chain by reducing the noise by providing the inverted toothed links to some links that engage the silent chained sprocket tooth profile.

Accordingly, it is to be understood that the embodiments of the invention described herein are merely illustrative of the application of the principles of the invention. Reference herein to details of the illustrated embodiments is not intended to limit the scope of the claims, which themselves refer to these features deemed to be essential to the invention.

Claims (26)

A plurality of links each including a pair of link holes each having a hole diameter and an inner opening surface; A plurality of transverse load bearing elements each comprising an outer element surface having an outer element diameter and an element hole having an inner element surface and an inner element diameter, each passing through at least one link opening; A plurality of cylindrical fins each comprising an outer fin surface and an outer fin diameter, passing through at least one link hole and passing through at least one element hole, wherein the outer fin diameter is such that the outer fin surface is with respect to the inner element surface; A plurality of cylindrical pins smaller than the inner element diameter to be movable; The hole diameter of the at least one link is greater than the outer element diameter such that the outer element surface is movable relative to the inner hole surface of the link, The outer pin surface is supported and articulated relative to the inner element surface and the inner bore surface through which the element passes and is supported against the outer element surface and articulated to support the load in the plane of the link. The use of both the inner element surface and the outer element surface for the chain allows for increased support area due to the desired chain width. The chain of claim 1 wherein said transverse load bearing element is a bushing. The method of claim 1, wherein the plurality of links further comprises a plurality of first links, a plurality of second links, and a plurality of external links, Each transverse load bearing element passes through at least one second link hole, Each pin passes through at least one outer link hole, The links are alternately arranged in rows between a first column comprising at least one first link and a second column comprising at least one outer link and at least one second link on each edge of the chain, The first link and the transverse load bearing element are fixed such that relative motion does not occur between the first link and the transverse load bearing element, The second link hole diameter is larger than the outer element diameter such that the outer element surface is movable relative to the second link inner hole surface, The outer link opening diameter and the pin diameter are hermetically fitted such that relative motion does not occur between the outer link inner hole surface and the outer pin surface, The chain is alternately comprised of a first row of first links rigidly attached to the transverse load bearing element, and a second row of movable second links on the transverse load bearing element and a second row of outer links attached to the pin; Wherein said first and second columns are articulated together along the direction of travel. 4. The apparatus of claim 3, wherein the first link further comprises a first link body having a pair of first link holes each having a first link hole diameter and a first link inner hole surface, The transverse load bearing elements each comprise a pair of protrusions each extending laterally from the first link body in a first link hole, thereby increasing the width of the first link inner hole surface, the outer protrusions A chain comprising a diameter and the surface of an outer protrusion. 4. The chain of claim 3 wherein said first link is an inverted tooth shaped link. 4. The chain of claim 3 wherein said second link is an inverted tooth shaped link. 4. The chain of claim 3 wherein the outer link is an inverted tooth shaped link. 4. The chain of claim 3 wherein said outer link is a guide link. 4. The chain of claim 3 wherein said second link is located along a centerline of the chain. The chain of claim 9, wherein the second link is a non-inverted center guide link. 4. The chain of claim 3 wherein each first row is a non-guided row. 4. The chain of claim 3, wherein each second row includes a plurality of second links symmetrically located along a centerline of the chain. 4. The chain of claim 3 wherein each pin passes through the link in a sequential order of an outer link, at least one first link, at least one second link, at least one first link, and an outer link. 14. The chain of claim 13 wherein each of said at least one first link in said sequential order comprises two first links. 14. The chain of claim 13 wherein said at least one second link in said sequential order comprises two second links. 16. The chain of claim 15 wherein each of said at least one first link in said sequential order comprises two first links. 17. The chain of claim 16 wherein the sequential order further comprises a third link between the two second links, wherein the third link is in a first row and is a non-inverted link. 4. The chain of claim 3 wherein the inner element surface is discontinuous on each pin such that each pin passes through two transverse load bearing elements. 19. The apparatus of claim 18, wherein each pin is an outer link, at least one first link, at least one second link, at least one first link, at least one outer link, at least one first link, at least one. A chain passing through the links in a sequential order of a second link, at least one first link, and an outer link. 20. The chain of claim 19 wherein the two transverse load bearing elements are spaced on the pin by the at least one outer link. 19. The apparatus of claim 18, wherein the two transverse load bearing elements are separated by at least one third link, each third link in the second row and including a pair of third link holes, each And the third link hole has a third link hole diameter and a third link inner hole surface, wherein the third link hole diameter is larger than the pin diameter such that the outer pin surface is movable relative to the third link inner hole surface. 22. The apparatus of claim 21, wherein each pin has an outer link, at least one first link, at least one second link, at least one first link, at least one third link, at least one first link, at least one. A chain passing through the links in a sequential order of a second link, at least one first link, and an outer link. 19. The apparatus of claim 18, wherein the two load bearing elements are separated by at least one third link, each third link in a second row and including a pair of third link holes, each third link The hole has a third link hole diameter and a third link inner hole surface, and the third link hole diameter and the pin diameter are hermetically sandwiched so that relative motion does not occur between the third link inner hole surface and the outer pin surface. Chain to be fitted. 24. The apparatus of claim 23, wherein each pin is an outer link, at least one first link, at least one second link, at least one first link, at least one third link, at least one first link, at least A chain passing through the links in a sequential order of one second link, at least one first link, and an outer link. 19. The apparatus of claim 18, wherein each pin is an outer link, at least one first link, at least one second link, at least one first link, at least one second link, at least one first link, at least A chain passing through a link in a sequential order of one second link, at least one first link, and an outer link. 27. The chain of claim 25 wherein each of said at least one second link in said sequential order comprises two second links.

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