FLEXIBLE BELT AND RELATIVE DRIVING SYSTEM

Abstract: An elastically extensible flexible (1) belt which comprises an annular body of elastomeric (2) material embedding a plurality of elongated elements (4) arranged along a surface corresponding to the position of the neutral axis. The belt is characterized in that each elongated element (4), at 1/10 of its ultimate tensile stress, has an elongation value able to balance a shrinking value of the innermost surface of the belt, ranging between two limit values ε₁, ε₂ corresponding to the bending of the belt according to two pre-established curvatures. The first curvature is represented by a circumference whose radius r₁ is equal to 60% of the radius R of the circumferential development of the annular body in correspondence of the elongated elements and the second curvature is represented by a circumference whose radius r₂ corresponds to 35% of the radius R of the circumferential development of the annular body.

Description: The present invention concerns an elastic extensible belt according to the premable of claim 1. Such a belt is e.g. known from US-A-3 900 680 or GB-A-1 123 225. As known, the belts of elastomeric material intended to be assembled around at least two pulleys and to exchange, on appropriate surfaces, friction forces able to transmit motion, comprise substantially a ring-shaped body which embeds in a same plane a plurality of tension-resistant elongated elements whose main feature is their inextensibility. The belt body is internally and externally limited by a pair of base surfaces and, laterally, by a pair of opposite sides. Belts of the above indicated type can have a V-shaped section and can transmit the friction forces by their sides, or a flat section and transmit the friction forces by at least one of their bases, or can be of the Poly-V type, identified in cross section by a base surface comprising several V-shaped longitudinal grooves arranged side-by-side. These belts find application in many fields and in particular they are mainly used for power drives in which one of the pulleys can have very small take-up diameters, in some cases of 70 mm, and often even smaller, ranging between 40 and 50 mm. Moreover,the present technical trend is that of using the above indicated belts on pulleys having diameters of 15 or 16 mm. Unfortunately, the application of the belt on a pulley having a strong curvature may lead to a reduction in the belt life. In fact, considering for instance a Poly-V belt mounted on the corresponding pulley, it can be noted - as known to the technicians of this field - that the stresses are distributed on the two parts of the annular body, i.e. above and below the surface containing the elongated elements; more precisely, the belt portion above these elements is subjected to tension, whilst that below them is subjected to compression. At said surface, owing to the inextensibility of the reinforcing elements, there are no deformations and it can be defined as a "neutral axis", or "pitch surface" of the belt. Obviously, the compression of the considered belt portion is the greater the more relevant the pulley curvature is, with a consequent high deformation of the elastomeric material which may give rise to substantially undulated configurations concerning areas corresponding to the joining between the longitudinal elements and the annular elastomeric body. It was noted that such deformations may originate sooner or later - but anyhow in times not admitted for the services required in many industrial applications - a detachment of the elongated elements forming the elastomeric body, with a consequently reduced life of the belt. The drawbacks ascertained in the Poly-V belts are common to other types of V-shaped or flat belts and can be ascribed also here to the compression of the belt portion underlying the "pitch surface" containing the longitudinal elements and to a "collapse" of the elastomeric material, compelled to deform and to find space to said deformation where this is possible, inter alia towards the elongated elements, with the already known consequences. The present invention aims to provide a flexible belt of elastomeric material which is intended to transmit friction forces able to generate motion and the relative driving system comprising said belt and at least two pulleys, in which the above mentioned disadvantages are eliminated. Accordingly, the object of the present invention is an elastic extensible belt as defined in claim 1. The present invention will be better understood from the following detailed description given only by way of non-limiting example and made with reference to the figures of the attached sheets of drawings, in which : FIGURE 1 - shows in section a multi-groove belt according to the invention, FIGURE 2 - shows a qualitative diagram reporting the tensile stresses and the elastic elongation of a continuous elongated element of the belt of Figure 1, FIGURE 3 - shows schematically a driving system comprising a V-shaped belt mounted between two pulleys, one of which of the expanding type, FIGURE 4 - shows in section the V-shaped belt of FIG.3, FIGURES 5 and 6 - show respectively in section and in side view a flat belt which forms no part of the invention and the relative driving system. With reference to FIG.1, 1 is a "Poly-v" belt formed by a flat portion and, in a position opposite to its back 2 , by a plurality of longitudinal V-shaped grooves 3 . Belt 1 comprises a body of elastomeric material and a plurality of continuous elongated elements 4 in the form of cords or the like, arranged side-by-side, on a cylindrical surface of the belt, at a distance "h" from the surface defined by points "V" of the grooves. The belt body is closed as a ring and the pitch circumferential layout of the belt along cords 4 is obtained by a radius of value R. The main feature of belt 1 is its elastic extensibility, which is due to the geometrical structure of the belt itself. Substantially, for a given geometry of the belt, defined by parameters "h" and "R", the inventive principle lies on the fact of inserting in the belt body, on its cylindrical surface, a plurality of continuous elongated elements 4 having a pre-established characteristic able to balance a convenient part of the shrinkage of the belt portion compressed by flexion on a curved surface. The balance of shrinkage due to compression is achieved by the elongated elements 4, whose elongation value is selected in accordance with two limit shrinkage conditions, obtained by bending the belt along two curvatures represented by two theoretical circumferences of pre-established radius. More precisely, a belt having given geometrical characteristics "R" and "h" is theoretically bent only by flexion on two circumferences, the first having a radius r₁ equal to 0.6 R and the second having a radius r₂ equal to 0.35 R, determining for said configurations the percent shrinkages ε₁ and ε₂ of the innermost base surface of the belt, namely that represented by the points of the grooves. When values ε₁ and ε₂ have been determined, the elongated elements 4 are inserted in the belt; their elongation after vulcanization, at 1/10 of their ultimate tensile stress, must have a percent value able to balance a corresponding shrinkage value ranging between the limit values ε₁ and ε₂. For the sake of clearness, reference is now made to the stresses/deformations qualitative diagram of FIG.2 concerning the elongated element 4, where the abscissae refer to the elongation and the ordinates to the tensile stress. The two dashed straight lines parallel to the axis of the ordinates correspond to the limit shrinkages ε₁, ε₂ (changed in sign) referred to the bending of the belt due to flexion only along the two circumferences having a radius r₁ = 0.6 R and a radius r₂ = 0.35 R, respectively. The elongated element having pre-established extensibility characteristics is chosen as follows. Considering a cord, whose stress/deformation curve after vulcanization is represented by a curve "a" and indicating with Fa its ultimate tensile stress, it can be seen from FIG.2 that, at 1/10 Fa, elongation ε a of the cord represented by said curve "a" is not comprised between the limit values ε₁ and ε₂; consequently cord "a" is not chosen as elongated element 4 to be inserted in the body of the belt shown in FIG.1. Considering now a cord whose stress/deformation curve is represented by curve "b", it can be seen from FIG. 2 that, at 1/10 of its ultimate tensile stress Fb, the cord represented by "b" has an elongation ε b comprised between the two values ε₁ and ε₂; therefore it can be inserted, in side by-side arrangement with analogous cords, in the body of the Poly-V belt of FIG.1. Substantially, as a function of the belt geometry, the choice of elongated elements 4 in the form of cords in accordance with curve "b" of FIG.2 enables the belt to be mounted between two pulleys at an elastic pretension corresponding to 1/10 of the ultimate tensile stress of each element 4 multiplied by the number of elements, so as to balance, by means of elongation ε b of the belt, shrinkage values comprised between ε₁ and ε₂. Parameter can be determined at once, as briefly explained hereinbelow. Indicate with letter "R" the radius referred to the belt pitch line L at the neutral axis comprising the elongated elements and with letter "h" the distance from said axis to the radially innermost surface of the belt, which in FIG.1 is represented by the points of the grooves. In this situation, for a generic arc between two given points of the belt, subtended by an angle ϑ, it will be : ϑ x ·R = belt layout at the neutral axis ϑ x ·(R-h) = belt layout at distance "h" Assuming to bend the belt along an arc of radius r, smaller than R, without varying the two points of the belt limiting the arcs, it will be : ϑ ' / x·r = belt layout at the neutral axis ϑ' x ·(r-h) = belt layout at distance "h" From the definition of neutral axis, i.e. the locus of the points where the fibers of the body subjected to flexion do not suffer elongation or shrinkage, it will be : ϑ x ' = ϑ x ·R/r The shrinkage at a distance "h" from the neutral axis, originated by the bending of the belt by flexion on a circumference of radius r is given by the difference of the layouts corresponding to R and r referred to the pitch layout, namely taking into account the preceding expressions : ε = (ϑ x (R-h) - ϑ x ')·(r-h) / [ϑ x ·(R-h)] so that ε = h·((R/r)-1)/(R-h) If the final expression of ε, r is replaced by the values of r₁ and r₂ corresponding to 0.6 R and 0.35 R, the following minimum and maximum shrinkage values ε₁ and ε₂ reported in the diagram of FIG.2, are obtained : ε₁ = 0.667 h / (R-h) ε₂ = 1.86 h / (R-h) Consequently, having already available a certain geometry of the belt, defined by "R" and "h", and having found values ε₁ and ε₂, it is possible to chose the elongated element 4 whose elongation, at 1/10 of its ultimate tensile stress, balances a shrinkage value ranging between ε₁ and ε₂; at last, by multiplying the number of elements arranged side-by-side by 1/10 of the ultimate tensile stress of each of them, it is possible to evaluate the nominal value of the tension of the belt in use, to which corresponds an elastic elongation able to balance that particular shrinkage value ranging between ε₁ and ε₂. Some particular embodiments of a belt according to the invention will now be described. 1st embodiment Poly-V belt, 1200 j 6 Pitch layout L = 1178 mm Radius of the pitch layout , R = 1178/2π = 187.5 mm Number of grooves = 6 Groove profile = j according to Standards Groove height = 2 mm Distance h = 3 mm Minimum percent shrinkage value ε₁ = 0.667 . h/(R-h). 100 = 1.08% Maximum percent shrinkage value ε₂ = 1.86 . h/(R-h). 100 = 3.02% The elongated element whose elongation at 1/10 of its ultimate tensile stress balances the shrinkage ranging between ε₁ and ε₂ is chosen as a function of the belt parameters R and h. The data regarding the elongated elements are the following : - continuous elongated element : - cord formed of two strands each comprising 940 monofilaments (940 X 2) - 4,8z twists per cm for each strand and 4,8s twists per cm for the two strands together. Cord diameter = 0.55 mm - Ultimate tensile stress = 145 N (Newton) - % elongation of the element at 1/10 of the above value = 3.5% - Insertion formed by 17 coils of cord situated on the belt surface at a distance "h" from the innermost surface - Ultimate tensile stress of the belt = 4000 N ( 2000 on each branch) - % elongation at 1/10 of the above value = 2.27% 2nd Embodiment Poly-V belt - Pitch layout L=853 mm - Radius of pitch layout R = L/2π = 135.7 mm - Number of grooves = 5 - Groove height = 2.7 - Groove profile = K according to Stand.s - Distance h = 4.8 mm - Minimum % shrinkage value ε₁ = 2.44% - Maximum % shrinkage value ε₂ = 6.82% Data regarding the elongated element : - continuous elongated element Nylon 66 1400 X 3 type cord, 3,1z 3,1s twists per cm - Cord diameter = 1.1 mm - Ultimate tensile stress of the element = 320 N - % elongation at 1/10 of the ultimate tensile stress = 4% - Belt insertion = 17 coils - Ultimate tensile stress of the belt = 4300 N on each branch - % elongation at 1/10 of the ultimate tensile stress of the belt = 3.2% 3rd embodiment V-shaped belt - Pitch layout L = 1250 mm - Pitch radius R = 199 mm - Trapezium greater side in cross section = 9.5 mm - Belt total height = 5.5 mm - Angle between sides = 40° - Distance h = 3.8 mm - Minimum % shrinkage value ε₁ = 1.3% - Maximum % shrinkage value ε₂ = 3.62% Data regarding the elongated element: - continuous elongated element 940 X 2 type cord, 4,8z 4,8s twists per cm - Cord diameter = 0.55 mm - Ultimate tensile stress of the element = 145 N - % elongation at 1/10 of the ultimate tensile stress = 3.7% - Insertion formed by 10 coils - Ultimate tensile stress of the belt = 2460 N (1230 N on each branch) - % elongation at 1/10 of the ultimate tensile stress of the belt = 2.56% The invention is able to achieve all of the above indicated purposes. To demonstrate that said purposes were obtained, the tests carried out on the Poly-V belt of the first embodiment will be described herebelow. The test had the aim to evaluate the life of a belt according to the invention after a high number of bendings on pulleys having small radii. The equipment used was the following : - Driving pulley, diameter = 80 mm - Driving pulley r.p.m. = 3500 - Driven pulley, diameter = 30 mm - Driven pulley r.p.m. = 9300 The belt of the first embodiment was mounted between two pulleys situated at such a fixed center distance as to originate an initial assembling elongation of 2%. The test was interrupted after 700 work hours and the examination of the belt did not show any detachment between the rubber compound and the cords embedded in the belt body. To better evaluate the validity of the invention, a further test was performed on the belt of the first embodiment; in this case the equipment was changed to simulate a condition of employment concerning a driving system for washing machines. The equipment used was the following : - Driving pulley, diameter = 18 mm - Driven pulley diameter = 336 mm The center distance was so selected as to mount the belt with an elongation of approximately 2%. The belt was caused to rotate at low and high speed cycles,both in clockwise and counterclockwise direction so as to simulate the washing and centrifugation phases of a washing machine. The test was interrupted after 2000 working cycles, corresponding to the service life of a household apparatus, without ascertaining any detachment between the cords and the rubber compound embedding them. The optimum results obtained can be explained only by hypothesis, owing to the multiplicity of the phenomena involved. In fact, as regards the first test performed on the belt of the first embodiment, it must be noted that the shrinking values ε ₁, ε ₂ resulting from the compression of the innermost surface of the belt bent on the two pulleys of 80 mm and 30 mm, are the following : ε₁ = 6% ε₂ = 18.7% Further, it must be noted that the belt was mounted between the two pulleys with a preliminary tension corresponding to an elongation of approximately 2%; in other words the elongation characteristics of the belt are such that it can balance about 1/3 of the shrinkage originated by its bending on the greatest pulley, but can compensate only in a minimum part the shrinkage due to its bending on the smallest pulley. However, in spite of the above, the first test showed surprisingly that the belt according to the first embodiment remained integer even if subjected to the stresses of a cyclic bending on a pulley having a diameter of 30 mm. In this connection the Applicants, as an attempt to explain the unexpected results obtained, make the following hypothesis. The belt under test comprises long portions to be taken up on the pulley having the greatest diameter and very reduced portions being taken up on the smallest pulley. The behaviour of the belt, in particular the phenomena occurring in the material constituting it, would be significantly influenced by the extent of the take up arc on the pulley of greater diameter, so that the fact of having eliminated the most part of the drawbacks,related to shrinkage, which take place on said pulley is by itself an useful contribution to the prolongation of the belt life even if, apparently, there still are phenomena of unbalanced shrinkage by compression in the smallest pulley. Inter alia, it can be thought that the belt life depends on the event originated by its winding on the two pulleys but that - owing to the difference of the concerned portions - what happens on the smallest pulley is not sufficient to prejudice the prolongation of the belt life consequent to the elimination of the most part of the drawbacks noted on the greatest pulley. This hypothesis is confirmed by the results of the second test carried out on the same belt mounted with an elongation of approximately 2% on two pulleys, one of which having a great diameter,corresponding to 336 mm, and the other having an extremely small diameter, corresponding to 18 mm, with a shrinkage value in the innermost surface of about 0.2% for the greatest pulley and of about 32% for the smallest pulley. As it can be noted, in this test situation the greatest pulley has a relevant circumferential layout, whilst the smallest pulley, owing to its dimensions, is very critical for the shrinkage originated by compression. However, a total balance of the shrinkage due to compression, on the greatest pulley and for long belt portions, seems sufficient by itself to prolonge the belt life so that the latter may last as long as the equipment without any prejudice. In other words, it can be said that the small belt portion bent time by time on the smallest pulley is subjected to high shrinkage, but this inconvenience is so localized in a little space and for a short time that it cannot affect the belt in its whole, at least for the time intervals which have been considered. As it can be noted, the result of the tests tends to confirm the validity of the belt features, with elongation values greater than 1% and in any case comprised in the cited range ε₁ and ε₂. As regards elongation values out of range ε₁-ε₂, at 1/10 of the ultimate tensile stress, at values smaller than ε₁ the belt would be scarcely extensible; therefore the elongated elements therein contained would not allow elongations able to balance the shrinkage by compression, and, at values greater than ε₂ the belt would be too elastic, with the risk of losing the assembly tension pre-established for a given operation. The present invention can be applied to belts having a section different from that of the above described Poly-V belt; inter alia, as shown in FIG.3, it can be applied to a belt 5 of trapezoidal section for a stepless speed change gear in which, by way of example, the greatest pulley 6 has a fixed trapezoidal groove and the smallest pulley 7 a variable trapezoidal groove. Also by way of example the invention can be applied, according to the same principles, to a flat belt provided with continuous elongated elements able to confer to the belt an elastic extensibility comprised in the desired range. For instance, such belt 8 might be mounted (FIG.5) between two pulleys 9 , 10 , whose fixed center distance is such as to determine the elongation and therefore the preliminary elastic tension of the belt itself. The flat belt might have a cross rectangular section or any other section, inter alia with a curvilinear shape on one of the two base surfaces or any other shape provided that - whichever solution is adopted - at least one of the two base surfaces is able to transmit, by friction, forces able to generate motion with at least a corresponding outer surface of a pulley . The invention is described with reference to the characteristic of extensibility of the belt. The elongation of the elongated elements gives rise to the elastic extensibility of the belt; however, it is to be taken into account that the stress/deformation curve of each element is drawn at room temperature and that, in the practice, when the element is inserted in the belt and the latter is vulcanized, a modification of the stress/deformation curve might be ascertained when specific materials are used to form the cords. In the practice, at the high curing temperatures the cords inserted in the elastomeric mass, under equal tension forces may show variations in their elongation characteristics. Further, also when the cords are treated with the adhesive agent, their extensibility characteristics may suffer modifications. These variations, depending on the treatment to which the cords and the belt are subjected, may be conveniently exploited to obtain a stress/deformation curve of the whole belt which is the most appropriate to balance the shrinkage by compression to which the belt being taken up on the pulley is subjected in use. Moreover, it is possible to build up belts in which the cords are different from those described in the above indicated embodiments. For instance, the Poly-V belt of the first embodiment might comprise elongated elements other than cords, as for example monofilaments or cords of a material different from nylon, provided that in the various possible solutions said elements - according to their dimensional characteristics and to the treatment suffered after their incorporation in the belt - are able to originate an ultimate tensile stress of 4000 N and, at 1/10 of said ultimate tensile stress, an elongation of the belt ranging from 1.08% to 3.02%. The same considerations concerning the different materials to be used for the elongated elements may be made also in respect of the belts described in the other above cited embodiments. Inter alia, further embodiments might be represented by Poly-V or V-shaped or flat belts comprising elongated elements made of rayon or polyester cords made up, as to the number of twists and the methods of treatment, in such a way to originate elongations greater than 1% and, inter alia, elongations ranging between 1% and 15%. Moreover, the Poly-V belt according to the invention might be used in a driving system in which one of the pulleys comprises an outer surface grooved like the belt and/the other pulley comprises a cylindrical smooth outer surface. In all the above indicated embodiments the belts might comprise layers of fabric, in particular covering fabric, each prepared and built up with such an extensibility as not to hinder the elastic elongation of the belt determined by the elongated elements present in the elastomeric compound. In all of these solutions, the fabrics present in the belt do not effect the belt ultimate tensile stress which is chiefly determined by the elongated elements embedded in the ring-shaped body on a surface corresponding to the pitch surface. Although some particular embodiments of the present invention have been described and illustrated, it is understood that they might comprise any other variation evident to a technician of this field; for instance the belt might have a cross section different from those indicated above, as for example a circular section, to be mounted between two pulleys having a V-shaped race.

Claims: An elastic extensible belt (1) which comprises an annular body of an elastomeric material and at least one elastically extensible elongated element which comprises a plurality of coils (4) embedded therein placed along a surface substantially corresponding to the position of the neutral axis of the belt at a predetermined distance h from its radially innermost surface and having a predetermined radius R referred to said neutral axis, characterized by the fact that the number of coils is in the range between 10 and 17 and that said elongated elements have a stress deformation behaviour in the finished belt such that, at 1/10 of its ultimate tensile stress, an elongation value ε of said belt is obtained which is included in the range of from ε₁ equal to 0, 667 h/(R-h) to ε₂ equal to 1,860 h/(R-h), wherein R and h have the above indicated meanings. An elastically extensible belt as in claim 1 characterized in that the elongated elements are cords. An elastically extensible belt as in claim 1 or 2 characterized in that the elongated elements are nylon cords. A belt as in claim 3, characterized in that each cord is of 940 x 2 type, 4.8 z, 4.8 s twists per cm type. A belt as in claim 3, characterized in that each cord is of the 1400 x 3 nylon 66, 3.1z 3.1s twists per cm type. An elastically extensible belt as in claim 1 characterized in that said belt body has a trapezoidal (5) section with sides intended to transmit forces by friction on the corresponding surfaces of at least two pulleys (6, 7). An elastically extensible celt as in claim 6, characterized in that it comprises a plurality of elongated elements in the form of nylon cords of the 940 x 2, 4.8 z, 4.8 s twists per cm type, forming 10 coils. An elastically extensible belt as in claim 6, characterized in that it comprises a pitch length of 1250 mm, a surface of the greater base of 9.5 mm, a height of 5.5 mm, an angle between the sides of 40°, and a distance between the surface of the smaller base and the plane containing the elongated elements corresponding to 3.8 mm. An elastically extensible belt as in claim 8, characterized in that it has an ultimate tensile stress of 2460 N (Newton) and, at a stress of 246 N, an elongation of 2.56%. An elastically extensible belt as in claim 1, characterized in that it comprises a ring-shaped body whose inner base surface is formed by a plurality of grooves (3) intended to transmit forces by friction with the grooved surface of a pulley. An elastically extensible belt as in claim 10, characterized in that it comprises a plurality of elongated elements in the form of nylon cords of the 940 x 2, 4.8 z, 4.8 s twists per cm type, forming 17 coils. An elastically extensible belt as in claim 10, characterized in that it comprises a pitch length of 1178 mm. 6 grooves and a distance of the grooves' ends from the plane containing the elongated elements corresponding to 3 mm. An elastically extensible belt as in claim 12, characterized in that it has an ultimate tensile stress of 4000 N (Newton) and, at a stress of 400 N, an elongation of 2.27%. An elastically extensible belt as in claim 1, characterized in that it comprises a ring-shaped body of flat section (8), with at least one of the base surfaces intended to come into contact with a cylindrical surface in a pulley. An elastically extensible belt as in claim 1, characterized in that the elongation values range between 1% and 15%. A driving system comprising an elastically extensible belt (5) as in claim 1 and at least two pulleys (6, 7), characterized in that the belt is mounted between the two pulleys in state of elastic pretension. A driving system as in claim 16, characterized in that it comprises a belt of V-shaped (5) section which can be elastically extended between two trapezoidal pulleys (6, 7), one of said pulleys (7) having a trapezoidal race of variable depth. A driving system as in claim 16, characterized in that the belt body comprises a grooved base surface and at least one of the two pulleys comprises a surface grooved like the belt. A driving system as in claim 16, characterized in that the belt, in cross section, has a flat shape (8) and the pulleys comprise cylindrical outer surfaces (9, 10).

Inventors: ROBECCHI, EDOARDO
Applicants: PIRELLI TRASMISSIONI INDUSTRIALI S.P.A.
Application year: 1989
Main classification: F16G1
IPC codes: F16G5, F16H7, F16G1