US20010000781A1 - Short pitch tooth chain - Google Patents
Short pitch tooth chain Download PDFInfo
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- US20010000781A1 US20010000781A1 US09/742,655 US74265500A US2001000781A1 US 20010000781 A1 US20010000781 A1 US 20010000781A1 US 74265500 A US74265500 A US 74265500A US 2001000781 A1 US2001000781 A1 US 2001000781A1
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- Prior art keywords
- link
- chain
- distance
- aperture
- sprocket
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
- F16G13/00—Chains
- F16G13/02—Driving-chains
- F16G13/04—Toothed chains
Definitions
- the present invention relates to the chain arts, and in particular, a short pitch tooth chain that provides improved noise reduction over conventional tooth chains.
- Drive chain systems and timing chain systems incorporating known chains such as inverted tooth chains and roller chains have several components of undesirable noise.
- a major source of noise is the sound generated as the chain engaging members, such as inverted teeth or rollers, leave the span and collide with a sprocket during meshing. The resulting impact noise is repeated with a frequency generally equal to that of the frequency of the chain meshing with the sprocket. It is known that the impact noise levels associated with chains can be reduced by altering the engagement geometry of the chain and/or sprocket to, in part, reduce the impact energy that must be absorbed during the meshing process.
- the present invention contemplates a new and improved short pitch tooth chain which provides improved noise reduction over conventional inverted tooth chains.
- a tooth chain in accordance with one aspect of the present invention, includes a first link having a first aperture spaced from a second aperture by a first distance; a second link having a first toe spaced from a second toe by a second distance, the second link having a third aperture and being connected to the first link by a first pin extending through the first and third apertures; a third link having a third toe spaced from a fourth toe by the second distance, the third link having a fourth aperture and being connected to the first link by a second pin extending through the second and fourth apertures; and the first distance defining a chain pitch and the second distance defining a sprocket chordal pitch wherein the chain pitch is about twice the sprocket chordal pitch.
- a chain system in accordance with another aspect of the present invention, includes a first sprocket having a first plurality of sprocket teeth spaced apart by a first distance; a second sprocket having a second plurality of sprocket teeth spaced apart by the first distance; a chain wrapped around the first and second sprockets, the chain including a first link having a first aperture spaced from a second aperture by a second distance, a second link having a first toe spaced from a second toe by the first distance, the second link having a third aperture and being connected to the first link by a first pin extending through the first and third apertures, a third link having a third toe spaced from a fourth toe by the first distance, the third link having a fourth aperture and being connected to the first link by a second pin extending through the second and fourth apertures; and the first distance defining a sprocket chordal pitch and the second distance defining
- a chain in accordance with a further aspect of the present invention, includes a first link member having a first aperture spaced from a second aperture by a first distance; a second link member connected to the first link member and having a first toe spaced from a second toe by a second distance, the toes being adapted for engagement with tooth spaces associated with a sprocket, the tooth spaces being spaced apart by a third distance; and the second distance being substantially equal to the third distance, and the second distance being about one half of the first distance.
- a chain system in accordance with yet another aspect of the present invention, includes a first sprocket having a first plurality of tooth spaces spaced apart by a first distance; a second sprocket having a second plurality of tooth spaces spaced apart by the first distance; and a chain including a first link member having a first aperture spaced from a second aperture by a second distance, a second link member connected to the first link member and having a first toe spaced from a second toe by a third distance, the toes being adapted for engagement with the first and second plurality of tooth spaces, and the first distance being substantially equal to the third distance, and the third distance being about one half of the second distance.
- a link member for a chain includes a body portion defining a first toe and a second toe spaced from the first toe by a predetermined distance, the toes adapted for meshing engagement with tooth spaces associated with a sprocket, and the link member further comprising a single aperture extending through the body portion.
- One advantage of the present invention is the provision of a short pitch tooth chain which reduces noise levels by increasing the frequency at which the chain meshes with a sprocket to a level which is inaudible, or at least less audible to the human ear.
- Another advantage of the present invention is the provision of a short pitch tooth chain having a chain pitch value which is approximately twice a sprocket chordal pitch value.
- a further advantage of the present invention is the provision of a chain system having a short pitch tooth chain that reduces noise levels by increasing the frequency at which the chain meshes with a sprocket to a level which is inaudible, or at least less audible to the human ear.
- Yet another advantage of the present invention is the provision of chain system having a short pitch tooth chain with a chain pitch value which is approximately twice a sprocket chordal pitch value.
- the invention may take form in various components and arrangements of components, and in various steps and arrangements of steps.
- the drawings are only for purposes of illustrating a preferred embodiment(s) and are not to be construed as limiting the invention.
- FIG. 1 illustrates a conventional double-toed link for a known inverted tooth chain
- FIG. 2 is a fragmentary view of a conventional inverted tooth chain that incorporates double-toed links of FIG. 1, as the chain engages a conventional sprocket;
- FIG. 3 illustrates a first embodiment of a chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 4 is a top fragmentary view of an exemplary lacing pattern for the short pitch tooth chain of FIG. 3;
- FIG. 5 illustrates a double-toed link of the short pitch tooth chain of FIG. 3
- FIG. 6 illustrates a tension link of the short pitch tooth chain of FIG. 3
- FIG. 7 illustrates a second embodiment of chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 8 is a top fragmentary view of an exemplary lacing pattern for the short pitch tooth chain of FIG. 7;
- FIG. 9 illustrates a double-toed link of the short pitch tooth chain of FIG. 7;
- FIG. 10 illustrates a tension link of the short pitch tooth chain of FIG. 7
- FIG. 11 illustrates a guide link of the short pitch tooth chain of FIG. 7
- FIG. 12 illustrates a spring link of the short pitch tooth chain of FIG. 7
- FIG. 12 a is a side view of the spring link taken along the line 12 a - 12 a of FIG. 12;
- FIG. 13 is an enlarged view of the drive sprocket of FIG. 7 with two double-toed links seated in a tooth space and a third double-toed link being collected from a taut span of the short pitch tooth chain;
- FIG. 14 illustrates a third embodiment of a chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 15 is a top fragmentary view of a first exemplary lacing pattern for the short pitch tooth chain of FIG. 14;
- FIG. 16 is a side view of the lacing pattern taken along the line 16 - 16 of FIG. 15;
- FIG. 17 illustrates a double-toed link of the short pitch tooth chain of FIG. 14;
- FIG. 18 illustrates a first tension link of the short pitch tooth chain of FIG. 14
- FIG. 19 illustrates a side view of the tension link taken along the line 19 - 19 of FIG. 18;
- FIG. 20 illustrates a guide link of the short pitch tooth chain of FIG. 14
- FIG. 21 illustrates a side view of the guide link taken along the line 21 - 21 of FIG. 20;
- FIG. 22 is an enlarged view of the drive sprocket of FIG. 14 with two double-toed links seated in a tooth space and a third double-toed link being collected from a taut span of the short pitch tooth chain;
- FIG. 23 is a top fragmentary view of a second exemplary lacing pattern for the short pitch tooth chain of FIG. 14;
- FIG. 24 is a side view of the lacing pattern taken along the line 24 - 24 of FIG. 23;
- FIG. 25 illustrates a second tension link of the short pitch tooth chain of FIG. 14.
- FIG. 26 illustrates a side view of the second tension link taken along the line 26 - 26 of FIG. 25.
- a conventional double-toed link 10 for a known inverted tooth chain 11 includes a body portion 12 having a first toe 14 spaced from a second toe 16 .
- the toes 14 , 16 consecutively engage adjacent and mutually conforming tooth spaces 17 associated with a sprocket 17 a .
- the link 10 also includes a first aperture 18 and a second aperture 20 spaced apart from the first aperture.
- the apertures 18 , 20 receive conventional pins 21 for joining together a number of different links, including links 10 , to form the known inverted tooth chain 11 .
- a major source of chain drive noise is the sound generated as the chain engaging members, i.e. the toes 14 , 16 , leave the span and collide with the sprocket during meshing.
- the resultant impact noise is repeated with a frequency generally equal to that of the frequency of the chain meshing with the sprocket. It is contemplated herein that the overall noise levels associated with a chain drive system can be reduced by increasing the frequency at which the chain meshes with the sprocket to a level which is inaudible, or at least less audible, to the human ear.
- reducing the chain pitch C p of the conventional link 10 to about 8.0 mm or less is problematic.
- the chain system 30 such as a drive chain system, timing chain system, etc. which incorporates the features of the present invention therein.
- the chain system 30 rotates in a counter-clockwise direction as shown by arrow 32 .
- the chain system 30 includes at least a drive sprocket 34 , a driven sprocket 36 , and a short pitch tooth chain 38 .
- the short pitch tooth chain 38 engages and wraps about sprockets 34 and 36 and has two spans extending between the sprockets, slack strand 40 and taut strand 42 .
- the taut strand 42 is under tension as shown by arrows 44 .
- the short pitch tooth chain 38 includes a number of double-toed links 46 , tension links 48 , and pins 50 interconnecting the links 46 , 48 .
- the links 46 , 48 are each pivotal about the pins 50 so that as the links enter the sprocket wrap, each link may articulate independently about the respective pin to conform with the curvature of the sprocket.
- the links 46 , 48 and pins 50 may be interconnected in various lacing patterns known in the art to produce short pitch tooth chains having different strength and load capacity characteristics.
- An exemplary lacing pattern is shown in FIG. 4.
- the dimensions (e.g. length, width, height, etc.) and material considerations (powdered metal, stamped metal, steel, etc.) of the links 46 , 48 and the pins 50 can be varied to produce chains having different strength and load capacity characteristics in a known manner.
- the double-toed link 46 (FIG. 5) includes a body portion 52 having a first toe 54 spaced from a second toe 56 by a distance T p (toe pitch).
- a central aperture 58 extends through the body portion 52 .
- the toes 54 , 56 engage mutually conforming tooth spaces 59 , 60 (FIG. 3) of the sprockets 34 , 36 , respectively.
- the sprockets 34 , 36 each have sprocket chordal pitch S p which is substantially equal to the toe pitch T p . It should be appreciated that by providing a link 46 with a single aperture therethrough, more link material extends between the aperture and each side edge thereof, relative to the link 10 .
- the tension link 48 (FIG. 6) primarily carries the load on the chain 38 .
- Each tension link 48 includes an arcuate-shaped body portion 62 having a first aperture 64 proximate one end thereof, and a second aperture 66 proximate the other end.
- each tension link 48 carries two double-toed links 46 via two pins 50 each extending through a respective aperture 64 , 66 .
- the chain pitch C p for the chain 38 is defined as the distance between the centers of the apertures 64 , 66 .
- the chain 38 maintains substantially the same high-strength and load capacity characteristics as a known inverted tooth chain incorporating the links 10 .
- the chain 38 also permits the sprocket chordal pitch S p to be reduced to substantially one-half of the chain pitch.
- the overall noise levels associated with the chain 38 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear.
- a timing, drive, etc. chain system 80 incorporates the features of the present invention therein.
- the chain system 80 rotates in a counter-clockwise direction as shown by arrow 82 , and includes a drive sprocket 84 , a driven sprocket 86 , and a short pitch tooth chain 88 .
- the short pitch tooth chain 88 engages and wraps about sprockets 84 and 86 and has two spans extending between the sprockets, slack strand 90 and taut strand 92 .
- the taut strand 92 is under tension as shown by arrows 94 .
- the short pitch tooth chain 88 includes a number of double-toed links 96 , tension links 98 , guide links 100 , spring links 102 , and pins 104 .
- the double-toed links 96 , tension links 98 , and spring links 102 are each pivotal about the pins 104 .
- the double-toed links 96 , tension links 98 , guide links 100 , and spring links 102 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics.
- FIG. 8 An exemplary lacing pattern is shown in FIG. 8.
- the tension links 98 and guide links 100 can be interchanged.
- the dimensions (e.g. length, width, height, etc.) and material considerations of the various links and pins can be varied to produce chains having different strength and load capacity characteristics in a known manner.
- the double-toed link 96 (FIG. 9) includes a body portion 106 having a first toe 108 spaced from a second toe 110 by a distance T p (toe pitch). A central aperture 112 extends through the body portion 106 .
- the toes 108 , 110 engage mutually conforming tooth spaces 114 , 116 (FIG. 7) of the sprockets 84 , 86 , respectively.
- the sprockets 84 , 86 each have a sprocket chordal pitch S p which is substantially equal to the toe pitch T p .
- the link 96 also includes a ledge or shoulder portion 118 on each side thereof.
- the tension links 98 (FIG. 10) primarily carry the load on the chain 88 .
- Each tension link 98 includes a body portion 120 having a first aperture 122 proximate one end thereof and a second aperture 124 proximate the other end.
- each tension link 98 carries two double-toed links 96 via two pins 104 each extending through a respective aperture 122 , 124 .
- the chain pitch C p for the chain 88 is defined as the distance between the centers of the apertures 122 , 124 .
- the guide links 100 (FIG. 11) primarily constrain lateral movement of the chain 88 relative to the sprockets 84 , 86 . In the embodiment being described, the guide links 100 are not pivotal relative to the pins 104 .
- Each guide link 100 includes a body portion 126 having a first aperture 128 proximate one end thereof and a second aperture 130 proximate the other end. As with the tension links 98 , the centers of the apertures 128 , 130 are separated by the distance C p .
- the guide links 100 also include an extended lower portion 132 which is constrained within a groove (not shown) on an external peripheral surface of the sprockets 84 , 86 when the link 100 enters the respective sprocket wraps.
- the guide links 100 can also carry the chain load.
- each spring link 102 provides means for preventing adjacent double-toed links 96 from contacting each other in the slack strand 90 or taut strand 92 .
- each spring link 102 includes a body portion 134 having a first aperture 136 proximate one end thereof and a second aperture 138 proximate the other end.
- the centers of the apertures 136 , 138 are separated by the distance C p .
- the spring links 102 also include a cantilevered arm portion 140 extending transversely from a central portion of the body 134 .
- a blade spring 142 or other biasing means is secured to a free end of the arm 140 .
- the blade springs 142 are interposed between adjacent double-toed links 96 such that the blade springs 142 are in tension by continuously contacting mutually opposing side walls of adjacent links 96 .
- the double-toed links 96 are freely articulatable about the respective pins 94 . Accordingly, the blade springs 142 urge the adjacent links 96 apart to prevent the links 96 from impacting, and thus generating undesirable noise.
- the chain 88 maintains substantially the same high-strength and load capacity characteristics as a known inverted tooth chain incorporating the links 10 .
- the chain 88 also permits the sprocket chordal pitch S p to be reduced to substantially one-half of the chain pitch.
- the overall noise levels associated with the chain 88 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear.
- a timing, drive, etc. chain system 150 incorporates the features of the present invention therein.
- the chain system 150 rotates in a counter-clockwise direction as shown by arrow 152 , and includes a drive sprocket 154 , a driven sprocket 156 , and a short pitch tooth chain 158 .
- the short pitch tooth chain 158 engages and wraps about sprockets 154 and 156 and has two spans extending between the sprockets, slack strand 160 and taut strand 162 .
- the taut strand 162 is under tension as shown by arrows 164 .
- the short pitch tooth chain 158 includes a number of double-toed links 166 , tension links 168 , guide links 170 , and pins 172 .
- the double-toed links 166 and tension links 168 are each pivotal about the pins 172 .
- the guide links 170 are not pivotal relative to the pins 172 .
- the double-toed links 166 , tension links 168 , and guide links 170 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics.
- An exemplary lacing pattern is shown in FIGS. 15 and 16.
- the dimensions (e.g. length, width, height, etc.) and material considerations of the various links and pins can be varied to produce chains having different strength and load capacity characteristics in a known manner.
- the double-toed link 166 (FIG. 17) includes a body portion 176 having a first toe 178 spaced from a second toe 180 by a distance T p (toe pitch) .
- a central aperture 182 extends through the body portion 176 .
- the toes 178 , 180 engage mutually conforming tooth spaces 184 , 186 (FIG. 14) of the sprockets 154 , 156 , respectively.
- the sprockets 154 , 156 each have a sprocket chordal pitch S p which is substantially equal to the toe pitch T p .
- the link 166 also includes a ledge or shoulder portion 188 on each side thereof.
- the tension links 168 (FIGS. 18 and 19) primarily carry the load on the chain 158 .
- Each tension link 168 includes a body portion 190 having a first aperture 192 proximate one end thereof and a second aperture 194 proximate the other end.
- each tension link 168 carries two double-toed links 166 via two pins 172 each extending through a respective aperture 192 , 194 and link 166 .
- the chain pitch C p for the chain 158 is defined as the distance between the centers of the apertures 192 , 194 .
- the tension link 168 further includes a raised pad 196 for supporting a wedge portion 198 .
- the wedge portion 198 forms a trapezoid in a plan view.
- the pad portion 196 extends between two adjacent guide links 170
- the wedge portion 198 extends between two adjacent double-toed links 166 .
- the thickness 196 a of the raised pad 196 is substantially equal to the thickness of the guide links 170 to permit the wedge portion 198 to extend at least partially between adjacent double-toed links 166 .
- the guide links 170 (FIGS. 20 and 21) primarily constrain lateral movement of the chain 158 relative to the sprockets 154 , 156 .
- Each guide link 170 includes a body portion 200 having a first aperture 202 proximate one end thereof and a second aperture 204 proximate the other end. As with the tension links 168 , the centers of the apertures 202 , 204 are separated by the distance C p .
- the guide links 170 also include an extended lower portion 206 which is constrained within a groove (not shown) on an external peripheral surface of the sprockets 154 , 156 when the link 170 enters the respective sprocket wraps.
- the guide links 170 can also carry a portion of the loading on the chain 158 .
- the guide link 170 further includes a raised wedge portion 208 .
- the wedge portion 208 forms a trapezoid in a plan view. As best seen in FIG. 15, the wedge portion 208 extends at least partially between two adjacent double-toed links 166 .
- the wedge portions 198 , 208 provide means for preventing adjacent double-toed links 96 from inadvertently contacting each other in the slack strand 160 or taut strand 162 .
- the raised wedge portion 208 b of guide link 170 b extends between adjacent double-toed links 166 c , 166 d .
- the mutually opposing shoulder portions 188 of the links 166 c , 166 d abut the wedge portion 208 b and thus prevent the adjacent double-toed links from articulating about the pins 172 while in the strands 160 , 162 .
- the wedge portion 198 a of the tension link 168 a extends between adjacent double-toed links 166 b , 166 c .
- the mutually opposing shoulder portions 188 of the links 166 b , 166 c abut the raised wedge portion 198 a and thus prevent the double-toed links from articulating about the pins 172 while in the strands 160 , 162 .
- the trapezoidal shape of the raised wedge portions 198 , 208 permit adjacent double-toed links 166 to pivot toward each other in the sprocket wrap.
- the side walls of the wedge portion 208 a converge in a radially inward direction (relative to the sprocket center) to permit the toes 180 a , 178 b to consecutively pivot toward each other as the links enter the sprocket wrap.
- the links 166 will exit the wrap back into the slack strand 160 .
- the links 166 will rotate about the respective pins 172 until the shoulder portions 188 abut the wedge portions 198 , 208 to prevent the links 166 from impacting, and thus generating undesirable noise.
- the frequency of impacts between the toes 178 , 180 and the tooth spaces 184 , 186 is increased, while maintaining high strength and load capacity characteristics of the conventional chain 11 . That is, the tension links 168 and guide links 170 have substantially the same chain pitch C p as the prior art links 10 .
- the overall noise levels associated with the chain 158 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear.
- the double-toed links 166 , tension links 168 , and guide links 170 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics.
- FIGS. 22 and 23 illustrate an exemplary lacing pattern having greater strength and load capacity characteristics than the lacing pattern of FIGS. 15 and 16. To implement the lacing pattern of FIGS. 22 and 23, two different tension link configurations must be utilized.
- a second tension link 220 includes a body portion 222 having a first aperture 224 proximate one end thereof and a second aperture 226 proximate the other end.
- each tension link 220 carries two double-toed links 166 via two pins 172 each extending through a respective aperture 224 , 226 .
- the chain pitch C p for the chain 158 is defined as the distance between the centers of the apertures 224 , 226 .
- the second tension link 220 further includes a raised wedge portion 228 that forms a trapezoid in a plan view.
- the wedge portion 228 extends at least partially between two adjacent double-toed links 166 to prevent the double-toed links from articulating about the pins 172 while in the spans 160 , 162 in the same manner as the first tension links 168 and guide links 170 .
- the raised wedge portion 208 of the guide links 170 cooperate with the raised wedge portions 228 of the second tension links 220 to prevent adjacent double-toed links 166 from contacting each other.
- the wedge portions 198 , 208 , 228 of the tension links 168 , 220 , and guide links 170 (and the pads 196 of the links 168 ) can be formed by molding, stamping, pressing, cutting, etc. the links in any known manner.
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- General Engineering & Computer Science (AREA)
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- Chairs For Special Purposes, Such As Reclining Chairs (AREA)
- Gears, Cams (AREA)
Abstract
Description
- This application claims the benefit of U.S. Provisional Patent Application Ser. No. 60/074,252, filed Feb. 10, 1998.
- The present invention relates to the chain arts, and in particular, a short pitch tooth chain that provides improved noise reduction over conventional tooth chains.
- Drive chain systems and timing chain systems incorporating known chains such as inverted tooth chains and roller chains have several components of undesirable noise. A major source of noise is the sound generated as the chain engaging members, such as inverted teeth or rollers, leave the span and collide with a sprocket during meshing. The resulting impact noise is repeated with a frequency generally equal to that of the frequency of the chain meshing with the sprocket. It is known that the impact noise levels associated with chains can be reduced by altering the engagement geometry of the chain and/or sprocket to, in part, reduce the impact energy that must be absorbed during the meshing process.
- The present invention contemplates a new and improved short pitch tooth chain which provides improved noise reduction over conventional inverted tooth chains.
- In accordance with one aspect of the present invention, a tooth chain is disclosed. The tooth chain includes a first link having a first aperture spaced from a second aperture by a first distance; a second link having a first toe spaced from a second toe by a second distance, the second link having a third aperture and being connected to the first link by a first pin extending through the first and third apertures; a third link having a third toe spaced from a fourth toe by the second distance, the third link having a fourth aperture and being connected to the first link by a second pin extending through the second and fourth apertures; and the first distance defining a chain pitch and the second distance defining a sprocket chordal pitch wherein the chain pitch is about twice the sprocket chordal pitch.
- In accordance with another aspect of the present invention, a chain system is disclosed. The chain system includes a first sprocket having a first plurality of sprocket teeth spaced apart by a first distance; a second sprocket having a second plurality of sprocket teeth spaced apart by the first distance; a chain wrapped around the first and second sprockets, the chain including a first link having a first aperture spaced from a second aperture by a second distance, a second link having a first toe spaced from a second toe by the first distance, the second link having a third aperture and being connected to the first link by a first pin extending through the first and third apertures, a third link having a third toe spaced from a fourth toe by the first distance, the third link having a fourth aperture and being connected to the first link by a second pin extending through the second and fourth apertures; and the first distance defining a sprocket chordal pitch and the second distance defining a chain pitch wherein the chain pitch is about twice the sprocket chordal pitch.
- In accordance with a further aspect of the present invention, a chain is disclosed. The chain includes a first link member having a first aperture spaced from a second aperture by a first distance; a second link member connected to the first link member and having a first toe spaced from a second toe by a second distance, the toes being adapted for engagement with tooth spaces associated with a sprocket, the tooth spaces being spaced apart by a third distance; and the second distance being substantially equal to the third distance, and the second distance being about one half of the first distance.
- In accordance with yet another aspect of the present invention, a chain system is disclosed. The chain system includes a first sprocket having a first plurality of tooth spaces spaced apart by a first distance; a second sprocket having a second plurality of tooth spaces spaced apart by the first distance; and a chain including a first link member having a first aperture spaced from a second aperture by a second distance, a second link member connected to the first link member and having a first toe spaced from a second toe by a third distance, the toes being adapted for engagement with the first and second plurality of tooth spaces, and the first distance being substantially equal to the third distance, and the third distance being about one half of the second distance.
- In accordance with a still further aspect of the present invention, a link member for a chain is disclosed. The link member includes a body portion defining a first toe and a second toe spaced from the first toe by a predetermined distance, the toes adapted for meshing engagement with tooth spaces associated with a sprocket, and the link member further comprising a single aperture extending through the body portion.
- One advantage of the present invention is the provision of a short pitch tooth chain which reduces noise levels by increasing the frequency at which the chain meshes with a sprocket to a level which is inaudible, or at least less audible to the human ear.
- Another advantage of the present invention is the provision of a short pitch tooth chain having a chain pitch value which is approximately twice a sprocket chordal pitch value.
- A further advantage of the present invention is the provision of a chain system having a short pitch tooth chain that reduces noise levels by increasing the frequency at which the chain meshes with a sprocket to a level which is inaudible, or at least less audible to the human ear.
- Yet another advantage of the present invention is the provision of chain system having a short pitch tooth chain with a chain pitch value which is approximately twice a sprocket chordal pitch value.
- Still further objects and advantages of the present invention will become apparent to those of ordinary skill in the art upon reading and understanding the following detailed description of the preferred embodiments.
- The invention may take form in various components and arrangements of components, and in various steps and arrangements of steps. The drawings are only for purposes of illustrating a preferred embodiment(s) and are not to be construed as limiting the invention.
- FIG. 1 illustrates a conventional double-toed link for a known inverted tooth chain;
- FIG. 2 is a fragmentary view of a conventional inverted tooth chain that incorporates double-toed links of FIG. 1, as the chain engages a conventional sprocket;
- FIG. 3 illustrates a first embodiment of a chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 4 is a top fragmentary view of an exemplary lacing pattern for the short pitch tooth chain of FIG. 3;
- FIG. 5 illustrates a double-toed link of the short pitch tooth chain of FIG. 3;
- FIG. 6 illustrates a tension link of the short pitch tooth chain of FIG. 3;
- FIG. 7 illustrates a second embodiment of chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 8 is a top fragmentary view of an exemplary lacing pattern for the short pitch tooth chain of FIG. 7;
- FIG. 9 illustrates a double-toed link of the short pitch tooth chain of FIG. 7;
- FIG. 10 illustrates a tension link of the short pitch tooth chain of FIG. 7;
- FIG. 11 illustrates a guide link of the short pitch tooth chain of FIG. 7;
- FIG. 12 illustrates a spring link of the short pitch tooth chain of FIG. 7;
- FIG. 12a is a side view of the spring link taken along the
line 12 a-12 a of FIG. 12; - FIG. 13 is an enlarged view of the drive sprocket of FIG. 7 with two double-toed links seated in a tooth space and a third double-toed link being collected from a taut span of the short pitch tooth chain;
- FIG. 14 illustrates a third embodiment of a chain system including a short pitch tooth chain, a drive sprocket, and a driven sprocket, that incorporates the features of the present invention therein;
- FIG. 15 is a top fragmentary view of a first exemplary lacing pattern for the short pitch tooth chain of FIG. 14;
- FIG. 16 is a side view of the lacing pattern taken along the line16-16 of FIG. 15;
- FIG. 17 illustrates a double-toed link of the short pitch tooth chain of FIG. 14;
- FIG. 18 illustrates a first tension link of the short pitch tooth chain of FIG. 14;
- FIG. 19 illustrates a side view of the tension link taken along the line19-19 of FIG. 18;
- FIG. 20 illustrates a guide link of the short pitch tooth chain of FIG. 14;
- FIG. 21 illustrates a side view of the guide link taken along the line21-21 of FIG. 20;
- FIG. 22 is an enlarged view of the drive sprocket of FIG. 14 with two double-toed links seated in a tooth space and a third double-toed link being collected from a taut span of the short pitch tooth chain;
- FIG. 23 is a top fragmentary view of a second exemplary lacing pattern for the short pitch tooth chain of FIG. 14;
- FIG. 24 is a side view of the lacing pattern taken along the line24-24 of FIG. 23;
- FIG. 25 illustrates a second tension link of the short pitch tooth chain of FIG. 14; and
- FIG. 26 illustrates a side view of the second tension link taken along the line26-26 of FIG. 25.
- With reference to FIGS. 1 and 2, a conventional double-
toed link 10 for a known inverted tooth chain 11 includes abody portion 12 having afirst toe 14 spaced from asecond toe 16. Thetoes sprocket 17 a. Thelink 10 also includes afirst aperture 18 and asecond aperture 20 spaced apart from the first aperture. Theapertures conventional pins 21 for joining together a number of different links, includinglinks 10, to form the known inverted tooth chain 11. - The
link 10 has a chain or link pitch Cp conventionally defined as the distance between the centers of the first andsecond apertures link 10 has a sprocket chordal pitch Sp (conventionally defined as the distance separating adjacent teeth or tooth spaces) substantially equal to the chain pitch Cp. Thus, for conventional chains, Sp=Cp, or Sp≅Cp. - As previously mentioned, a major source of chain drive noise is the sound generated as the chain engaging members, i.e. the
toes - Since frequency is inversely proportional to time, reducing the time period between impacts results in a corresponding increase in the frequency of the impact noise generated at a given rotational velocity of the drive chain. Thus, if the time period between impacts is reduced far enough, the frequency of the impact noise is correspondingly increased to the point that the frequency-dependent impact noise is less audible or not audible to the human ear.
- The time period between impacts can be reduced by reducing the chain pitch Cp, and necessarily, the sprocket pitch Sp, for a given chain velocity (v). That is, with chain velocity (v) remaining constant, reducing the time period (t) between impacts requires a corresponding reduction in the chain pitch Cp, where v=Cp/t. However, reducing the chain pitch Cp of the
conventional link 10 to about 8.0 mm or less is problematic. - That is, as chain pitch Cp is reduced, the size of the
link 10 decreases, and a corresponding decrease in strength and load capacity of the chain results. More particularly, as the size of thelink 10 decreases, there is less link material between theapertures aperture link 10 thereby resulting in a structurally weaker link. - Referring now to FIG. 3, there is shown a
chain system 30, such as a drive chain system, timing chain system, etc. which incorporates the features of the present invention therein. Thechain system 30 rotates in a counter-clockwise direction as shown byarrow 32. Thechain system 30 includes at least adrive sprocket 34, a drivensprocket 36, and a shortpitch tooth chain 38. The shortpitch tooth chain 38 engages and wraps aboutsprockets slack strand 40 andtaut strand 42. Thetaut strand 42 is under tension as shown by arrows 44. - With continuing reference to FIG. 3, and particular reference to FIGS. 4-6, the short
pitch tooth chain 38 includes a number of double-toedlinks 46, tension links 48, and pins 50 interconnecting thelinks links pins 50 so that as the links enter the sprocket wrap, each link may articulate independently about the respective pin to conform with the curvature of the sprocket. - It should be appreciated that the
links links pins 50 can be varied to produce chains having different strength and load capacity characteristics in a known manner. - The double-toed link46 (FIG. 5) includes a
body portion 52 having afirst toe 54 spaced from asecond toe 56 by a distance Tp (toe pitch). A central aperture 58 extends through thebody portion 52. Thetoes sprockets sprockets link 46 with a single aperture therethrough, more link material extends between the aperture and each side edge thereof, relative to thelink 10. - The tension link48 (FIG. 6) primarily carries the load on the
chain 38. Each tension link 48 includes an arcuate-shapedbody portion 62 having afirst aperture 64 proximate one end thereof, and asecond aperture 66 proximate the other end. As best seen in FIG. 4, each tension link 48 carries two double-toedlinks 46 via twopins 50 each extending through arespective aperture chain 38 is defined as the distance between the centers of theapertures chain 38, Cp=2Sp=2Tp, or Cp≅2Sp≅2Tp. It has been determined that, in automotive applications, the frequency-dependent impact noise is reduced when the chain pitch Cp of thechain 38 is about 8.0 mm (0.315 inches) or less. - Thus, by reducing the toe pitch Tp and the sprocket pitch Sp to a value approximately one-half of the chain pitch Cp, the frequency of impacts between the
toes tooth spaces 58, 60 is increased, while maintaining high strength and high load capacity characteristics of thechain 38. That is, the tension links 48 have substantially the same chain pitch Cp as the prior art links 10. - Accordingly, the
chain 38 maintains substantially the same high-strength and load capacity characteristics as a known inverted tooth chain incorporating thelinks 10. However, thechain 38 also permits the sprocket chordal pitch Sp to be reduced to substantially one-half of the chain pitch. As a result, for a given operating velocity of the chain, the overall noise levels associated with thechain 38 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear. - However, since the
links 46 are freely pivotal about thepins 50, depending upon the particular dynamics of thechain 38,adjacent links 46 may inadvertently rotate into contact with each other when in thespans - Referring now to FIG. 7, a timing, drive, etc.
chain system 80 incorporates the features of the present invention therein. Thechain system 80 rotates in a counter-clockwise direction as shown byarrow 82, and includes adrive sprocket 84, a drivensprocket 86, and a shortpitch tooth chain 88. The shortpitch tooth chain 88 engages and wraps aboutsprockets slack strand 90 andtaut strand 92. Thetaut strand 92 is under tension as shown by arrows 94. - With continuing reference to FIG. 7, and particular reference to FIGS. 8-13, the short
pitch tooth chain 88 includes a number of double-toedlinks 96, tension links 98, guide links 100, spring links 102, and pins 104. The double-toedlinks 96, tension links 98, andspring links 102 are each pivotal about thepins 104. The double-toedlinks 96, tension links 98, guide links 100, andspring links 102 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics. - An exemplary lacing pattern is shown in FIG. 8. For instance, it is known that the tension links98 and guide
links 100 can be interchanged. Further, the dimensions (e.g. length, width, height, etc.) and material considerations of the various links and pins can be varied to produce chains having different strength and load capacity characteristics in a known manner. - The double-toed link96 (FIG. 9) includes a body portion 106 having a
first toe 108 spaced from asecond toe 110 by a distance Tp (toe pitch). Acentral aperture 112 extends through the body portion 106. Thetoes tooth spaces 114, 116 (FIG. 7) of thesprockets sprockets link 96 also includes a ledge orshoulder portion 118 on each side thereof. - The tension links98 (FIG. 10) primarily carry the load on the
chain 88. Each tension link 98 includes abody portion 120 having afirst aperture 122 proximate one end thereof and asecond aperture 124 proximate the other end. As best seen in FIG. 8, each tension link 98 carries two double-toedlinks 96 via twopins 104 each extending through arespective aperture chain 88 is defined as the distance between the centers of theapertures chain 88, Cp=2Sp=2Tp, or Cp≅2Sp≅2Tp. - The guide links100 (FIG. 11) primarily constrain lateral movement of the
chain 88 relative to thesprockets pins 104. Each guide link 100 includes a body portion 126 having afirst aperture 128 proximate one end thereof and asecond aperture 130 proximate the other end. As with the tension links 98, the centers of theapertures lower portion 132 which is constrained within a groove (not shown) on an external peripheral surface of thesprockets link 100 enters the respective sprocket wraps. The guide links 100 can also carry the chain load. - The spring links102 (FIGS. 12 and 12a) provide means for preventing adjacent double-toed
links 96 from contacting each other in theslack strand 90 ortaut strand 92. In particular, eachspring link 102 includes abody portion 134 having a first aperture 136 proximate one end thereof and asecond aperture 138 proximate the other end. As with theother links apertures 136, 138 are separated by the distance Cp. The spring links 102 also include acantilevered arm portion 140 extending transversely from a central portion of thebody 134. Ablade spring 142 or other biasing means is secured to a free end of thearm 140. - As shown in FIG. 13, the blade springs142 are interposed between adjacent double-toed
links 96 such that the blade springs 142 are in tension by continuously contacting mutually opposing side walls ofadjacent links 96. As previously mentioned, the double-toedlinks 96 are freely articulatable about the respective pins 94. Accordingly, the blade springs 142 urge theadjacent links 96 apart to prevent thelinks 96 from impacting, and thus generating undesirable noise. - In particular, as shown in FIG. 13, as the links96 a, 96 b enter the wrap of the
sprocket 84, the toe 108 a of link 96 a and thetoe 110 b of link 96 b consecutively pivot around theirrespective pins 94 a, 94 b toward each other. As a result, the blade spring 142 a is increasingly compressed in tension relative to the blade spring 142 b interposed betweenlinks 96 b, 96 c. As thesprocket 84 rotates in the direction ofarrow 82, thelinks 96 b, 96 c will fully engage thesprocket 84 in the wrap resulting in a full compression of the blade spring 142 b. - It should be appreciated that as the
sprocket 84 continues further in the direction ofarrow 82, thelinks 96 exit the wrap into the slack strand 90 (FIG. 7). As a result, thelinks 96 are again free to rotate about the respective pins 94. Thus, the blade springs 142 betweenadjacent links 96 progressively flex outwardly under a spring force to urgeadjacent links 96 apart and prevent thelinks 96 from undesirably contacting while in thestrands - Thus, by reducing the toe pitch Tp and the sprocket pitch Sp to a value approximately one-half of the chain pitch Cp, the frequency of impacts between the
toes tooth spaces 114, 116 is increased, while maintaining high strength and load capacity characteristics of the conventional chain 11. That is, the tension links 98 and guidelinks 100 have substantially the same chain pitch Cp as the prior art links 10. - Accordingly, the
chain 88 maintains substantially the same high-strength and load capacity characteristics as a known inverted tooth chain incorporating thelinks 10. However, thechain 88 also permits the sprocket chordal pitch Sp to be reduced to substantially one-half of the chain pitch. As a result, for a given operating velocity of the chain, the overall noise levels associated with thechain 88 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear. - Referring now to FIG. 14, a timing, drive, etc.
chain system 150 incorporates the features of the present invention therein. Thechain system 150 rotates in a counter-clockwise direction as shown byarrow 152, and includes adrive sprocket 154, a drivensprocket 156, and a shortpitch tooth chain 158. The shortpitch tooth chain 158 engages and wraps aboutsprockets slack strand 160 andtaut strand 162. Thetaut strand 162 is under tension as shown byarrows 164. - With continuing reference to FIG. 14, and particular reference to FIGS. 15-22, the short
pitch tooth chain 158 includes a number of double-toedlinks 166, tension links 168, guidelinks 170, and pins 172. The double-toedlinks 166 andtension links 168 are each pivotal about thepins 172. In the embodiment being described, the guide links 170 are not pivotal relative to thepins 172. - The double-toed
links 166, tension links 168, and guidelinks 170 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics. An exemplary lacing pattern is shown in FIGS. 15 and 16. The dimensions (e.g. length, width, height, etc.) and material considerations of the various links and pins can be varied to produce chains having different strength and load capacity characteristics in a known manner. - The double-toed link166 (FIG. 17) includes a
body portion 176 having afirst toe 178 spaced from asecond toe 180 by a distance Tp (toe pitch) . Acentral aperture 182 extends through thebody portion 176. Thetoes sprockets sprockets link 166 also includes a ledge orshoulder portion 188 on each side thereof. - The tension links168 (FIGS. 18 and 19) primarily carry the load on the
chain 158. Each tension link 168 includes abody portion 190 having afirst aperture 192 proximate one end thereof and asecond aperture 194 proximate the other end. As best seen in FIG. 15, each tension link 168 carries two double-toedlinks 166 via twopins 172 each extending through arespective aperture chain 158 is defined as the distance between the centers of theapertures chain 158, Cp=2Sp=2Tp, or Cp≅2Sp≅2Tp. - The tension link168 further includes a raised
pad 196 for supporting awedge portion 198. In the embodiment being described, thewedge portion 198 forms a trapezoid in a plan view. As best seen in FIG. 15, thepad portion 196 extends between twoadjacent guide links 170, and thewedge portion 198 extends between two adjacent double-toedlinks 166. The thickness 196 a of the raisedpad 196 is substantially equal to the thickness of the guide links 170 to permit thewedge portion 198 to extend at least partially between adjacent double-toedlinks 166. - The guide links170 (FIGS. 20 and 21) primarily constrain lateral movement of the
chain 158 relative to thesprockets body portion 200 having afirst aperture 202 proximate one end thereof and asecond aperture 204 proximate the other end. As with the tension links 168, the centers of theapertures lower portion 206 which is constrained within a groove (not shown) on an external peripheral surface of thesprockets link 170 enters the respective sprocket wraps. The guide links 170 can also carry a portion of the loading on thechain 158. - The guide link170 further includes a raised
wedge portion 208. In the embodiment being described, thewedge portion 208 forms a trapezoid in a plan view. As best seen in FIG. 15, thewedge portion 208 extends at least partially between two adjacent double-toedlinks 166. - The
wedge portions links 96 from inadvertently contacting each other in theslack strand 160 ortaut strand 162. In particular, as best seen in FIG. 22, the raised wedge portion 208 b of guide link 170 b extends between adjacent double-toedlinks 166 c, 166 d. The mutuallyopposing shoulder portions 188 of thelinks 166 c, 166 d abut the wedge portion 208 b and thus prevent the adjacent double-toed links from articulating about thepins 172 while in thestrands links 166 b, 166 c. The mutuallyopposing shoulder portions 188 of thelinks 166 b, 166 c abut the raised wedge portion 198 a and thus prevent the double-toed links from articulating about thepins 172 while in thestrands - The trapezoidal shape of the raised
wedge portions links 166 to pivot toward each other in the sprocket wrap. With reference again to FIG. 22, the side walls of thewedge portion 208 a converge in a radially inward direction (relative to the sprocket center) to permit thetoes 180 a, 178 b to consecutively pivot toward each other as the links enter the sprocket wrap. As thesprocket 154 continues to rotate in the direction ofarrow 152, thelinks 166 will exit the wrap back into theslack strand 160. As a result, thelinks 166 will rotate about therespective pins 172 until theshoulder portions 188 abut thewedge portions links 166 from impacting, and thus generating undesirable noise. - Thus, by reducing the toe pitch Tp and the sprocket pitch Sp to a value of approximately one-half the chain pitch Cp, the frequency of impacts between the
toes links 170 have substantially the same chain pitch Cp as the prior art links 10. As a result, for a given operating velocity of the chain, the overall noise levels associated with thechain 158 are reduced by increasing the frequency at which the chain meshes with the sprockets to a level which is inaudible, or at least less audible to the human ear. - As mentioned, the double-toed
links 166, tension links 168, and guidelinks 170 may be interconnected in various lacing patterns to produce chains having different strength and load capacity characteristics. FIGS. 22 and 23 illustrate an exemplary lacing pattern having greater strength and load capacity characteristics than the lacing pattern of FIGS. 15 and 16. To implement the lacing pattern of FIGS. 22 and 23, two different tension link configurations must be utilized. - Referring now to FIGS. 25 and 26, a
second tension link 220 includes abody portion 222 having afirst aperture 224 proximate one end thereof and asecond aperture 226 proximate the other end. As best seen in FIG. 23, each tension link 220 carries two double-toedlinks 166 via twopins 172 each extending through arespective aperture chain 158 is defined as the distance between the centers of theapertures chain 158, Cp=2Sp=2Tp, or Cp≅2Sp≅2Tp. - The
second tension link 220 further includes a raisedwedge portion 228 that forms a trapezoid in a plan view. As best seen in FIG. 24, thewedge portion 228 extends at least partially between two adjacent double-toedlinks 166 to prevent the double-toed links from articulating about thepins 172 while in thespans wedge portion 208 of the guide links 170 cooperate with the raisedwedge portions 228 of the second tension links 220 to prevent adjacent double-toedlinks 166 from contacting each other. - The
wedge portions pads 196 of the links 168) can be formed by molding, stamping, pressing, cutting, etc. the links in any known manner. - The invention has been described with reference to the preferred embodiments. Obviously, modifications and alterations will occur to others upon reading and understanding the preceding detailed description. It is intended that the invention be construed as including all such modifications and alterations insofar as they come within the scope of the appended claims or the equivalents thereof.
Claims (22)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US09/742,655 US6287229B2 (en) | 1998-02-10 | 2000-12-21 | Short pitch tooth chain |
US09/949,180 US6623392B2 (en) | 1998-02-10 | 2001-09-07 | Short pitch tooth chain |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US7425298P | 1998-02-10 | 1998-02-10 | |
US09/247,211 US6186920B1 (en) | 1998-02-10 | 1999-02-09 | Short pitch tooth chain |
US09/742,655 US6287229B2 (en) | 1998-02-10 | 2000-12-21 | Short pitch tooth chain |
Related Parent Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/247,211 Division US6186920B1 (en) | 1998-02-10 | 1999-02-09 | Short pitch tooth chain |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/949,180 Continuation US6623392B2 (en) | 1998-02-10 | 2001-09-07 | Short pitch tooth chain |
Publications (2)
Publication Number | Publication Date |
---|---|
US20010000781A1 true US20010000781A1 (en) | 2001-05-03 |
US6287229B2 US6287229B2 (en) | 2001-09-11 |
Family
ID=22118579
Family Applications (3)
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US09/247,211 Expired - Lifetime US6186920B1 (en) | 1998-02-10 | 1999-02-09 | Short pitch tooth chain |
US09/742,655 Expired - Lifetime US6287229B2 (en) | 1998-02-10 | 2000-12-21 | Short pitch tooth chain |
US09/949,180 Expired - Fee Related US6623392B2 (en) | 1998-02-10 | 2001-09-07 | Short pitch tooth chain |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/247,211 Expired - Lifetime US6186920B1 (en) | 1998-02-10 | 1999-02-09 | Short pitch tooth chain |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
US09/949,180 Expired - Fee Related US6623392B2 (en) | 1998-02-10 | 2001-09-07 | Short pitch tooth chain |
Country Status (6)
Country | Link |
---|---|
US (3) | US6186920B1 (en) |
EP (1) | EP1053412B1 (en) |
JP (1) | JP2002502944A (en) |
BR (1) | BR9907799A (en) |
CA (1) | CA2312567C (en) |
WO (1) | WO1999040342A1 (en) |
Cited By (2)
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US8454465B2 (en) | 2006-02-15 | 2013-06-04 | Iwis Motorsysteme Gmbh & Co. Kg | Toothed chain with optimized chain joint and enlarged external flank angle |
CN109987164A (en) * | 2017-12-30 | 2019-07-09 | 卡特彼勒公司 | To the chassis supports of caterpillar chain |
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US6186920B1 (en) * | 1998-02-10 | 2001-02-13 | Cloyes Gear And Products, Inc. | Short pitch tooth chain |
US20020049107A1 (en) * | 2000-07-20 | 2002-04-25 | Ledvina Timothy J. | Small pitch silent chain with freely rotating pins having wear resistant coating |
JP2002130385A (en) * | 2000-10-26 | 2002-05-09 | Tsubakimoto Chain Co | Wear and elongation resistant silent chain |
US6443795B1 (en) * | 2001-09-11 | 2002-09-03 | Wen-Pin Lin | Transmission chain for toys |
DE102004007100B4 (en) * | 2003-02-20 | 2017-02-16 | Schaeffler Technologies AG & Co. KG | Tabs for a plurality of different link chains for conical-pulley transmission and link chain |
WO2006036603A1 (en) * | 2004-09-24 | 2006-04-06 | Cloyes Gear And Products, Inc. | Inverted tooth chain system with inside flank engagement |
US7686722B2 (en) * | 2005-10-01 | 2010-03-30 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Plate-link chain for a continuously variable transmission |
US20070205085A1 (en) * | 2006-03-02 | 2007-09-06 | Esco Corporation | Chain For Conveying Logs Or The Like |
US8529389B2 (en) * | 2008-09-09 | 2013-09-10 | Cloyes Gear And Products, Inc. | Inverted tooth chain and sprocket drive system with reduced meshing impact |
US9377082B2 (en) | 2008-09-09 | 2016-06-28 | Cloyes Gear And Products, Inc. | Inverted tooth chain and sprocket drive system with reduced meshing impact |
WO2010030669A1 (en) | 2008-09-09 | 2010-03-18 | Cloyes Gear And Products, Inc. | Inverted tooth chain sprocket drive system with reduced meshing impact |
US8672786B2 (en) * | 2008-09-09 | 2014-03-18 | Cloyes Gear And Products, Inc. | Inverted tooth chain and sprocket drive system with reduced meshing impact |
DE102009009526A1 (en) * | 2009-02-18 | 2010-08-19 | Schaeffler Technologies Gmbh & Co. Kg | toothed chain |
DE102009009369A1 (en) * | 2009-02-18 | 2010-08-19 | Schaeffler Technologies Gmbh & Co. Kg | toothed chain |
JP5522965B2 (en) * | 2009-04-03 | 2014-06-18 | ボーグワーナー インコーポレーテッド | chain |
JP5334710B2 (en) * | 2009-06-30 | 2013-11-06 | ボーグワーナー インコーポレーテッド | chain |
DE102011111943A1 (en) * | 2011-08-30 | 2013-02-28 | Robert Bosch Gmbh | Sprocket chain for transporting heated transport goods such as hollow glass articles, has contact elements that are axially and radially connected with isolation tab through connecting links |
JP5766140B2 (en) * | 2012-03-13 | 2015-08-19 | 株式会社椿本チエイン | Chain transmission |
CN105452714B (en) * | 2013-08-14 | 2018-06-08 | 博格华纳公司 | Inner link position replaces the chain to improve narrow-band noise-vibro-acoustic vibration roughness (NVH) performance |
WO2017045156A1 (en) * | 2015-09-16 | 2017-03-23 | GM Global Technology Operations LLC | Chain composed of different pitch links with repeated sequence |
KR101937780B1 (en) * | 2016-12-29 | 2019-01-15 | 유신정밀공업 주식회사 | Silent chain |
USD998059S1 (en) * | 2021-07-14 | 2023-09-05 | Jinfeng Cai | Marble run toy |
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-
1999
- 1999-02-09 US US09/247,211 patent/US6186920B1/en not_active Expired - Lifetime
- 1999-02-10 WO PCT/US1999/002827 patent/WO1999040342A1/en active Application Filing
- 1999-02-10 CA CA002312567A patent/CA2312567C/en not_active Expired - Fee Related
- 1999-02-10 EP EP99905913.2A patent/EP1053412B1/en not_active Expired - Lifetime
- 1999-02-10 JP JP2000530720A patent/JP2002502944A/en active Pending
- 1999-02-10 BR BR9907799-0A patent/BR9907799A/en not_active IP Right Cessation
-
2000
- 2000-12-21 US US09/742,655 patent/US6287229B2/en not_active Expired - Lifetime
-
2001
- 2001-09-07 US US09/949,180 patent/US6623392B2/en not_active Expired - Fee Related
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US8454465B2 (en) | 2006-02-15 | 2013-06-04 | Iwis Motorsysteme Gmbh & Co. Kg | Toothed chain with optimized chain joint and enlarged external flank angle |
CN109987164A (en) * | 2017-12-30 | 2019-07-09 | 卡特彼勒公司 | To the chassis supports of caterpillar chain |
Also Published As
Publication number | Publication date |
---|---|
BR9907799A (en) | 2001-09-04 |
US6287229B2 (en) | 2001-09-11 |
US20020006843A1 (en) | 2002-01-17 |
EP1053412A4 (en) | 2005-07-13 |
CA2312567C (en) | 2007-09-18 |
US6186920B1 (en) | 2001-02-13 |
WO1999040342A1 (en) | 1999-08-12 |
EP1053412B1 (en) | 2013-10-30 |
EP1053412A1 (en) | 2000-11-22 |
CA2312567A1 (en) | 1999-08-12 |
US6623392B2 (en) | 2003-09-23 |
JP2002502944A (en) | 2002-01-29 |
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