Classifications

• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
  • F16G1/00—Driving-belts
  • F16G1/06—Driving-belts made of rubber
  • F16G1/08—Driving-belts made of rubber with reinforcement bonded by the rubber
  • F16G1/10—Driving-belts made of rubber with reinforcement bonded by the rubber with textile reinforcement
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
  • F16G1/00—Driving-belts
  • F16G1/06—Driving-belts made of rubber
  • F16G1/08—Driving-belts made of rubber with reinforcement bonded by the rubber
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
  • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
  • B65G13/00—Roller-ways
  • B65G13/02—Roller-ways having driven rollers
  • B65G13/06—Roller driving means
  • B65G13/07—Roller driving means having endless driving elements
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
  • B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
  • B65G39/00—Rollers, e.g. drive rollers, or arrangements thereof incorporated in roller-ways or other types of mechanical conveyors 
  • B65G39/02—Adaptations of individual rollers and supports therefor
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
  • F16G1/00—Driving-belts
  • F16G1/28—Driving-belts with a contact surface of special shape, e.g. toothed
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
  • F16G5/00—V-belts, i.e. belts of tapered cross-section
  • F16G5/04—V-belts, i.e. belts of tapered cross-section made of rubber
  • F16G5/06—V-belts, i.e. belts of tapered cross-section made of rubber with reinforcement bonded by the rubber
  • F16G5/08—V-belts, i.e. belts of tapered cross-section made of rubber with reinforcement bonded by the rubber with textile reinforcement
• • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
  • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
  • F16G—BELTS, CABLES, OR ROPES, PREDOMINANTLY USED FOR DRIVING PURPOSES; CHAINS; FITTINGS PREDOMINANTLY USED THEREFOR
  • F16G5/00—V-belts, i.e. belts of tapered cross-section
  • F16G5/20—V-belts, i.e. belts of tapered cross-section with a contact surface of special shape, e.g. toothed

Definitions

• TITLE TRANSMISSION BELT FOR CONCAVE GROOVED ROLLER CONVEYOR AND ASSOCIATED CONVEYOR
• the present invention relates to a transmission belt for a roller conveyor with concave grooves.
• the invention also relates to a roller conveyor with concave grooves provided with such belts.
• Roller conveyors are widely used in the logistics and flow of goods sector for the routing and sorting of objects of all kinds, and in particular packages.
• these conveyors comprise a plurality of rollers driven in rotation by a motor element by means of transmission elements.
• rollers There are different types of rollers and just as many transmission elements, each meeting specific criteria.
• roller conveyors with so-called concave grooves, most often round, are very widespread. They are represented for example in Figures 1 to 4.
• Figures 1 and 2 show classic configurations of roller conveyors with round grooves, that is to say a straight conveyor 1 a as shown in Figure 1 and a curved part of a conveyor 1 b as shown in Figure 2.
• each of the rollers 10 of the conveyor 1a, 1b comprises at least, at one of its longitudinal ends, grooves 12 whose groove bottom 14 is round.
• Belts 2 called round, that is to say whose section forms a disc, are engaged in these grooves 12 to allow the driving of the rollers 10.
• These belts typically made of polyurethane, have the advantage of being inexpensive and easy to mount in gorges.
• a motor roller drives the adjacent rollers 10, called slave rollers, in rotation via the belts 2.
• This motor roller is similar to the slave rollers with the difference that it is equipped with a motor allowing it to turn on itself.
• a motor roller then rotates a first slave roller, via a first belt 2, the first roller which can itself rotate a second slave roller via a second belt, etc.
• the belt 2 must rest on the bottom 14 of the groove 12 with the largest possible contact surface, while avoiding as much as possible contact with the side 16 of the throat 12. Indeed, the existence of contact with the side of the throat involves several harmful consequences.
• the belt is then subjected to two very different speeds because there are then two contact surfaces between the belt and the groove which are located at relatively different distances from the axis of rotation of the roller. Such a situation accentuates the deformation of the belt and therefore its wear. Second, it makes it easier to turn the belt.
• Document US-A1 -2009/107809 describes a typical example of a roller conveyor.
• Figure 3 shows a first type of roller 10, made of steel, which has grooves 12 formed directly in the roller 10 at one of its ends. These grooves can for example be stamped into the roller.
• a zone Z1 for the passage of packages which extends over the entire length of the roller 10, therefore encompassing a transmission zone Z2 where the grooves 12 and the round belts 2 are located.
• this configuration makes it possible to have the widest possible passage zone Z1, this can prove problematic if a package comes into contact with one of the belts 2. Indeed, in the event of an impact between the belt 2 and the package, the belt 2 can disengage from the groove 12 of the roller 10, which is likely to cause the conveyor to stop.
• the diameter of the section of the round belt 2 is chosen to be strictly less than the depth of the groove 12. For example, for a groove of 10 mm (millimeter) of depth, the diameter of the belt section is 6 mm.
• rollers with a drive head 18 mounted at one end of the roller 10, as illustrated in Figure 4.
• the drive head 18, typically made of plastic material, offers the advantage of having a transmission zone Z2, closer to the end of the roller 10 and the side profile of the conveyor 1a, 1b. It is thus possible to separate the zone Z2 of the belts and the zone Z1 of passage of the packages to be transported on the rollers, thus limiting, or even preventing, the packages from coming into contact with the belts 2.
• the rollers in Figure 4 will be able to drive packages smaller than the rollers in Figure 3.
• an objective of the invention is to propose a transmission belt for a roller conveyor with concave grooves not having, at least, one of the aforementioned drawbacks.
• Another objective of the invention is to propose a transmission belt for a roller conveyor with concave grooves offering improved performance on the torque transmissible between two rollers.
• Another objective of the invention is to propose a transmission belt for a roller conveyor with concave grooves which also limits the risk of the belt turning over, particularly in a curved part of a conveyor.
• a transmission belt is therefore proposed for a roller conveyor having concave grooves made of steel or plastic, the belt comprising:
• an elastomer-based body comprising a dorsal portion and a ventral portion formed of a single tooth, an external surface of which has a convex shape which is configured to cooperate with a concave groove of a roller; - a set of traction cables embedded in the body between the dorsal portion and the ventral portion of the body;
• a coating arranged at the level of the external surface of the teeth defining, with the shape of the external surface of the teeth, a non-zero coefficient of friction and less than or equal to 0.8 with the concave groove of a roller.
• the contact surface between the belt and the bottom of the roller groove is high thanks to the convex shape of the belt teeth which adapts to the concave shape of the groove.
• the combination of this convex shape of the teeth with the coating arranged at the level of the external surface of the teeth makes it possible to define the coefficient of friction of the belt in the groove at a controlled value. With a controlled coefficient of friction and the presence of cables improving the traction modulus of the belt, the transmissible torque can be controlled. Furthermore, this limits the risk of the belt rolling over when it rises to the side of the groove, particularly in a curved part of a conveyor.
• the invention also relates to a conveyor comprising a plurality of rollers with concave grooves made of steel or plastic, in which the rollers are connected together in pairs by a belt as described in the above, so that the covering of the belt is in contact with the concave grooves of the rollers.
• the belt is installed between the rollers with an installation tension of between 60 N/strand and 100 N/strand.
• Figure 1 represents a schematic view of a straight roller conveyor according to the prior art
• Figure 2 represents a schematic view of a curved roller conveyor according to the prior art
• Figure 3 represents a schematic view in longitudinal section of a roller with concave grooves with a conventional transmission belt according to the prior art
• Figure 4 represents a schematic view in longitudinal section of another form of roller with concave grooves with a conventional transmission belt according to the prior art
• Figure 5 represents a schematic cross-sectional view of the transmission belt for a roller conveyor with concave grooves according to the invention
• Figure 6 represents a schematic perspective and partial sectional view of the belt of Figure 5
• Figure 7 represents a schematic cross-sectional view of the belt according to the invention, illustrating in particular different penetration rates of the coating at the external surface of the teeth of the body of the belt,
• Figure 8 represents a schematic cross-sectional view of an embodiment of the belt according to the invention, defining in particular the dimensions of the belt,
• Figure 9 represents a photographic cross-sectional view of the belt of Figure 8.
• Figure 10 represents a schematic view in longitudinal section of a mandrel, around which belt materials are placed, and of a knitted sleeve as used during the manufacture of a belt according to the example of realization,
• Figure 11 represents a schematic view in longitudinal section of the knitting sleeve placed on the belt materials, themselves arranged on the mandrel of Figure 10,
• Figure 12 represents a schematic view in longitudinal section of the object of Figure 11 introduced into a mold
• Figure 13 is a schematic view of an experimental installation used to measure the coefficient of friction of a belt with a pulley
• Figure 14 is a graph comparing the evolution of sliding as a function of the torque transmitted for a conventional belt known from the prior art and the belt of the exemplary embodiment
• Figure 15 represents a schematic view in longitudinal section of the belt according to the invention, mounted on a roller with concave grooves as shown in Figure 3, and
• Figure 16 represents a schematic view in longitudinal section of the belt according to the invention, mounted on a roller with concave grooves as shown in Figure 4.
• Figure 5 and Figure 6 respectively show a sectional view and a perspective and partial sectional view of a transmission belt 100 for conveyor 1 a, 1 b to rollers 10 with concave grooves 12.
• concave grooves is meant any groove having a section of generally concave shape, for example a round groove (i.e. having an arcuate throat base, or a groove having an elliptical or even ovoid bottom).
• the belt 100 comprises an elastomer-based body 102, a set of traction cables 110 and a covering 112.
• the elastomer-based body 102 comprises a dorsal portion 104.
• the elastomer-based body 102 also comprises a ventral portion 106, formed of a single set of teeth, a convex external surface of which is configured to cooperate with a concave groove 12 of the conveyor 1 a, 1 b with rollers 10.
• external, convex surface of the teeth can for example have the shape of an arc of a circle, an ellipse or an ovoid, in particular depending on the shape of the concavity forming the groove.
• the external surface of the teeth of the ventral portion 106 forms an arc of a circle, when the groove of the roller is round.
• this convex external surface contributes to defining the coefficient of friction (COF) between the belt 100 and the groove 12 of the roller 10 in which the belt 100 is intended to be installed.
• COF coefficient of friction
• the higher this coefficient of friction the more torque can be transmitted.
• more this coefficient of friction is high and the more the risk of overturning of the belt 100 increases, particularly in a curved part of a conveyor.
• the lower this coefficient of friction the less torque can be transmitted, thus limiting the torque transmissible from one roller to another.
• the belt 100 also includes a set of traction cables 110.
• the cables 110 are embedded in the body 102 between the dorsal portion 104 and the ventral portion 106 of the body 102.
• the cables 110 make it possible to increase the traction modulus of the belt 100. They therefore extend along the length of the belt and are arranged next to each other over the width of the body 102.
• a cable 110 of the set of cables can in particular be made of a material chosen from polyamide (PA) or polyester. They therefore make it possible, for the application considered, to authorize greater torque transmission while maintaining a very limited elongation of the belt 100.
• each cord 110 The constitution of each cord 110, the number of cords 110 arranged in the width of the belt 100 and the choice of the material constituting them is variable and depends on the traction module sought for the belt 100 to ensure torque transmission in limiting the elongation of the belt 100.
• the presence of such cables 110 has the general effect of allowing higher torque transmission, in particular compared to known round belts (generally made of polyurethane) which do not have cables for this. type of conveying application.
• the belt 100 also includes a coating 112 arranged at the external surface of the teeth.
• This coating 112 contributes, with the shape of the teeth, to define the coefficient of friction (COF) between the belt 100 and the steel roller 10 or the plastic drive head 18 of the roller 10.
• the covering 112 can typically be chosen from a knitted fabric, a fabric, a non-woven fabric or even a set of fibers.
• the covering 112 can be made of a material typically chosen from a polyamide, a polyester, cellulosic fibers, in particular cotton, a mixture of cellulosic fibers and polyurethane, in particular a mixture of cotton and polyurethane or a combination thereof.
• the covering 112 may be a polyamide knit, a cotton fabric mixed with polyurethane.
• part of the coating 112 is embedded in the teeth.
• the coefficient of friction is linked to different parameters, such as the type of covering 112, for example knitted or fabric, the nature of its material, for example polyamide, its weight or even its penetration rate T in the ventral portion 106 at the level of the external surface of the teeth. This also depends on the nature of the elastomer and its properties.
• the coefficient of friction of an elastomer with a steel or a plastic is particularly high, typically greater than 1.5.
• the parameters mentioned above to characterize the coating 112 make it possible, depending on the choices made, to reduce the coefficient of friction (compared to this same surface without coating 112) and, therefore, to control it. Given the number of parameters, there are multiple ways to define the friction coefficient. From a practical point of view, we can first choose the type of covering 112 (knitted fabric, fabric, etc.) then the material composing it (polyamide, polyester, etc.), its weight (the higher the weight, the more the coating 112 covers the external surface and vice versa) and finally its rate of penetration into the teeth.
• This penetration rate T is defined as the fraction of the total thickness of the coating 112 which is embedded in the teeth of the elastomer-based body 102. Locally, this penetration rate T can vary from one location to another on the belt 100, so we considers an average penetration rate T over the entire belt 100. In practice, the penetration rate T will be non-zero and strictly less than 100%, its exact value depending on the other parameters. The choice of these parameters will also depend on the nature of the elastomer used.
• Figure 7 only aims to illustrate this notion of penetration rate T of the coating 112 into the teeth from the external surface of this toothing, the coating 112 considered here being a knitted fabric.
• T penetration rate
• the coating 112 can be a film of partly crosslinked thermoplastic material, comprising at least 30% polyethylene (PE), this film covering the external surface of the teeth. We understand that the thermoplastic film does not penetrate the teeth.
• PE polyethylene
• the body 102 of the belt 100 is advantageously based on ethylene alpha olefin elastomer, in particular an EPDM or an EPM.
• the thermoplastic film may comprise between 30% and 90% polyethylene, advantageously between 50% and 90% polyethylene, and preferably between 75% and 90% polyethylene.
• the polyethylene of the film co-crosslinks with the elastomer, for example EPDM or EPM, thanks to the presence of peroxide or another crosslinking agent. This promotes adhesion of the film to the elastomer.
• the thermoplastic film may consist, in a non-limiting manner, of a mixture of polyolefins containing a homo or a copolymer comprising ethylene.
• Ethylene copolymers include in particular ethylene/alpha-olefin copolymers, ethylene/unsaturated ester copolymers, ethylene/acrylate/acrylic acid copolymers, ethylene/methacrylic acid copolymers and polyethylene-ethyleneoctene copolymers.
• the thermoplastic film can also be based on low density polyethylene.
• the thermoplastic film can have a thickness of between 10 pm (micrometer) and 500 pm, and more particularly between 50 pm and 200 pm.
• thermoplastic film also comprises particles and/or fibers of graphite, molybdenum disulfide and/or polytetrafluoroethylene (PTFE). This allows, among other things, to influence the coefficient of friction.
• PTFE polytetrafluoroethylene
• the particles can have a particle size of between 15 pm and 200 pm, advantageously between 30 pm and 100 pm and more particularly between 30 pm and 90 pm.
• the belt 100 has a geometry defined as follows and illustrated in Figure 8.
• the body 102 has a thickness, or height, H of 2.3 mm and a width L of 6 mm.
• the single convex toothing of body 102 has the shape of an arc of a circle whose diameter D is 10 mm.
• the set of cables 110 embedded in the body 102 comprises nine cables 110.
• the cables 110 have a diameter d of 0.6 mm and their centers are separated laterally by a pitch p of 0.7 mm.
• the center of each cable 110 is also located at a distance h of 0.7 mm from the dorsal part 104 of the belt 100.
• Each cord 110 is made of polyamide (PA), and in particular polyamide 6-6 (PA66) 940x1x2, that is to say that each wire has a density of 940 dtex (decitex), i.e. 940x10 -7 kg/m (kilogram per meter), and that each wire is first twisted individually before being twisted with the other.
• PA polyamide
• PA66 polyamide 6-6
• Each cable 110 also has a Young's modulus of 400 MPa (MegaPascal), or 400 N/mm 2 (Newton per square millimeter).
• the traction modulus of the belt can thus be calculated and is expressed as being the multiplication of the Young's modulus of the cord 110 with the surface area of the cord 110.
• the belt has nine cables 110 whose diameter d of each cable 110 is 0.6 mm, i.e. a total cross-sectional area of 2.54 mm 2 .
• the traction modulus of the belt is approximately 1000 N.
• the set of cables 110 defines the traction modulus of the belt 100.
• the covering 112 is a jersey type knit made of polyamide (PA), and in particular polyamide 6-6 (PA66), with a tubular finish and a weight of 60 g/m 2 (gram per square meter).
• Figure 9 shows a photograph of a section of the exemplary embodiment of the belt 100.
• the penetration rate T can be estimated qualitatively by measuring the fraction f2 of the knitting located in the teeth relative to the thickness f1 of the knitting.
• the penetration rate T to nine of the knitting in the teeth at the level of its external surface is of the order of 50%.
• the weight chosen in this embodiment is 60 g/m 2 .
• This weight can be at least 20 g/m 2 , preferably at least 30 g/m 2 , and more preferably at least 40 g/m 2 .
• Figures 10 to 12 illustrating steps in manufacturing a belt 100 according to the aforementioned embodiment.
• Figures 10 to 12 show half views in longitudinal section.
• FIG. 10 represents the present case, where the belt materials which form the assembly 200 include the dorsal part 104 (in the raw state) of the body 102 of the belt, the cables 110 and the ventral portion (in the raw state). the raw state) of the body 102 of the belt.
• the assembly 200 is already placed on the mandrel 202.
• the knitting sleeve 206 112 is then elongated, by approximately 20%, in the direction defined by the circumference of the mandrel 202, to be placed around the mandrel 202 so as to cover the external surface of the assembly 200, as shown in Figure 11.
• Figure 12 shows the mandrel 202, with the assembly 200 and the knitting sleeve 206 112 placed around it, once introduced into a mold 204 comprising on its internal wall 208 at least one concave pattern.
• the mold 204 is pressed, with a pressure of 7 bars, against the assembly 200 and the knitting sleeve 206 112 so that the internal wall 208 of the mold 204 with at least one concave pattern forms a corresponding convex pattern on the external surface of the assembly 200 with the knitting 112.
• the pressure of the mold 204 also allows the penetration of the knitting 112 at the level of the external surface of the teeth thus formed.
• the mandrel 202 is heated to 170°C to ensure vulcanization of the dorsal 104 and ventral 106 portions intended to form the body 102 of vulcanized elastomer.
• the concave pattern of mold 204 is printed on set 200 with knitting 112.
• Test Determination of the coefficient of friction of the belt of the exemplary embodiment on a steel pulley
• the coefficient of friction of the belt was determined with the experimental installation shown in Figure 12.
• the belt 100 is in the form of a single strand (not welded to be closed on itself). same) is arranged on a pulley P.
• the pulley P is chosen to be representative of a steel roller with a round groove.
• One end of the belt strand 100 is mounted on a mass M generating a force F of 1.75 daN (deca Newton), the other end of the belt 100 being mounted on a frame, at the level of which the tension T exerted on the belt strand 100 is measured by a suitable measuring means S, such as a force sensor.
• the pulley P is rotated at a speed of 43 revolutions per minute for the two minutes of the test duration. The force measurement is then carried out at the end of these two minutes, on the still rotating pulley.
• T is the tension measured at one end of the belt expressed in Newton (N)
• F is the force generated by the mass placed at the other end of the belt expressed in Newton (weight).
• Tests to determine the maximum transmissible torque of the belt 100 thus produced were carried out on a test bench comprising two pulleys, a driving one and a receiving one, simulating two rollers of a conveyor.
• the drive pulley rotates at 305 revolutions per minute.
• a resistant torque is applied gradually in steps of 0.1 Nm (Newton meter) on the receiving pulley so as to slide the belt on the pulley. This pair defines the abscissa of the graph presented in Figure 14 and described below.
• WHERE p is the overall slippage, expressed as a percentage (%)
• R m and R r are respectively the radius of the driving pulley and the radius of the driving pulley, each expressed in meters (m), and ⁇ m and ⁇ r are respectively the angular speed of the driving pulley and the angular speed of the receiving hen, each expressed in radians per second (rad/s).
• Figure 14 shows a comparison of the evolution of the sliding as a function of the torque, for a conventional round belt 2 (curve A) and for a belt 100 according to the embodiment example of the invention (curve B).
• Curve A shown in Figure 14 shows that for a conventional round belt 2 the slip is 100% for a maximum torque close to 0.7 Nm.
• Curve B shows that for a belt 100 according to the example of embodiment, the slip is 100% for a maximum torque close to 2.1 Nm
• the belt 100 has a torque transmission capacity, in this case approximately three times greater than that of a conventional belt 2.
• the test consists of repeating a certain number of 1 s / 1 s (second) on/off cycles. This means that the motor roller rotates for one second then stops for one second before starting again for one second and so on until it reaches 500,000 cycles.
• the accelerations/decelerations linked to the on/off cycles combined with the inertia of the slave roller thus generate a resistive torque.
• the coefficient of friction of the belt 100 with the groove 12 of the roller 10 must be less than or equal to 0.8.
• this coefficient of friction of the belt 100 is non-zero and less than 0.8, and at the same time the traction modulus of the belt 100 is between 500 N and 1500 N, advantageously between 800 N and 1500 N, and preferably between 800 N and 1200 N.
• the coefficient of friction of the belt 100 with the groove 12 of the roller 10 is between 0.3 and 0.8, and combined with a traction modulus of the belt 100 of between 500 N and 1500 N , advantageously between 800 N and 1500 N, and preferably between 800 N and 1200 N.
• the invention also relates to a roller conveyor with concave grooves similar to the conveyors 1a, 1b illustrated in Figures 1 and 2.
• This conveyor 1 a, 1 b comprises a plurality of rollers 10 with concave grooves 12 which are connected together in pairs by a belt 100 as described in the above.
• the belt 100 is advantageously installed between the rollers 10 with an installation tension of between 60 N/strand and 100 N/strand.
• FIGS 15 and 16 show the belt 100 according to the invention engaged respectively in a concave groove 12, for example in steel, formed in a roller 10 and in a concave groove 12 belonging to a drive head 18, for example example in plastic such as a polyamide (PA), a polypropylene (PP) or a composite material based on fibers embedded in a thermoplastic or thermosetting resin, fixed on a roller 10.
• a concave groove 12 for example in steel
• a roller 10 for example in plastic
• a polyamide (PA) a polypropylene (PP) or a composite material based on fibers embedded in a thermoplastic or thermosetting resin
• the radius of curvature of the bottom 14 of the groove 12 is substantially equal to the radius of curvature of the teeth of the ventral portion 106 of the body 102. In this way, the contact surface between the belt 100 and the bottom 14 of the groove 12 is maximum.
• the transmission capacity of the belt 100 according to the invention is at least twice as large as that of a conventional round belt 2. Consequently, the conveyor according to the invention can have twice as many slave rollers as a conveyor equipped with conventional 2 round belts.
• a conventional conveyor is dimensioned to include a plurality of motor rollers separated from each other by at least 3 to 5 slave rollers, then the conveyor according to the invention can comprise a plurality of separate motor rollers from each other by at least 6 to 10 slave rollers.
• the classic conveyor is sized as such.
• the belt according to the invention allows an improvement in the torque transmissible by the belt and its stability.
• the contact surface between the belt and the bottom of the roller groove is high thanks to the convex shape of the belt teeth which adapts to the concave shape of the groove.
• the combination of this convex shape of the teeth with the coating arranged at the level of the external surface of the teeth makes it possible to define the coefficient of friction of the belt in the groove at a controlled value.
• the transmissible torque can be controlled as well as the levels of deformation of the belt in the event of contact with one side of the groove, which limits the risk of belt overturning, particularly in a curved part of a conveyor.
• Another advantage is to allow improved durability of the belt over time. Indeed, thanks to the coefficient of friction stable over time, the belt wears less quickly, which improves its lifespan.
• Yet another advantage is to reduce the costs of developing a conveyor. Indeed, thanks to the improvement in the torque transmissible by the belt according to the invention, more slave rollers can be slaved to a motor roller in a conveyor. In fact, the number of motor rollers can be reduced, representing savings in infrastructure and energy.

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• Engineering & Computer Science (AREA)
• General Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Textile Engineering (AREA)
• Belt Conveyors (AREA)
• Rollers For Roller Conveyors For Transfer (AREA)

Applications Claiming Priority (2)

Publications (1)

Family

ID=82594830

Family Applications (1)

Country Status (8)

Family Cites Families (8)

• 2022
  • 2022-05-16 FR FR2204634A patent/FR3135453B1/fr active Active
• 2023
  • 2023-05-12 EP EP23727803.1A patent/EP4526232A1/de active Pending
  • 2023-05-12 WO PCT/EP2023/062724 patent/WO2023222528A1/fr not_active Ceased
  • 2023-05-12 US US18/865,558 patent/US20250314284A1/en active Pending
  • 2023-05-12 CN CN202380039370.3A patent/CN119173458A/zh active Pending
  • 2023-05-12 CA CA3252843A patent/CA3252843A1/fr active Pending
  • 2023-05-12 JP JP2024566731A patent/JP2025517701A/ja active Pending
• 2024
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