POWER TRANSMISSION TOOTHED BELT AND DRIVE

Abstract: A power transmission toothed belt drive having a belt tooth power transmission surface (18) defined by an arc having a radius centered on a point (20) approximately one-half the belt tooth pitch from the centerline of the tooth. The pulley groove (26) has a sidewall surface (31) which confronts the power transmission surface (18) of the belt tooth centered on the same point (20) when the belt tooth (14) is fully meshed with the pulley groove (26) in the operation of the drive. A relatively small clearance with the pulley is provided adjacent the belt tooth root (16) and a relatively large clearance is provided be­ tween the pulley groove inner surface (36) and the tip surface (17) of the belt tooth. In one form of the invention, both the pow­ er transmission surface and tip surface of the belt tooth are defined by a single radius and the confronting pulley groove sidewall surface (31) and inner surface (36) confronting the belt tooth power transmission surface (18) and tip surface (17) have a constant clearance therewith and are defined by continuous circular arcs.

Description: This invention relates to power transmission belt drives and in particular to power transmission toothed belt drives. Toothed belt drives are advantageously adapted for providing positive power transmission free of slip, with relatively low noise. A common form of such toothed belt drive is one wherein the belt tooth has a trapezoidal cross section and the pulley groove is complementary thereto. A number of belt drives have been developed utilizing rounded teeth. In the conventional toothed belt drive system, the belt tooth has a maximum backlash at the root portion thereof. While such a belt smoothly engages the pulley, such belts tend to wear rapidly and because of the possible movement of the belt relative to the pulley at start-up, the pulley tends to scrape the surface of the belt tooth, further aggravating the wear problem. One solution to this problem has been to apply a substantial tension to the belt so as to minimize the movement of the belt relative to the pulley at start-up. It has been found, however, that the application of high tension to the belt causes the belt to lengthen and have shortened useful life due to early breakage thereof. Another attempted solution to the problem has been to provide a toothed belt drive wherein there is a constant clearance between the belt tooth and the pulley groove sidewall from the belt tooth root to the belt tooth tip. This attempted solution has not proven fully satisfactory because of the interference with the pulley by the belt teeth, requiring the belt tension to be reduced. With reduced belt tension, the belt tends to jump from the pulley grooves under low loads. In one form of prior art belt, the power transmission surface portion of the belt tooth flank is defined by an arc centered on the belt pitch line. Such design, however, causes the teeth to be relatively small so as to reduce the force transmission capabilities and thereby aggravating the belt jumping problem. Another attempted solution has been to locate the centre of the power transmission surface arc on the belt land line. This results, however, in the inclination of the belt tooth power transmission surface to become relatively large, thereby increasing interference of the belt with the pulley and requiring an increased backlash at the belt tooth root, thereby again causing the problem of movement of the belt relative to the pulley during start-up or upon reverse rotation of the drive. The various problems cause a reduction in the accuracy in the positive driving by such toothed belts and is a vexatious problem which has not been fully solved, notwithstanding the longstanding need for such a solution. In FR-A-2238094, there is disclosed a power transmission toothed belt comprising a belt body defining a longitudinal pitch line and an inner land line, and a plurality of teeth projecting inwardly from said body, each tooth defining a centerline and being symmetrical about said centerline, each side of the tooth being defined by a convex radially outer root surface, an inner tip surface, and an intermediate power transmission surface, said power transmission surface defining a circular arc having a radius centered at a point spaced from said centerline approximately one-half the pitch of the teeth, and said radius having a length less than the pitch of the teeth. In EP-A-0106694, there is disclosed a flexible power transmission belt having a plurality of teeth each of which has a pair of arcuate convex flank portions which in longitudinal cross-section closely approximate to an arc of a circle. Each tooth exhibits a height to width relationship within a predetermined range, and the arcuate flanks each have a pressure angle within a predetermined range of 18° to 23°. The belt is preferably used in combination with a toothed pulley whose teeth are substantially conjugate to the belt teeth and whose cavities between the teeth have a height to width relationship within another predetermined range and have concave flanks exhibiting a pressure angle in still another predetermined range, said belt tooth width being approximately 0.98 of the pulley cavity width. According to the present invention, there is provided a power transmission toothed belt comprising: a belt body defining a longitudinally pitch line and an inner land line; and a plurality of teeth projecting inwardly from said body, each tooth defining a centerline and being symmetrical about said centerline, each side of the tooth being defined by a concave radially outer root surface, an inner tip surface, and an intermediate power transmission surface, said power transmission surface defining a circular arc having a radius centered at a point spaced from said centerline approximately one-half the pitch of the teeth, said radius having a length less than the pitch of the teeth, said power transmission surface extending inwardly from a first junction with an outer end of said root surface, said first junction being spaced inwardly from said land line approximately one-fourth the height of the belt tooth from said land line or less, and said tip surface extending inwardly from a second junction with an outer end of said power transmission surface; characterised in that a line extending through said first and second junctions intersects said tooth centerline at an angle in the range of approximately 9° to 18°. Preferably, the second junction is spaced inwardly from the land line approximately two-thirds the height of the belt tooth from the land line, or less. Preferably, the line extending through the first and second junctions intersects the tooth centerline at an angle in the range of approximately 12° to 14°. Preferably, the power transmission surfaces at the opposite sides of the belt tooth define reversely similar circular arcs having their respective radii centered at points spaced apart a distance in the range of approximately 0.95 to 1.05 the pitch of the teeth. The power transmission surface arc radii preferably have a length in the range of approximately 80% to 85% of the spacing between the points. The invention further comprehends the use of a power transmission toothed belt drive comprising: a power transmission toothed belt of the invention; and a pulley having a plurality of circumferential radially outwardly opening grooves, each groove being symmetrical about a radial centerline, each half of each groove having a convex outer surface defined by an arc of a circle extending inwardly from a face line defined by the radially outer distal face of a land between successive pulley grooves, a concave sidewall surface extending inwardly from said outer surface and being defined by a circular arc having a radius centered at a point spaced from said centerline approximately one-half the pitch of the grooves, and a concave inner surface. The present invention thus comprehends an improved power transmission toothed belt drive which provides a long, troublefree life of the belt over a wide range of loads and with improved high accuracy in the positioning characteristics of the drive. In the illustrated embodiment, the point at which the sidewall arc radius is centered is coincident with the point at which the power transmitting surface of the belt is centered when the belt tooth is fully meshed with the pulley in the groove. In the illustrated embodiment, the outer surface of the pulley groove is defined by a circular arc having a radius centered in the pulley. The inner surface of the pulley groove defines a circular arc having a radius centered at a point in the pulley groove, the inner pulley groove surface radius being shorter than the belt tooth tip surface radius. The pulley groove further defines a convex radially inner bottom surface and, in the illustrated embodiment, the belt tooth has a length greater than the depth of the pulley groove, whereby compression of the belt tooth is effected when the belt tooth is fully meshed with the pulley in the operation of the drive system. In the illustrated embodiment, the belt root surface defines a circular arc having a radius centered at a point inwardly of the land line, and the pulley outer surface defines a circular arc having a radius centered at a point in the pulley, the pulley groove outer surface radius being longer than the belt root surface radius. In the illustrated embodiment, the belt tooth surfaces and pulley groove surfaces are constructed such that a clearance is provided between the confronting surfaces, the clearance between the pulley groove outer surface and the belt tooth root surface being smaller than the clearance between the pulley groove sidewall surface and the belt tooth power transmission surface, and the clearance between the pulley groove sidewall surface and the belt tooth power transmission surface being smaller than the clearance between the pulley groove inner surface and the belt tooth tip surface. In a modified form of power transmission toothed belt drive system embodying the invention, the inner tip surface of the belt tooth is defined by an arc having a radius centered on the same point as that on which the power transmission surface is centered. A relatively small diameter rounded surface extends inwardly from the tip surface. The pulley groove is caused to have a similar construction in that the sidewall surface and inner surface of the pulley groove are respectively defined by arcs having radii centered on the same point and, in the illustrated embodiment, the pulley groove surface center point is coincident with the belt tooth surface center point when the belt tooth is fully meshed with the pulley groove. Thus, in the modified form, a constant clearance is had between the belt tooth power transmission and tip surfaces and the pulley groove sidewall and inner surfaces, respectively. In the modified embodiment, the flank surfaces of the tooth and pulley groove extend as a single continuous circular arc substantially to the distal end of the belt tooth and bottom of the pulley groove. The improved construction of the power transmission belt toothed drive of the present invention permits the belt to be relative large and strong for transmitting relatively high loads. An improved constant clearance between the power transmission surface and confronting pulley groove sidewall surface, and the relatively small angle of the extent of the power transmission surface relative to the centerline of the belt tooth provides improved positive power transmission with effectively minimized tendency for jumping of the belt from the pulley in the operation of the drive. The provision of a small clearance between the pulley root surface and the outer surface of the pulley groove sidewall effectively minimizes movement of the belt tooth relative to the pulley at start-up. The provision of a relatively large clearance between the tip surface of the belt tooth and the inner surface of the pulley groove minimizes interference between the belt tooth and pulley and provides for facilitated engagement and disengagement of the belt tooth relative to the pulley in the operation of the drive. The power transmission toothed belt drive of the present invention is extremely simple and economical of construction while yet providing the highly desirable features discussed above. Other features and advantages of the invention will be apparent from the following description taken in connection with the accompanying drawing wherein: FIGURE 1 is a fragmentary side elevation of a toothed belt embodying the invention; FIGURE 2 is a fragmentary side elevation of a pulley embodying the invention; FIGURE 3 is a fragmentary side elevation of the belt and pulley in meshed association; FIGURE 4 is a fragmentary side elevation of a modified form of belt embodying the invention; FIGURE 5 is a fragmentary side elevation of a modified form of pulley embodying the invention; and FIGURE 6 is a fragmentary side elevation of the modified belt and pulley constructions in meshed association. In the exemplary embodiment of the invention as disclosed in Figures 1-3 of the drawing, a toothed power transmission belt generally designated 10 is shown to include a body 11 defining a longitudinal pitch line 12 and an inner land line 13. The body may be provided with a plurality of laterally spaced tensile cords (not shown), in the usual manner. The belt further includes a plurality of teeth generally designated 14 projecting inwardly from the land line 13. Each tooth defines a centerline 15 and is symmetrical about the centerline. As shown, each side of the tooth is defined by a concave radially outer root surface 16, a convex inner tip surface 17, and an intermediate power transmission surface 18. The power transmission surface 18 defines a circular arc having a radius 19 centered at a point 20 spaced from centerline 15 approximately one-half the pitch of the teeth. As shown, radius 19 has a length less than the pitch of the teeth. Root surface 16 defines a circular arc having a radius 21 centered at a point 22 inwardly of land line 13. The power transmission surface 18 extends inwardly from a junction 23 with the outer end of the root surface to an outer junction 24 with the inner end of the tip surface 17. As seen in Figure 1, a line drawn through junctions 23 and 24 intersects the centerline 15 at an angle α. The invention comprehends that the angle a be in the range of approximately 9° to 18° and preferably in the range of 12° to 14°. Junction 23 is spaced from land line 13 approximately one-fourth the height H of the belt tooth from the land line, or less. Junction 24 is preferably spaced inwardly from the land line approximately two-thirds the height of the belt tooth from the land line, or less. A preferred spacing for the junction 24 is approximately one-half the height of the belt tooth from the land line. As further shown in Figure 1, the power transmission surfaces 18 at the opposite sides of the belt tooth define reversely similar arcs having their respective radii centered at points spaced apart a distance W. The spacing W is preferably in the range of approximately 0.95 to 1.05 the pitch of the belt teeth. The power transmission surface radius 19 preferably has a length in the range of approximately 80% to 85% of the spacing W. Belt 10 is adapted for cooperative use with an improved pulley 25 shown in Figure 2. As shown, pulley 25 has a plurality of circumferentially radially outwardly opening grooves 26. Each groove is symmetrical about a radial centerline 27. As shown in Figure 2, each half of the groove has a convex outer surface 28 defined by an arc of a circle extending inwardly from a face line 29 defined by the radially outer distal face of the lands, or teeth, 30 between the pulley grooves 26. The flank surface of the pulley groove further defines a concave sidewall surface 31 extending inwardly from the outer surface 28. Sidewall surface 31 is defined by a circular arc having a radius 32 centered at a point 33 spaced from the centerline of the groove approximately one-half the pitch of the pulley grooves P'. As shown in Figure 2, the outer surface 28 is defined by a circular arc having a radius 34 centered at a point 35 in the pulley land 30. The pulley groove further defines an inner surface 36 extending inwardly from the sidewall surface 31 and defining a circular arc having a radius 37 centered on a point 38 in the pulley groove 26. Belt tooth tip surface 17 defines a circular arc having a radius 39 centered at a point 40 in the belt tooth, as shown in Figure 1. Preferably, radius 37 of the pulley groove inner surface 36 has a length shorter than the length of radius 39. Belt tooth 14 defines a distal inner surface 42 inwardly of the tip surfaces 17 and pulley groove 26 further defines a convex radially inner bottom surface 43. The height of the belt tooth from land line 13 to the distal surface 42 is preferably greater than the depth of the pulley groove from face line 29 to the bottom surface 43. Preferably, radius 21 of the belt tooth surface is longer than the radius 34 of the pulley groove outer surface. Thus, referring to Figure 3, when the pulley tooth is fully meshed with the pulley groove, a small clearance 44 is had between the belt root surface 16 and pulley outer surface 28, a constant clearance 45 is had between the belt power transmission surface 18 and the pulley sidewall surface 31, and a relatively large clearance 46 is had between the belt tip surface 17 and the pulley groove inner surface 36. Further as seen in Figure 3, because the height of the belt tooth is greater than the depth of the pulley groove, an interference occurs at the distal end 42 of the belt tooth, causing the belt tooth to be compressed by the engagement thereof with the convex bottom surface 43 of the pulley groove. The belt tooth 14 is relatively large and strong for use in transmitting high loads. A large surface area is provided between the power transmission surface 18 of the belt tooth and the sidewall surface 31 of the pulley groove, providing improved power transmission capabilities and prevention of belt jumping. The provision of the relatively small clearance 44 at the outer end of the groove and the relatively large clearance 46 at the inner end thereof reduces the amount of movement of the belt tooth on start-up and effectively prevents interference between the belt tooth and pulley in the operation of the drive. Referring now to the embodiment of Figure 4-6, a modified form of power transmission toothed belt drive generally designated 147 is shown to comprise a drive similar to drive 47 of the embodiment of Figures 1-3, but wherein the tip surface 117 of the pulley tooth 114 comprises a continuation of the circular arc defining the power transmission surface 118 thereof. Thus, the power transmission surface 118 and tip surface 117 are defined by a single radius 148 from the point 120 corresponding to point 20 of belt 10. The junctions 123 and 124 with the root surface 116 and tip surface 117 of power transmission surface 118 are located similarly as junction 23 and 24 in belt 10 and, thus, define a relatively small angle α (i.e. 9° to 18°) with the centerline 115 of the belt tooth. The distal end of the tooth is defined by a flat surface 149 joined to the outer ends of the tip surfaces 117 by rounded corners 150. The rounded corner is defined by an arc having a radius 151 centered on a point 152 in the belt tooth. Radius 151 is relatively small. Thusly, the surfaces 118 and 117 define a continuous circular arc extending substantially the entire height of the belt tooth inwardly from the root surface 116. In all other respects, belt 110 is similar to belt 10. Elements of belt 110 which are similar to elements of belt 10 are identified by similar reference numerals but 100 higher. As shown in Figure 5, drive 147 includes a pulley 125 having a groove 126. Pulley groove 126 is similar to groove 26 of pulley 25 except that the inner surface 136 is defined by the radius 132 centered on point 133 corresponding to radius 32 and point 33 of pulley 25 and further defining the sidewall surface 131 of pulley 125. Bottom surface 143 is joined to the outer ends of the inner surfaces 136 of the pulley groove 126 by rounded corner surfaces 153. The corner surfaces are defined by a radius 154 centered on a point 155. As seen in Figure 6, the clearance 156 between the belt tooth and pulley groove flank surface is constant between the confronting surfaces 131 and 118, and the confronting surfaces 136 and 117. As in drive 47, the clearance 144 between the belt tooth root surface 116 and the pulley groove outer surface 128 is relatively small, and the clearance 146 between the rounded corners 153 of the pulley groove and 150 of the belt tooth is somewhat smaller. The length of the belt tooth is preferably approximately 3% longer than the depth of the pulley groove in the respective embodiments. Such a relationship provides for low noise engagement of the belt with the pulley by minimizing noise of contact at the pulley lands by the belt root surfaces. In each of the embodiments, an improved high load transmission characteristic is provided while yet minimizing interference between the belt and pulley in the operation of the drive. By enlarging the area of engagement between the power transmission surface of the belt tooth and the pulley groove sidewall surface, increased capability of load transmission is obtained while, at the same time, minimizing the belt jumping problem discussed above. Other than as discussed specifically above, drive 147 functions similarly to drive 47.

Claims: A power transmission toothed belt (10) comprising: a belt body (11) defining a longitudinally pitch line (12) and an inner land line (13); and a plurality of teeth (14) projecting inwardly from said body (11), each tooth (14) defining a centerline (15) and being symmetrical about said centerline (15), each side of the tooth (14) being defined by a concave radially outer root surface (16), an inner tip surface (17), and an intermediate power transmission surface (18), said power transmission surface (18) defining a circular arc having a radius (19) centered at a point (20) spaced from said centerline (15) approximately one-half the pitch of the teeth (14), said radius (19) having a length less than the pitch of the teeth (14), said power transmission surface (18) extending inwardly from a first junction (23) with an outer end of said root surface (16), said first junction (23) being spaced inwardly from said land line (13) approximately one-fourth the height of the belt tooth (14) from said land line (13) or less, and said tip surface (17) extending inwardly from a second junction (24) with an outer end of said power transmission surface (18); characterised in that a line extending through said first and second junctions (23,24) intersects said tooth centerline (15) at an angle in the range of approximately 9° to 18°. A belt (10) as claimed in claim 1, wherein said power transmission surface (18) at the opposite side of the belt tooth (14) defines reversely similar circular arcs having their respective radii centered at points spaced apart a distance (W) in the range of approximately 0.95 to 1.05 the pitch of the teeth (14). A belt (10) as claimed in claim 1 or 2, wherein said inner tip surface (17) defines a circular arc having a radius (39) centered at a point (40); and wherein said radius (39) of said tip surface (17) is substantially smaller than said radius (19) defining said power transmission surface (18). A power transmission toothed belt drive comprising: a power transmission toothed belt (10) as claimed in any of claims 1 to 3; and a pulley (25) having a plurality of circumferential radially outwardly opening grooves (26), each groove (26) being symmetrical about a radial centerline (27), each half of each groove (26) having a convex outer surface (28) defined by an arc of a circle extending inwardly from a face line (29) defined by the radially outer distal face of a land (30) between successive pulley grooves (26), a concave sidewall surface (31) extending inwardly from said outer surface (28) and being defined by a circular arc having a radius (32) centered at a point (33) spaced from said centerline (27) approximately one-half the pitch of the grooves (26), and a concave inner surface (36). A drive as claimed in claim 4, wherein said point (33) at which the sidewall arc radius (32) is centered is coincident with said point (20) at which the power-transmitting surface (18) of the belt (10) is centered when the belt tooth (14) is fully meshed with the pulley (25) in the groove (26). A drive as claimed in claim 4 or 5, wherein said sidewall surface (31) and said inner surface (36) of the pulley groove (26) define circular arcs having radii centered substantially at the same points at which said belt power transmission surface (18) and said tip surface (17), respectively, are centered when the belt tooth (14) is fully meshed with said pulley groove (26) whereby a constant clearance is provided between said belt tooth power transmission and tip surfaces (18,17) and the confronting pulley groove sidewall and inner surfaces (31, 36) respectively. A drive as claimed in any of claims 4 to 6, wherein said sidewall surface (31) extends inwardly from a first junction with an outer end of a root surface (28), and said inner surface (36) extends inwardly from a second junction with an outer end of said sidewall surface (31), a line extending through said first and second junctions intersecting said centerline (27) at an angle in the range of approximately 9° to 18°.

Inventors: KAWAI, KAZUMI, SHAURA, TSUNEO, TANAKA, HIROYUJI, UTO, KUNIHARA, YASUHUKU, MOTONOBU
Applicants: MITSUBOSHI BELTING LTD.
Application year: 1988
Main classification: F16G1
IPC codes: F16H7, F16G1