LOBMEYER LUCAS (DE)
FOWLER MARCEL (GB)
EP0611000A1 | 1994-08-17 | |||
EP1033509A2 | 2000-09-06 | |||
EP1120586A2 | 2001-08-01 |
CLAIMS 1. A drive sprocket comprising a plurality of teeth for meshing with a drive member to transmit rotary motion, the drive member including a plurality of engagement pockets engaging the teeth of the drive sprocket, wherein each tooth has a tooth profile defined by a first side comprising a first engagement surface and an opposite second side comprising a second engagement surface, which engagement surfaces are configured such that when driven, a tooth meshes to the engagement pocket at a first contact location on the first engagement surface and also at a second contact location on the second engagement surface, wherein the first contact location is radially offset from the second contact location. 2. A drive sprocket as claimed in claim 1, wherein each tooth has a front face and a back face, the shape of which faces being defined by the first and second sides, wherein the shape of each face is symmetrical about a radial axis of the tooth, and the sides of the faces are defined at least partially by two arcs. 3. A drive sprocket according to claim 2, wherein the two arcs each have a radius of R, the centres of the arcs being at a distance x from one another, and at a perpendicular distance, y, from the centre of the drive sprocket, and wherein the centre of each arc is at +x/2,y. 4. A drive sprocket according to any one of the preceding claims, wherein adjacent teeth are spaced apart from one another to define a connecting portion of the sprocket. 5. A transmission system comprising a drive sprocket according to any one of the preceding claims, further comprising a drive member, which drive member is adapted to mesh with the drive sprocket. 6. A transmission system as claimed in claim 5, wherein the drive member comprises a plurality of engagement pockets, each of which engagement pockets comprising a first engaging surface and a second engaging surface spaced apart from the first engaging surface, the first and second engaging surfaces forming an engagement surface pair, which pair is rotatable about a rotational axis, wherein adjacent engagement pockets are connected to one another by a connecting member. 7. A transmission system as claimed in claim 6, wherein adjacent engagement pockets are connected to one another by a primary link, which primary link is rotatable about the rotational axis of the engagement surface pair. 8. A transmission system as claimed claim 7, wherein each primary link is rotatable about the rotational axis of each adjacent engagement pocket. 9. A transmission system according claim 7 or claim 8, comprising a plurality of first primary links which are coplanar with one another and are pivotally connected to one another at first and second pivot points, which pivot points are spaced apart from one another such that adjacent first primary links are pivotable about the axis of rotation of each adjacent engagement pocket. 10. A transmission system as claimed in claim 9, comprising a plurality of second primary links coplanar with one another and pivotally connected to one another at first and second pivot points, which pivot points are spaced apart from one another such that adjacent second primary links are pivotable about the axis of rotation of each adjacent engagement pocket, wherein the first primary links are connected to the second primary links such the first and second primary links are substantially parallel to one another, and the first pivot points of the first links are coaxial with the second pivot points of the second links, and the second pivot points of the first links are coaxial with the first pivot points of the second links. 11. A transmission system as claimed in any one of claims 7 to 10, wherein each engagement pocket comprises first and second transverse members, each having a first end and a second end, the first and second transverse members being spaced apart from one another, wherein the first and second engaging surfaces are formed on the first and second transverse members respectively. 12. A transmission system as claimed in claim 11, wherein each engagement pocket comprises a secondary link connecting the first and second transverse members, wherein the secondary links are coplanar with one another. 13. A transmission system as claimed in claim 12, wherein the secondary links are parallel with the primary links, and the transverse members are substantially perpendicular to the primary and secondary links. 14. A transmission system as claimed in claim 12 or claim 13, wherein each engagement pocket comprises a first secondary link positioned at, or close to the first ends of the first and second transverse members, and a second secondary link positioned at, or close to the second ends of the transverse members, where in the first and second secondary links are parallel with one another. 15. A transmission system as claimed in claim 14, wherein each engagement pocket comprises a first set of first and second primary links which are proximate the first secondary links, and a second set of primary and secondary links with are proximate the second secondary links. 16. A transmission system as claimed in claim 15, wherein the first and second transverse members each have a radius r, wherein the distance between the first and second members of an engagement pocket is p2, and the distance between first and second pivot points of a primary link is p. 17. A drive member forming part of a transmission system as claimed in any one of claims 5 to 16. 18. A power transmission drive member adapted to mesh with a drive sprocket to transmit rotary motion, the drive member comprising a plurality of engaging mechanisms, each comprising an engaging body comprising an engagement pocket adapted to engage with the drive sprocket, each of which engagement pockets comprising a first engaging surface and a second engaging surface spaced apart from the first engaging surface, the first and second engaging surfaces forming an engaging surface pair, which pair is rotatable about an engaging mechanism rotational axis, wherein the power transmission drive member comprises a carrier, which carrier is articulated and is adapted to support the plurality of engaging mechanisms. 19. A power transmission drive member as claimed in claim 18 wherein the first and second engaging surfaces are positioned symmetrically relative to the rotational axis of a respective engaging body. 20. A power transmission drive member as claimed in claim 18 or claim 19 wherein the engaging surfaces are configured such that when driven, a tooth of the sprocket meshes to the engagement pocket at a first contact location on the first engaging surface, and also at a second contact location on the second engaging surface. 21. A power transmission drive member as claimed in claim 20 wherein the first contact location is radially offset from the second contact location during use. 22. A power transmission drive member as claimed in one of claims 18 to 21 wherein the first and second engaging surfaces of each engaging body are formed on first and second pins respectively. 23. A power transmission drive member as claimed in any one of claims 18 to 22 wherein each engaging mechanism comprises two engaging bodies, which engaging bodies are spaced apart from one another. 24. A power transmission drive member as claimed in any one of claims 18 to 23 wherein each engaging mechanism comprises a connecting member having a first end and an opposite second end, and attachable to one engaging body at the first end, to the other engaging body at the second end, and extending colinearly with the rotational axis of the respective engaging mechanism wherein each engaging body of a respective engaging mechanism comprises a front face and an opposite back face, wherein the engaging surfaces of each engaging body extend from the front face of a respective engaging body, and the connecting member extends from the back face of one engaging body to the back face of the other engaging body , which connecting member is adapted to enable connection of a respective engaging mechanism to the carrier. 25. A power transmission drive member as claimed in Claim 24 wherein the connecting member is attached to each engaging body by means of a press fit with the engaging body. 26. A power transmission drive member as claimed in any one of claims 18 to 25 wherein each engaging body comprises a receiving portion adapted to receive the connecting member, which receiving portion comprises an aperture, the centre of which is coaxial with the rotational axis of a respective engaging mechanism 27. A power transmission drive member as claimed in any one of claims 24 to 26 wherein the carrier comprises hollow pins extending transversely at least partially across the carrier at spaced apart intervals along the length of the carrier, wherein each connecting member extends through a hollow pin to thereby connect the engaging mechanisms to the carrier. 28. A power transmission drive member as claimed in claim 18 wherein the carrier comprises a chain formed from links, wherein each link comprises a body portion and first and second legs extending from the body portion to define a space between the legs and the body portion, wherein each leg comprises a hollow pin receiving portion, wherein the hollow pin receiving portion of a first leg of a link is coaxial with the rotational axis of a first engaging mechanism, and the hollow pin receiving portion of the second leg of the link is coaxial with the rotational axis of a second, adjacent, engaging mechanism, and wherein each connecting member is adapted to extend through a respective hollow pin and engaging body, to thereby link the engaging bodies to the links, such that each engaging body is rotatable about its rotational axis, the space of each link providing space for such rotation. 29. A power transmission drive member as claimed in any one of claims 18 to 28 comprising a chain having inner links and outer links, wherein the inner links of the chain each comprise a composite inner link formed from a plurality of link plates. 30. A power transmission drive member as claimed in any one of claims 18 to 29 wherein each engaging mechanism comprises first and second extension members, which extension members are spaced apart from, and coaxial with one another, and each has first and second end portions, wherein the extension member extends across the width of the engaging mechanism and through each engaging body such that the first and second end portions of each extension member extend from the first face of each engaging body, away from the carrier to form a pin, wherein the first engaging surfaces of each engaging body are formed on the first and second end portions respectively of the first extension member, and the second engaging surfaces of each engaging body are formed on the first and second end portions respectively of the second extension member. 31. A power transmission drive member as claimed in any one of claims 18 to 30 wherein the carrier comprises angle rotation limiters providing stops formed on the carrier. 32. An engaging mechanism forming part of a power transmission drive member as claimed in any one of claims 18 to 31. 33. A power transmission system comprising a power transmission drive member as claimed in any one of claims 18 to 31, further comprising a drive sprocket, the power transmission drive member being adapted to engage with the drive sprocket. 34. A drive sprocket comprising a plurality of teeth for meshing with a drive member to transmit rotary motion, the drive member including a plurality of engagement pockets engaging the teeth of the drive sprocket, wherein each tooth has a tooth profile defined by a first side comprising a first engagement surface and an opposite second side comprising a second engagement surface, which engagement surfaces are configured such that when driven, a tooth meshes to the engagement pocket at a first contact location on the first engagement surface and also at a second contact location on the second engagement surface, the first contact location being radially offset from the second contact location, and wherein each tooth has a front face and a back face, the shape of which faces being defined by the first and second sides such that the shape of each face is symmetrical about a radial axis of the tooth, and the first side of each face is defined at least partially by a first face arc, and the second side of each face is defined at least partially by a second face arc, wherein the distance between the centre of the first face arc and the centre of the second face arc of each tooth is substantially the same as the distance between the centre of the first face arc of a first tooth and the centre of the second face arc of an adjacent tooth. 35. A drive sprocket as claimed in claim 34 wherein the first face arc of each tooth comprises a base portion of the first side of the said tooth, and the second face arc of each tooth forms a base portion of the second side of the respective tooth, wherein the first and second face arcs each comprise a roller seating curve. 36. A drive sprocket as claimed in claim 34 or claim 35 wherein each first and second side comprises a second portion comprising a convex arc extending from a respective roller seating curve towards a tip portion of a respective tooth. 37. A drive sprocket as claimed in any one of the claims 34 to 36 further comprising a supporting curve extending from the roller seating curve of a first tooth towards the roller seating curve of an adjacent tooth. 38. A transmission system comprising a drive sprocket according to any one of claims 34 to 37 further comprising a drive member, which drive member is adapted to mesh with the drive sprocket. 39. A transmission system as claimed in claim 38 wherein the drive member comprises a plurality of engagement pockets, each of which engagement pockets comprising a first engaging surface and a second engaging surface spaced apart from the first engaging surface. 40. A transmission system as claimed in claim 39 wherein the drive member comprises a roller chain and wherein the engagement pockets are defined between adjacent rollers forming the roller chain. 41. A transmission system as claimed in claim 40 wherein the roller chain has a pitch p, and the distance between the centre of the first face arc and the centre of the second face arc of each tooth, and the distance between the centre of the first face arc of a first tooth and the centre of the second face arc of an adjacent tooth is substantially equal to p. 42. A transmission system as claimed in claim 40 or claim 41 wherein the radius of each roller forming the roller chain is substantially equal to, or slightly smaller than, the radius of each arc forming the first and second faced arcs. 43. A drive member forming part of a transmission system as claimed in any one of claims 38 to 42. 44. A transmission system comprising a drive sprocket and a drive member adapted to mesh with the drive sprocket, the drive sprocket comprising a plurality of teeth for meshing with the drive member to transmit rotary motion and the drive member comprising a plurality of engagement pockets adapted to engage the teeth of the drive sprocket, wherein each tooth of the drive sprocket has a tooth profile defined by a first side comprising a first engagement surface and an opposite second side comprising a second engagement surface, which engagement surfaces are configured such that when driven, a tooth meshes to an engagement pocket at a first contact location on the first engagement surface and also at a second contact location on the second engagement surface, the first contact location being radially offset from the second contact location, wherein the drive member comprises a roller chain comprising a plurality of spaced apart rollers, each roller being spaced apart from adjacent rollers by a predetermined distance, and connected to an adjacent roller by a rigid connecting member extending between two adjacent rollers whereby the engagement pockets are defined between adjacent rollers, wherein, a first engagement pocket is formed by first and second rollers which are adjacent to one another, a second engagement pocket is formed by the first roller and a third roller, and a third engagement pocket is formed by the second roller and a fourth roller, the third roller being adjacent to the first roller, and the fourth roller being adjacent to the second roller, and wherein an angle formed between a connecting member connecting the first and second rollers, and a connecting member connecting the first and third rollers, comprises a first articulation angle, and an angle formed between the connecting member connecting the first and second rollers, and a connecting member connecting the second and fourth rollers comprises a second articulation angle, wherein, the magnitude of the first articulation angle formed when the first second and third rollers are all in contact with a tooth is different to the magnitude of the second articulation angle formed when the first second and fourth rollers are all in contact with a tooth. 45. A transmission system according to Claim 44 wherein the drive member comprises a plurality of articulation points, and the articulation angles are defined at articulation points. 46. A transmission system according to Claim 44 or Claim 45 wherein the first roller comprises a load bearing roller and the second roller comprises a supporting roller. 47. A transmission system according to any one claims 44 to 46 wherein the magnitude of the first articulation angle is greater than the magnitude of second articulation angle. 48. A transmission system according to any one of claims 44 to 47 wherein magnitude of every other articulation angle is substantially the same. 49. A transmission system according to any one of the claims 44 to 48 wherein the shape of each tooth face is symmetrical about a radial axis of the tooth. 50. A transmission system according to any one of claims 44 to 49 wherein the first side of each face is defined at least partially by a first face arc, and the second side of each face is defined at least partially by a second face arc. 51. A transmission system according to any one of claims 44 to 50 wherein the first face arc forms a base portion of the first side of each tooth, and the second face arc forms a base portion of the second side of each tooth, wherein the first and second face arcs each comprise a roller seating curve. 52. A transmission system according to Claim 51 wherein the roller seating curve is adapted to receive a roller which is adapted to mesh with the sprocket. 53. A transmission system according to any one of claims 44 to 52 wherein each first and second side comprises a second portion comprising a convex arc extending from a respective roller seating curve towards a tip portion of a respective tooth. 54. A transmission system according to any one of claims 44 to 52 comprising a supporting curve extending from the roller seating curve of a first tooth towards a roller seating curve of an adjacent tooth. 55. A transmission system according to any one of claims 44 to 54 wherein the roller chain comprises a plurality of inner links, each of which serves to connect two rollers to form a roller pair, and a plurality of outer links, each of which serves to connect roller pairs to one another to form the roller chain, such that a space is defined between inner surfaces of facing inner links, and also between inner surfaces of facing outer links wherein each tooth of the sprocket tooth has a width which is the same as, or slightly less than the distance between inner surfaces of facing outer links, and greater than the distance between inner surfaces of facing inner links. 56. A transmission system according to claim 55 wherein each tooth of the sprocket comprises a first width which is the same as or slightly less than the distance between inner surfaces of facing inner links, and a second width that is the same as or slightly less than the distance between the inner surfaces of facing outer links. 57. A sprocket forming part of a transmission system according to any one of claims 44 to 56. |
Table 1 Example values for R, x & y given p, p2, r, n, ^ & ^ Referring to Figures 14 to 20, and initially to Figure 14, a power transmission drive member according to an embodiment of the invention is designated generally by the reference numeral 100. The drive member 100 is shown articulating around a drive sprocket 200, shown in more detail in Figure 20. As can be seen, particularly from Figure 20, sprocket 200 comprises a first set of teeth 210 and a second set of teeth 220. The sets of teeth 210, 220 are spaced apart from one another by the sprocket body 230. In other embodiments of the invention, the drive sprocket 200 may be replaced by two separate sprockets each having a single set of teeth and spaced apart from one another so that the teeth of both sprockets engage with the drive member. In this embodiment of the invention, the drive member comprises a hollow pin bush chain 110 comprising inner links 120 and outer links 130, the links 120, 130 being connected together by hollow pins 140 as shown particularly in Figures 15 and 16, for example. The drive member 100 further comprises engaging mechanisms 300, as shown particularly in Figure 18. In this embodiment of the invention each engaging mechanism comprises two engaging bodies 310. Each of the engaging bodies 310 comprises an engagement pocket 320 adapted to engage with the drive sprocket 200. Each engagement pocket comprises a first engaging surface 330 and a second engaging surface 340 spaced apart from the first engaging surface 330. Together the first and second engaging surfaces 330, 340 form an engaging surface pair 350 which is rotatable about an engaging mechanism rotational axis shown by the dotted line 360 in Figure 18. When the drive member 100 articulates with the sprocket 200, each tooth 240 of the drive sprocket 200 will engage with an engaging body 310 by contacting both the first engaging surface 330 and the second engaging surface 340 of the engaging body 310. In other words the engaging mechanisms 300 are adapted to engage with each tooth 240 of the sprocket 200 using the principle of dual engagement, whereby contact is made on both sides of each tooth 240 to enable a secure engagement that is energetically efficient and able to distribute the load of the chain over a larger number of teeth of the sprocket 200. The first and second engaging surfaces 330, 340 are configured such that when driven, a tooth 240 of the sprocket 200 meshes to the engagement pocket 320 of an engaging mechanism 300 at a first contact location 250 on the first engaging surface 330, and also at a second contact location 260 on the second engaging surface 340. During use, the first contact location 250 is radially offset from the second contact location 260. This helps to prevent the engagement pockets 320 from becoming wedged or stuck on a tooth 240 during use. In this embodiment of the invention, the first and second engaging surfaces 330, 340 are formed on first and second pins 280, 290 respectively. The pins 280, 290 may be integrally formed with the remainder of the engagement body 310. In another embodiment of the invention, the pins 280, 290 may be formed separately from the remainder of the engagement body 310 as shown in Figure 19. In this embodiment, the engaging body 310 comprises pin apertures 370 shaped such that the pins 280, 290 may be press fitted into the pin apertures 370. In another embodiment of the invention, the pins 280, 290 have a semi-circular cross- section, with the engaging surfaces being formed on the curved portion of the pins 280, 290. In another embodiment, the first and second engaging surfaces 330, 340 are formed from folded sheet material. Alternatively, the engaging body 310 is shaped to optimise engagement with a sprocket tooth 240. Each of the engaging bodies 310 comprises an aperture 270, the centre of which is coaxial with the engaging mechanism rotational axis 360. The engaging mechanisms 300 each further comprise a connecting member 400, having a first end 410 and a second end 420. The connecting member 400 is attachable to a first engaging body 310 at its first end 410 and to a second engaging body 310 at its second end 420, such that it extends coaxially with the rotational axis of the respective engaging mechanism. In this embodiment of the invention, the first and second ends 410, 420 of the connecting member 400 each fit into an aperture 270 of an engaging body 310 such that both engaging bodies 310 of an engaging mechanism 300 rotate about the rotational axis 360 with the connecting member 400. In other words, the engaging bodies 310 are not able to rotate independently of the connecting member. The aperture 270 thus serves as a receiving portion adapted to receive the connecting member 400. In some embodiments of the invention, the aperture 270 is profiled. This may aid orientation of the engaging body 310 relative to the connecting member 400. In this embodiment of the invention, each connecting member 400 extends through a hollow pin 140, thereby connecting the engaging mechanisms 300 to the chain 110, such that a first engaging body 310 is on one side of the chain 110, and the other engaging body 310 is on the other side of the chain. Both of the engaging bodies 310 are thus external to the chain 110, with the engaging surfaces extending away from the chain, and the connecting member 400 extending transversely across the chain. In addition, both engaging bodies 310 rotate about the rotation axis 360. By means of the invention, therefore, a standard hollow pin bush chain may be readily adapted so that it can engage with either two sprockets, or, as is the case in this embodiment, it can engage with a single sprocket 200 having two sets of teeth 210, 220, whereby the teeth 240 of the sprocket 200 mesh with engagement pockets 320 positioned externally to the chain. Referring now to Figures 21 to 23, a power transmission drive member 1100 according to another embodiment of the invention is shown articulating around a drive sprocket 1200, having teeth 1240. In this embodiment of the invention, the power transmission drive member 1100 comprises a hollow pin chain 1110 which is narrower than a conventional hollow pin chain of the type shown in Figure 34 for example. The chain 1110 comprises inner links 1120, and outer links 1130 which are similar to the links 110 and 120 of the chain 110 of Figure 3, except that the width of the chain 1110 no longer has to be wide enough to accommodate sprocket teeth. This is because the teeth 1240 of sprocket 1200 engage externally of the chain 1110 in the same way as described herein above with respect to the embodiment illustrated in Figures 14 to 20. Because the width of the chain 1110 is narrower than that of chain 110, the space between the two sets of teeth of sprocket 1200 is correspondingly narrower than the space between the two sets of teeth of sprocket 200. In an alternative embodiment illustrated in Figures 24 and 25, the inner links 1120 are replaced by a single plate 1135, which plate comprises first and second hollow pin receiving portions adapted to receive a hollow pin in a similar manner to the previous embodiments described above. In all other respects, the power transmission drive member 1100 contains corresponding parts and operates in the same way as power transmission drive member 100. Turning now to Figure 26 a further embodiment of the invention is shown. In this embodiment, the inner link 1135 has been replaced by a plurality of thinner link plates 1235 forming a composite inner link. This can be advantageous from a manufacturing point of view, and also means that by having a plurality of link plates 1235, the thickness of the composite link can be varied according to suit the application. Turning now to Figures 27 and 28, another embodiment of a power transmission drive chain according to an embodiment of the invention is shown. In this embodiment of the invention, the power transmission drive member comprises a bush chain 4200 comprising solid pins 4300 which extend across the width of the chain 4200. Each of the pins 4300 has a pin extension 4320 at either end of each pin 4300. Each of the pins 4300 passes through apertures in the outer link plates 4130 and the inner link plates 4120 as well as bushes 4150. The pins are sized and shaped so that there is an interference fit between each pin and a respective outer link plate 4130. Each pin extends between respective engaging bodies 310, and each pin extension 4320 is adapted to pass through the aperture 270 of each engaging body 310. Each pin extension is sized and shaped such that there is a clearance fit between each pin extension 4320 and a respective engaging body 310. In such embodiments of the invention each engaging body 310 is able to rotate independently about a respective pin extension 4320. Each pin 4300 may have a head formed at each end thereof in order to prevent each engaging body 310 from becoming detached from a respective pin 4300. Referring now to Figures 29 to 32 part of a power transmission drive member 2100 according to another embodiment of the invention is shown. In this embodiment, each engaging mechanism 2300 comprises two engaging bodies 2310 which are spaced apart from one another. Each engaging mechanism further comprises first and second extension members 2500, 2510, which extend through each engaging body and serve to connect two engaging bodies 2310 to one another. Each extension member 2500, 2510 extends through the engaging bodies 2310 to form pins 2280, 2290 on which the first and second engaging surfaces 2330, 2340 are formed. The first and second engaging surfaces of both engaging bodies 2310 are thus integrally formed. The drive member 2100 comprises a chain 2110, part of which is shown particularly in Figure 30. The chain comprises outer links 2120, and inner links 2130 connected together by a hollow pin 2140. Each link 2120, 2130 comprises a body portion 2520, and first and second legs 2530, 2540 integrally formed with the body portion 2520, and extend from the body portion 2520 to define a space 2550 between the legs 2530, 2540 and the body portion 2520. Each leg 2530, 2540 comprises a hollow pin receiving portion 2560, and each link 2120, 2130 is positionable on the engaging bodies 2310 such that the hollow pin receiving portion 2560 of a first leg 2530 of a link is coaxial with the rotational axis of a first engaging mechanism, and the hollow pin receiving portion 2560 of the second leg of the link is coaxial with the rotational axis of a second, adjacent engaging mechanism. This means that the hollow pin receiving portions 2560 are coaxial with the apertures 2270 of the engaging bodies 2310. Each engaging mechanism 2300 further comprises a central pin 2570 which passes through a respective hollow pin 2140. Each hollow pin 2140 fits through the hollow pin receiving portion 2560 of a respective inner link 2130. The central pin 2570 extends through the hollow pin 2140 and the respective apertures 2270 of both engaging bodies 2310, with the engaging bodies 2310 positioned on either side of the outer link 2120. This arrangement enables the engaging mechanisms to rotate about their respective rotational axes. The space 2550 provides space for the rotation. The engaging mechanism 2300 and the engaging bodies 2310 are equivalent to the engaging mechanism 300 and the engaging bodies 310 and function in the same way. In particular, the first and second engaging surfaces 2330, 2340 form an engagement pocket 2320 which is equivalent to engagement pocket 320 and therefore results in dual engagement of the tooth of a sprocket in the pitch pocket as described with reference to the previous embodiment. Turning now to Figures 33 a further embodiment of an outer link plate 3120 is shown including angle of rotation limiters. These limiters are designed to prevent over rotation of the engaging bodies during use. In the embodiment shown in Figure 33, the outer link plate 3120 comprises limiters 3600 formed from bent sections of the outer link plate 3120. The angle limiters 3600 limit the rotational movement of the engaging bodies 3310 and thus reduce the likelihood that the engaging bodies will become stuck. By means of the present invention, and as described above, each tooth of a drive sprocket will engage with an engaging body by contacting both a first engaging surface and a second engaging surface. This dual engagement reduces the stress on the sprocket as well as relative movement between the chain and sprocket during use thereby reducing wear and tear on the drive member as well as the drive sprocket. In addition, frictional losses are reduced, thereby increasing transmission efficiency. Referring now to Figures 34 and 35 a transmission system according to an embodiment of the invention is designated generally by the reference numeral 2. The transmission system comprises a sprocket 4 and a drive member comprising a roller chain 6. In this embodiment of the invention the roller chain 6 is a standard roller chain comprising a plurality of rollers 8 which extend transversely across the transmission member and are spaced apart along the length of the drive member to form the chain. The rollers are connected to one another by links 10 in a known manner. The roller chain 6 is able to articulate between adjacent rollers 8. An engagement pocket 40 is defined between adjacent rollers 8. Each engagement pocket 40 is adapted to engage with a tooth 12 as will be described in more detail below. By means of the present invention, however, only every other engagement pocket 40 will engage with a tooth during use of the transmission system 2. The remaining every other engagement pockets 40 will effectively engage with the space between adjacent teeth 12. Turning now to Figure 36, the sprocket 4 is shown in more detail. The sprocket 4 comprises a plurality of teeth 12 which are all shaped substantially identically to one another. Each tooth has a tooth face or profile 14 which is symmetrical about a radial axis R of the sprocket 4. The tooth profile 14 is defined by a first side 16 comprising a first engagement surface 18, and a second side 20 defining a second engagement surface 22. Each of the first and second sides 16,20 comprises a base portion 24 which forms a roller seating curve 25. Each side further comprises a portion 26 extending from the roller seating curve towards a tip 28 of the tooth. The portion 26 is convex and defines a working curve 29. The sprocket 4 comprises a further curve 30 forming a supporting curve 31 which extends between adjacent teeth. As shown in Figures 37 and 38 particularly, in use of the transmission system 2, every other engagement pocket 40 will engage with a respective tooth 12 whilst the remaining every other engagement pocket 40 will not engage a tooth. This is because, due to the dimensions of the sprocket, and particularly the profile of the tooth, relative to the dimensions of the rollers 8, when the roller chain 6 is engaged with the sprocket 4 there will be two rollers 8 positioned between adjacent teeth. This in turn means that every other engagement pocket 40 will engage with a tooth 12, with every other engagement pocket effectively engaging with spaces between adjacent teeth 12 of the sprocket. Referring to Figure 37 the manner in which the rollers 8 engage with the sprocket 4 during use of the transmission system 2 is shown schematically. When considering a pair of rollers 8 positioned on either side of a tooth 12, one roller 32 will be a load bearing roller, and the second roller 8 will be a supporting roller 34. The roller seating curve 25 provides an initial seating position for the engaged rollers 8 of the roller chain 6. For both load bearing and supporting rollers, this curve helps to distribute the contact load over a larger area reducing material stresses, at least initially when the chain wear is low. The roller seating curve 25 enables rollers to easily transition between supporting and load bearing positions if the drive direction is ever reversed. The load bearing roller 32 will engage with the tooth 12 on a first engagement surface 36, and the support roller 34 will engage with the tooth at a second engagement surface 38. The first and second engagement surfaces 36,38 are radially offset from one another. This enables the pair of rollers 8 engaging the tooth 12 to engage with dual engagement, since the roller chain makes contact with the sprocket teeth 12 at two contact points 37, 39 on engagement surfaces 36, 38 in each tooth of the sprocket. The two contact points 37, 39 are thus on opposing sides of the tooth relative to its radial centreline R, and are radially offset from one another and therefore not symmetric relative to the radial centreline R. The combination of these features leads to a secure engagement of the drive sprocket tooth by the roller chain 6 and ensures that the rollers 8 do not become wedged on the tooth. In addition, there is little to no relative movement between the tooth and the rollers 8 whilst in contact. The first contact point 37 is load bearing and transfers the load between the roller chain 6 and the tooth 12. The second contact point 39 is supporting and thus stabilises the roller chain 6 on the sprocket 4 and increases the load distribution over the sprocket teeth 12. As shown in Figures 36 and 37, each tooth 12 further comprises a working curve 26 that extends from the roller seating curve towards the tip 28 of the tooth. The working curve 26 is convex, and the convex arc forming the working curve 26 curves towards the tooth centreline R. The surface of working curve 26 makes contact with the load bearing roller 32, enabling torque transfer between the roller chain 6 and the sprocket 4. As the chain pitch elongates due to internal wear, this surface also accommodates the climbing of the load-bearing roller as shown in Figure 40. The tip 28 of each tooth does not need to have a pointed profile. This is because when an engagement pocket 40 is at the point of engagement with the tooth 12 it has a single degree of freedom only which is the articulation of the engagement pocket about the centre of the roller. The working curve is the primary load bearing contact surface situated on an upper portion of the sides of each tooth. It is this surface that makes contact with the load bearing roller 32, enabling torque transfer between chain and sprocket. As the chain pitch elongates due to internal wear, this surface also accommodates the climbing of the load bearing roller ensuring that the sprocket is able to transfer load through the entire lifetime of the chain. Turning again to Figure 36, the sprocket further comprises a supporting curve 50 which extends between the roller seating curves of adjacent teeth. The supporting curve is designed to accommodate the supporting roller 34. The supporting curve may also accommodate some movement of the supporting roller 34 over the lifetime of the roller chain 6, as the worn chain adopts an altered position on the sprocket. Referring specifically to Figures 37 and 38, the engaging pockets 40 are represented by lines 42. The line 42 of each engagement pocket sits with endpoints situated on a circle 44 known as the pitch circle. The pitch circle defines the centre point of all the roller seating curves 25. In this embodiment of the invention the radius of each roller seating curve is slightly larger than the radius of each roller. This results in the engagement pockets 40 sitting marginally off the pitch circle 44. This in turn ensures that the rollers adopt their respective load bearing and supporting positions and prevents the engagement pockets from getting stuck on the teeth. Referring to Figure 39, the dimensions of the roller chain 6 are shown in more detail. As can be seen from Figure 39, the distance between adjacent rollers, known as the chain pitch, may be represented by the letter p, and the diameter of each roller may be represented by dr. Referring now to Figure 40, a schematic representation of part of the transmission system 2 of Figure 34 is shown. The circle radius r p represents the pitch circle. This is the circle which passes through all of vertices of a regular polygon of n sides, for a sprocket 4 which has n/2 teeth. Each side of the regular polygon has a length ρ. Figure 40 shows three of the sides of the regular polygon showing the length as ρ. The radius of the arc forming the first face arc and the second face arc may be represented by r s . The centre of a roller seating curve 25 with radius r s sits at each vertex of the regular polygon forming the bases of the teeth. The radius of the arc may be compared with the radius of the roller and given as a ratio ρ. In addition, the steepness of the working curve relative to the centreline of the tooth at the contact point of the load bearing roller 32 may be denoted by Θ. In embodiments of the invention, the ratio ρ was found to be 1.01 regardless of the number of teeth on the sprocket 12. Θ was found to vary depending on the number of teeth forming the sprocket. A representative, but non-exhaustive list of values for Θ is set out below:
Thus, it can be seen that in a transmission system according to an embodiment of the invention, the teeth 12 of the sprocket 4 will have a profile that hardly varies depending on the number of teeth forming the sprocket. By means of the embodiments of the invention therefore a standard roller chain, for example a roller chain meeting the ISO 606 standard, is able to engage a sprocket such that dual engagement is achieved. In embodiments of the invention where the sprocket 4 has n teeth, the roller seating arc has a fixed radius r s for all n, and this radius is slightly larger than the radius of each roller 8. Referring initially to Figures 34 and 35 a transmission system according to an embodiment of the invention is designated generally by the reference numeral 2. The transmission system comprises a sprocket 4 and a drive member comprising a roller chain 6. In this embodiment of the invention the roller chain 6 is a standard roller chain comprising a plurality of rollers 8 which extend transversely across the transmission member and are spaced apart along the length of the drive member to form the chain. The rollers are connected to one another by links 10 in a known manner. The roller chain 6 is able to articulate between adjacent rollers 8. An engagement pocket 40 is defined between adjacent rollers 8. Each engagement pocket 40 is adapted to engage with a tooth 12 as will be described in more detail below. By means of the present invention, however, only every other engagement pocket 40 will engage with a tooth during use of the transmission system 2. The remaining every other engagement pockets 40 will effectively engage with the space between adjacent teeth 12. Turning now to Figure 36, the sprocket 4 is shown in more detail. The sprocket 4 comprises a plurality of teeth 12 which are all shaped substantially identically to one another. Each tooth has a tooth face or profile 14 which is symmetrical about a radial axis R of the sprocket 4. The tooth profile 14 is defined by a first side 16 comprising a first engagement surface 18, and a second side 20 defining a second engagement surface 22. Each of the first and second sides 16,20 comprises a base portion 24 which forms a roller seating curve 25. Each side further comprises a portion 26 extending from the roller seating curve towards a tip 28 of the tooth. The portion 26 is convex and defines a working curve 29. The sprocket 4 comprises a further curve 30 forming a supporting curve 31 which extends between adjacent teeth. As shown in Figure 37 particularly, in use of the transmission system 2, every other engagement pocket 40 will engage with a respective tooth 12 whilst the remaining every other engagement pocket 40 will not engage a tooth. This is because, due to the dimensions of the sprocket, and particularly the profile of the tooth, relative to the dimensions of the rollers 8, when the roller chain 6 is engaged with the sprocket 4 there will be two rollers 8 positioned between adjacent teeth. This in turn means that every other engagement pocket 40 will engage with a tooth 12, with every other engagement pocket effectively engaging with spaces between adjacent teeth 12 of the sprocket. Referring to Figure 37 the manner in which the rollers 8 engage with the sprocket 4 during use of the transmission system 2 is shown schematically. When considering a pair of rollers 8 positioned on either side of a tooth 12, one roller 32 will be a load bearing roller, and the second roller 8 will be a supporting roller 34. The roller seating curve 25 provides an initial seating position for the engaged rollers 8 of the roller chain 6. For both load bearing and supporting rollers, this curve helps to distribute the contact load over a larger area reducing material stresses, at least initially when the chain wear is low. The roller seating curve 25 enables rollers to easily transition between supporting and load bearing positions if the drive direction is ever reversed. The load bearing roller 32 will engage with the tooth 12 on a first engagement surface 36, and the support roller 34 will engage with the tooth at a second engagement surface 38. The first and second engagement surfaces 36,38 are radially offset from one another. This enables the pair of rollers 8 engaging the tooth 12 to engage with dual engagement, since the roller chain makes contact with the sprocket teeth 12 at two contact points 37, 39 on engagement surfaces 36, 38 in each tooth of the sprocket. The two contact points 37, 39 are thus on opposing sides of the tooth relative to its radial centreline R, and are radially offset from one another and therefore not symmetric relative to the radial centreline R. The combination of these features leads to a secure engagement of the drive sprocket tooth by the roller chain 6 and ensures that the rollers 8 do not become wedged on the tooth. In addition, there is little to no relative movement between the tooth and the rollers 8 whilst in contact. The first contact point 37 is load bearing and transfers the load between the roller chain 6 and the tooth 12. The second contact point 39 is supporting and thus stabilises the roller chain 6 on the sprocket 4 and increases the load distribution over the sprocket teeth 12. As shown in Figure 37, each tooth 12 further comprises a working curve 26 that extends from the roller seating curve towards the tip 28 of the tooth. The working curve 26 is convex, and the convex arc forming the working curve 26 curves towards the tooth centreline R. The surface of working curve 26 makes contact with the load bearing roller 32, enabling torque transfer between the roller chain 6 and the sprocket 4. As the chain pitch elongates due to internal wear, this surface also accommodates the climbing of the load-bearing roller. Turning again to Figure 36, the sprocket further comprises a supporting curve 50 which extends between the roller seating curves of adjacent teeth. As mentioned above, the rollers 8 of the roller chain 6 are able to articulate relative to one another via the links connecting adjacent rollers to one another. In Figure 44 two articulations angles are shown, a 1 and a 2 and these will now be explained further. First roller 32 and second roller 34 are shown forming a first engagement pocket 401 which meshes with a first tooth 112. A third roller 322 is in contact with a second tooth 212 and is positioned to one side of the first roller 32. The third roller 322 and the first roller 32 together form a second engagement pocket 402. A fourth roller 422 is positioned adjacent to second roller 34 and is in contact with a third tooth 312. The second and fourth rollers 34, 422 together form a third engagement pocket 403. In this embodiment of the invention, the first roller 32 is a load bearing roller, and the second roller 34 is a support roller. Every other roller starting with the load bearing roller 32 will also be a load bearing roller. With reference to Figure 42 therefore, the fourth roller 422 is also a load bearing roller. This pattern will repeat itself around the sprocket 4. At the point that first roller 32 makes contact with first tooth 112, and third roller 322 is also in contact with a second tooth 212, first roller 32 and third roller 322 are positioned on their respective engagement surfaces, and the second roller 34 is in position, a first articulation angle a 1 is formed at an articulation point 400, which in this embodiment coincides with the axis of the first roller 32. Considering now the second roller 34 and fourth roller 422, the second articulation angle a2 is formed at the second roller 34 when the second roller 34 and the fourth roller 422 are in contact with a respective tooth 12, and the first roller 322 is in contact with tooth 112. The magnitude of the first articulation angle a1 at the point defined above, is in this example greater than the second articulation angle a2 at the point defined above. Similarly, every other roller starting with the second roller 34 is a support roller. In this embodiment therefore the third roller 322 is also a support roller and this pattern will repeat itself around the sprocket 4. In this embodiment, every other articulation angle will be the same. This means that the articulation angle a1 will be at every load bearing roller, and the articulation angle a 2 will be at every support roller. Adjacent rollers are connected to one another by a link which provides a rigid connection between adjacent rollers. In this embodiment, first roller 32 is connected to second roller 34 by link 450. Third roller 322 is connected to first roller 32 by link 452, and second roller 34 is connected to fourth roller 422 by link 454. It is the links 450, 452, 454 which articulate relative to one another as shown by the articulation angles. Because the articulation angle at each load bearing roller 32, 422 is larger in this embodiment that the articulation angle a 2 at every support roller 34, 322, each load bearing roller 332 will articulate for a longer duration than is the case with each support roller 34. This can improve the efficiency of the transmission system. By means of the present invention therefore it is possible to achieve selective articulation by setting the articulation angle at each tooth to be different, or to follow a regular pattern as is the case in this embodiment. This is desirable from the perspective of both power transmission efficiency and chain wear. Articulation under load causes inevitable friction between adjacent chain links. This leads to both energy loss and component wear. The size of these losses is roughly proportional to the size of the articulation angle. The losses associated with each articulation alternates with the alternating inner and outer chain links of a standard power transmission roller chain. The articulation of the outer link is more efficient than the inner, while the articulation of the inner link leads to less chain elongation than the outer. By using selective articulation, the magnitude of the beneficial or deleterious effects of a given articulation can be manipulated to improve the drive trains overall performance. As shown particularly in Figures 43 and 44, the articulation points 400 in a transmission system according to embodiments of the invention define a n sided irregular polygon 500. In embodiments of the invention where the first articulation angle is a 1 and the second is a2, the pattern is repeated for every pair of links around the sprocket circumference. Thus, the relationship between these new articulation angles and the original exterior angle of a polygon of n sides, a is, a1+a2=2a as shown in Figure 43. To achieve this n sided irregular polygon, a sprocket of n/2 teeth is used, where a tooth sits between the vertices of every other side of the polygon. This is shown more clearly in Figure 44. Turning now to Figures 45 to 47, a sprocket 904 according to another embodiment of the invention is illustrated schematically. The sprocket 904 forms part of a transmission system 1002 comprising the sprocket 904 and a roller chain 6. Parts of the transmission system 1002 that are equivalent to the transmission system 2 described above will be given corresponding reference numerals for ease of reference. As shown particularly in Figure 45, the roller chain 6 comprises a plurality of rollers 8. The rollers 8 are connected to adjacent rollers by means of inner links 810 and outer links 820. The inner links 810 serve to connect two rollers 8 together to form a roller pair 850. The outer links serve to connect roller pairs 850 together to form the roller chain 6. The distance between inner surfaces 860 of inner links 810 is indicated by the reference numeral d 1 in Figure 45. The distance between inner surfaces 870 of facing outer links 820 is indicated by the reference numeral d 2 . As shown in Figure 45, d 2 is greater than d 1 . Turning now to Figures 46 and 47, the sprocket 904 is described in more detail. The sprocket comprises a plurality of teeth 12 spaced apart around the sprocket. Each tooth has a first width 914 that is equal to or slightly less than the distance between inner surfaces of facing inner links 800 (d 1 ). Each tooth 12 also has a second width 915 which is equal to or slightly less than the distance between the inner surfaces 870 of outer links 820 (d2). In this embodiment of the invention each tooth comprises a middle tooth portion 920 and outer tooth portions 922, 924 which together define the second width. When the sprocket 904 engages with the roller chain 6, the teeth will be positioned between two outer links as shown in Figure 47. The width of the outer tooth portions 922, 924 together with the width of the middle portion 920 results in an overall tooth width that is the same as or slightly less than the distance (d 2 ) between inner surfaces of facing outer links, and greater than the distance (d 1 ) between the inner surfaces of facing inner links. This means that the fit between the tooth 12 and the chain 6 is such that there is little clearance between the tooth and the chain. Furthermore, the presence of the outer tooth portions 922, 924 prevents the teeth from engaging between inner links, and thus the alignment of the chain is substantially maintained during use of the drive transmission system. In addition, the presence of the middle portion 920 prevents the inner links from interfering with the tooth during use.
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