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WO2024258760A1 - Système de rail utilisant un pneu non pneumatique - Google Patents

Système de rail utilisant un pneu non pneumatique Download PDF

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Publication number
WO2024258760A1
WO2024258760A1 PCT/US2024/033187 US2024033187W WO2024258760A1 WO 2024258760 A1 WO2024258760 A1 WO 2024258760A1 US 2024033187 W US2024033187 W US 2024033187W WO 2024258760 A1 WO2024258760 A1 WO 2024258760A1
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WO
WIPO (PCT)
Prior art keywords
track system
tire
load
track
pneumatic tire
Prior art date
Application number
PCT/US2024/033187
Other languages
English (en)
Inventor
Ronald Hobart Thompson
Original Assignee
Compagnie Generale Des Etablissements Michelin
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Compagnie Generale Des Etablissements Michelin filed Critical Compagnie Generale Des Etablissements Michelin
Publication of WO2024258760A1 publication Critical patent/WO2024258760A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62D—MOTOR VEHICLES; TRAILERS
    • B62D55/00—Endless track vehicles
    • B62D55/08—Endless track units; Parts thereof
    • B62D55/14—Arrangement, location, or adaptation of rollers

Definitions

  • This disclosure relates to non-pneumatic tires for track systems, and, more generally, to vehicles such as agricultural vehicles or industrial vehicles.
  • Track systems are used in a variety of industries, particularly in off-road vehicles needing high traction. These can include construction vehicles (loaders, excavators, etc.) and military vehicles (tanks) and agricultural vehicles (tractors, sprayers, etc). Track systems may enhance traction and/or flotation on soft, slippery, and/or irregular grounds.
  • suspension systems on track vehicles may be expensive and complex. Due to their very nature, track systems employ a track that wraps around a plurality of wheels. Mounting a suspension system on each wheel may increase complexity, cost, and may reduce system reliability.
  • US Patent Application Publication 2020/0277012 shows a compliant wheel in the idler position.
  • This compliant wheel may reduce impact forces passed to the track suspension frame by acting like a shock absorber of sorts. As such, the performance of the track system may be enhanced.
  • WO 2022/104481 also owned by the current applicant and included herein by reference, discloses a track tensioning system.
  • This track tensioning system comprises springs that support both idler wheels. It is therefore a dual track tensioning system.
  • This system may be efficient for reducing the required function of a compliant wheel in the idler wheel. It may enable the use of a more rigid wheel that still deforms under impact. It may also reduce the track tension forces developed during acceleration and braking. Therefore, a dual tension system in a track system may enable complaint wheels.
  • a track system may benefit by having complaint wheels not only in the idler wheel position, but also in the midroller position. This, however, is a challenge because the midroller supports the majority (if not all) the weight of the vehicle. Midrollers may be smaller than idler wheels, meaning that even small deflections may be large percentages of the radius of the wheel. Designing a large enough compliance within a small design window could be challenging.
  • a non-pneumatic tire for use as a midroller in a track system, the non-pneumatic tire comprising an annular beam, further comprising an annular support extending radially inward from the annular beam, for which a deflection at a contact patch of the annular beam is no less than 0.5% of the diameter of the annular beam when the non-pneumatic tire is loaded to a design load, the annular support being configured to develop tension forces when the non-pneumatic tire is loaded to the design load.
  • the deflection may be no less than 1% of the diameter; in other cases, 2%. In such an embodiment the diameter is measured to the outer extent of the annular beam.
  • a track system comprising a non-pneumatic tire, the non-pneumatic tire comprising an annular beam, further comprising an annular support extending radially inward from the annular beam, the annular support being configured to develop tension forces when the non-pneumatic tire is loaded to the design load.
  • the track system further comprises a dual tension system for a track.
  • a non-pneumatic tire for use in a track system, the non-pneumatic tire comprising an annular beam, further comprising an annular support extending radially inward from the annular beam, the annular support being configured to develop tension forces when the non-pneumatic tire is loaded to the design load.
  • An initial secant vertical stiffness of the non-pneumatic tire measured at the design load is at least twice that of a secant vertical stiffness measured at 2.7 times the design load, and in other cases the secant vertical stiffness is at least three times, and in other cases, even more.
  • a non-pneumatic tire for use in a track system, the non-pneumatic tire comprising an annular beam, the annular beam comprising a reinforcing ring extending in the circumferential direction, the non- pneumatic tire further comprising an annular support extending radially inward from the annular beam, the annular support being configured to develop pre-tension forces after the non-pneumatic tire is formed.
  • the non-pneumatic tire comprises a thermoplastic elastomer.
  • a track system having a non-pneumatic wheel, where the wheel comprises a tire portion and a hub portion.
  • the non-pneumatic wheel has a wheel mass divided by a tire outer diameter divided by a max tire width should be no more than 0.0002 kg / mm 2 : in other cases no more than 0.00015 kg / mm 2 , and in other cases, even less.
  • the wheel mass is calculated by adding the mass of the hub and outer tire portion of the wheel.
  • Figure 1 is an exemplary example of an NPT used in a track system.
  • Figure 2 is an exemplary example of an NPT used in a track system having spokes that intersect one or a plurality of other ones of the spokes.
  • Figure 3 is an exemplary example of an NPT used in a track system.
  • Figure 4 is a track system comprising exemplary examples of NPTs.
  • Figure 5 is a track system comprising and exemplary example of an NPT.
  • the track system comprises a dual-tensioning system for a track.
  • Figure 6 is a graph showing load vs. deflection of three midroller NPTs.
  • Figure 7 is a graph showing load vs. deflection of three idler wheel NPTs.
  • Figure 8 shows a deformed Finite Element Model (FEM) of an exemplary example of an NPT, loaded to an impact load.
  • FEM Finite Element Model
  • Figure 9 is a photograph of an NPT in a track system, having wheels in accordance with an embodiment of the invention, when subjected to an impact load.
  • Figure 10 is a track system dynamic modeling result of a midroller stiffness vs midroller impact force transferred to the track system frame transiting an obstacle at a speed of 3 kph.
  • Figure 11 is an example of a reinforcing ring used in an annular beam of an NPT.
  • Figure 12 is a close-up image of a reinforcing ring.
  • Figure 13 is a close-up image of a reinforcing ring.
  • Figure 14 shows a reinforcing ring comprising a pin for fixation inside a mold.
  • Figure 15 shows another exemplary example of a reinforcing ring.
  • Figure 16 shows load vs. deflection for NPTs with and without a reinforcing ring.
  • Figure 17 shows creep performance of NPTs with and without a reinforcing ring.
  • Figure 18 is an NPT comprising a tread.
  • the present invention provides a compliant non-pneumatic tire for an endless track system for a vehicle.
  • embodiments and/or methods of the invention one or more examples of which are illustrated in or with the drawings.
  • Each example is provided by way of explanation of the invention, not limitation of the invention.
  • various modifications and variations can be made in the present invention without departing from the scope or spirit of the invention.
  • features or steps illustrated or described as part of one embodiment can be used with another embodiment or steps to yield a still further embodiments or methods.
  • the present invention covers such modifications and variations as come within the scope of the appended claims and their equivalents.
  • Human refers to any structure for supporting the tire and capable of attachment to a vehicle axis.
  • modulus means Young’s tensile modulus of elasticity measured per ASTM D638. The tensile modulus may be calculated as the secant modulus at a tensile strain of 0.5%.
  • modulus means Young’s tensile modulus of elasticity measured per ASTM D638. The tensile modulus may be calculated as the secant modulus at a tensile strain of 0.2%.
  • Design Load of a tire is operating load of the tire when the track system is loaded to a Maximum Load.
  • Diameter of a tire is measured at the outer extent of the annular beam inclusive of any tread material that may be present.
  • Tire vertical force vs. deflection and footprint measurements may be performed according to SAEJ2704.
  • ‘Maximum Load” of the track system is the maximum permissible load assigned to a track system by the manufacturer, or where the manufacturer does not specify a Maximum Load, as specified by the designer of the track system, or where the manufacturer or designer does not specify a Maximum Load, as specified by the distributor.
  • ‘Midroller” refers to a wheel position between the idler wheels in a track system as shown in Figure 4.
  • idle wheel refers to a wheel position on the front and back ends in a track system as shown in Figure 4, the “front” and “back” referring to the potential directions of travel of the track.
  • Figure 1 shows a non-pneumatic tire 100 for a track system according to an aspect of the invention.
  • a cylindrical coordinate system 140 defined by the invention is shown, along with a corresponding cartesian coordinate system 150.
  • the "X" or longitudinal direction may be considered the direction of travel.
  • the tire has a circumferential beam 110, with an annular support 120 that extends radially inward from the beam.
  • a hub 130 is positioned radially inward from the annular support. The tire rotates around the Y axis.
  • the annular support comprises a spoke structure comprising a plurality of spokes in which each spoke of the plurality of spokes extends radially from the hub to the annular beam.
  • each tire has a first lateral side and a second lateral side opposite the first lateral side forming the axial extents of the tire and each of the spokes of the plurality of spokes extend from the first lateral side to the second lateral side.
  • the annular support comprises spokes that intersect one or a plurality of other ones of the spokes.
  • Figure 2 shows an example of an annular support having spokes 820 that are not continuous from the annular beam 810 to the hub 830, thereby creating two rows of rectangular openings.
  • Each spoke 820 is comprised of a radially outer portion 822 and a radially adjacent radially inner portion 826.
  • Each spoke 820 is adjoined to a circumferentially adjacent spoke by a flange 824 positioned between the hub 830 and the annular support 820.
  • a flange 824 positioned between the hub 830 and the annular support 820.
  • FIG 3 shows an idler wheel 200 according to aspects of the invention.
  • the idler wheel comprises an annular beam 210 which may comprise a web structure 240.
  • the web structure may comprise circular, oval, or elliptical openings. These openings may extend from one axial extent of the annular beam to the other axial extent.
  • a track system 300 is shown in Figure 4.
  • the track system comprises a nonpneumatic tire in a midroller position 310 and a non-pneumatic tire in an idler wheel position 320.
  • midroller will henceforth refer to a non-pneumatic tire in the midroller position
  • idle wheel will refer to a nonpneumatic tire in the idler wheel position, unless otherwise noted.
  • the track system further comprises a track 330.
  • the track has a pretension force which is reacted by the idler wheels.
  • the track system carries a weight which is supported by the midrollers and idler wheels as they roll on the radially inward side of the track.
  • the track system may be configured such that most or all the load is carried by the midrollers when in operation on flat ground at a design load.
  • Figure 5 shows the track system from an axial perspective.
  • This exemplary embodiment further comprises a twin tensioning system, similar to that described in PCT publication WO 2022/104481 Al describing a Track System for Traction of a Vehicle, incorporated herein by reference.
  • tensioning elements are configured such that the track system may be operated in either longitudinal direction.
  • the tensioning system is configured such that rapid deceleration of the track system does not result in high track tension force. The tension force during deceleration may be the same whether the track system is traveling in the +X or the -X direction.
  • Figure 5 further shows a track system frame 360.
  • This frame must be designed of sufficient strength to withstand not only a design load during normal operation but also impacts and other punctual loads to which the track system is anticipated to be subjected to.
  • the use of a twin tensioning system may enable or enhance the use of a non-pneumatic, deformable tire as an idler wheel. While deformable, the idler wheel must still be able to resist the tension force in the track. Under certain braking conditions, the tension force in a single tension element track system may be so high that the use of a deformable idler wheel becomes very difficult. Therefore, in some cases, a twin tension system and deformable idler wheels may be combined. [0059] Example 1.
  • NPTs designed according to Figures 1 and 3 were reduced to practice and tested in a battery of lab and on-vehicle tests.
  • the NPTs were further designed to be injection molded with a single elastomeric thermoplastic.
  • Several different thermoplastic materials were prototyped.
  • Several figures and tables will now disclose results obtained. These results were, in part, surprising and unexpected. Not surprising, these results form the basis for several aspects of the invention.
  • Elastomers from any suitable family may be employed. This may include thermoplastic elastomers such as co-polymers. This may include products from DuPont (Hytrel) or from DSM (Amitel), or other similar products. Other elastomer families may include certain nylon resins with softening agents added, such as impact modifiers (EPDM rubber or the like). Other elastomer families could include TPUs, such as BASF's Ellastolan.
  • the midroller carries most of the load at the design load.
  • the idler wheels carry minimal load when in normal operation on flat ground. In specific embodiments, the idler wheels carry less than 10% of the design load. Idler wheels may be functionally important in shock absorption, for example, when the track system encounters obstacles.
  • 2200 N is a design load on one midroller when the track system is operating at the design load. The midroller must support this load during normal operation on flat ground.
  • 5940 N is an impact load on one midroller when the track system encounters an obstacle, such as a rock or a curb or a railroad track. This load is punctual and is equal to 2.7 times the nominal load.
  • Suspension systems comprising springs and shock absorbers may be expensive and complex in a track system. For this reason, track systems may have no suspension system other than the idler wheels, midrollers, and track itself. Having deformable wheels may greatly improve the inherent shock absorbing capability of a track system that does not have a dedicated suspension system.
  • Wheels that deform may greatly reduce shock loading to the frame of the track system. In doing so, deformable wheels may improve the fatigue life of the system and/or enable a lighter weight, lower cost frame to be designed.
  • deformable wheels in a track system may reduce the pressure that the wheel exerts on the radially inward surface of the track.
  • a deformable, compliant wheel may develop a larger contact area, thereby reducing pressure at a given load.
  • energy loss in an elastomer directly relates to the change in strain energy as the elastomer is subjected to a cyclic stress. By reducing the stress applied by the wheel to the track, the hysteretic energy loss of the track may be reduced.
  • Figure 7 shows a load vs. deflection plot of these three idler wheels. As with the midrollers, the three levels of elastomer stiffness result in three different load vs. deflection curves. Similar to the midroller, Tire A is linear and much stiffer, while B and C show nonlinear behavior.
  • Figure 8 shows a deformed FEA model of midroller tire B, when loaded to the impact load of 5940 N.
  • the annular support comprises spokes 320 away from the contact area and spokes 310 in the contact area. Spokes away from the contact area develop tension forces. Spokes in the contact area are deformed in bending at this load. In fact, these spokes behave as postbuckled columns. Before the critical bucking load, spokes in the contact area are stiff. After the buckling load, their load-carrying contribution is reduced. Hence, the load vs. deflection of the tire is non-linear.
  • Equation 1 Euler's critical buckling load formula for a column fixed at both ends is shown below in Equation 1 :
  • Fc buckling load
  • E the spoke modulus
  • I the spoke moment of inertia in the R-T plane
  • w the spoke width
  • t the spoke thickness
  • L the distance from spoke intersection with annular beam to intersection with hub.
  • the secant vertical stiffness at a load of 2200 N is 1560 N /mm.
  • the secant stiffness 960 N/mm is 1.6 times as large as the secant stiffness at the impact load.
  • a secant stiffness of the midroller at the design load should be at least 1.4 times that of a secant stiffness at the impact load. In other cases, at least 1.8 times, and in other cases, even more.
  • the idler wheel carries relatively little to no load when under normal operation on a flat surface. Its primary function is to simply support track tension while carrying transient loads during impacts as the vehicle navigates non-flat terrain or encountering obstacles. Therefore, there is no vertical design load, per se, for the idler wheel. Nevertheless, the inventors have determined that the non-linear behavior of Tires B and C in Figure 7 is very beneficial for reducing impact loading. Instead of being defined relative to load, the idler wheel secant vertical stiffness may be defined according to displacement.
  • an initial secant stiffness is measured at a small displacement equal to 0.5% of the idler wheel diameter.
  • the idler wheel impact displacement can be estimated as 5% of the idler wheel diameter.
  • a secant stiffness of the idler at a displacement of 0.5% of the diameter should be at least 2.0 times that of a secant stiffness at a displacement of 5% of the diameter. In other cases, at least 2.6 times, and in other cases, even more.
  • a track system may comprise a compliant midroller and a rigid idler wheel.
  • a track system may comprise a complaint idler wheel and a rigid midroller. Aspects of this invention are meant to encompass both of these configurations, as well as the exemplary embodiment tested here, in which both midroller and idler wheel were compliant.
  • one advantage of a complaint wheel is that shock loads to the track system may be reduced, compared to a rigid wheel. The inventors studied this with a track system that was reduced to practice and instrumented with strain gauges installed in key high stress areas of the system frame. Then, using an engineered "bump" or obstacle, strain gauge measurements were made using a step-speed test. This was performed with the same track system, but mounted with Tire A, Tire B, and Tire C. For all tests, both idler wheel and midrollers were tested using the same material.
  • Figure 9 is a photograph of test apparatus used to gather data for Table 2. Idler wheel 310 and midroller 320 both deform during contact. In the Figure, the midroller is clearly seen deforming to approximately the impact load as the track and midroller envelop an obstacle 400. Spokes 222 are post-buckled in the contact area and under tension 221 away from the contact area.
  • the midroller deflection at the design load is desirable to be within a specific range of the tire diameter. It was discovered if the deflection at the design load as a percentage of the diameter is very small, such as Tire A (0.2%) for example, then the tire is too stiff. If this ratio is too large, such as Tire C (1.5%) for example, then the tire is too compliant.
  • a midroller deflection should be at least 0.5% and no more than 1.3% of the tire diameter when loaded to a design load and in other cases, at least 0.8% and no more than 1.3%.
  • Table 3 Power required to operate at steady state speed on level ground.
  • elastomeric compliant midrollers and idler wheels Another benefit of elastomeric compliant midrollers and idler wheels is weight.
  • the specific gravity of an elastomer may be about 1.1, whereas steel is 7.8. Therefore, intrinsic wheel mass may be reduced compared to a steel wheel.
  • the track system frame is designed to resist the transient, but significant forces that occurs due to punctual impact loading. The impacts upon a steel wheel are transferred directly to the frame that supports the midrollers.
  • Midroller and idlerwheel compliance enables a lower weight track system frame by reducing the punctual loading that would be endured by the system.
  • the inventors designed a standard track system using prior art metal wheels, with corresponding prior art design rules.
  • the use of compliant wheels in the track system results in weight reduction from two sources, intrinsic weight reduction from the use of lighter weight wheels and extrinsic weight reduction by enabling lighter weight components in the design of the track frame itself which is permitted by reduced impact loads during operation such as depicted occurring in Figure 9.
  • the inventors compared track system mass of this prior art system to the mass obtained with aspects of the current invention. Results are shown in Table 4.
  • Table 4 shows that a 7% mass reduction was achieved due to aluminum components in the undercarriage.
  • this undercarriage had been tested with rigid wheels, it would not have had the required strength to meet endurance requirements because the metal wheels lack of compliance allows for transient impact loads to excessively load the undercarriage components.
  • the inventors found the architecture of an elastomeric non-pneumatic tire with an annular beam and an annular support that develops tension forces to be surprisingly efficient in terms of mass reduction.
  • This benefit can be characterized as a ratio equal to the tire mass divided by the tire outer diameter divided by the tire width. This gives an equivalent mass density.
  • a wheel mass divided by a tire outer diameter divided by a max tire width should be no more than 0.0002 kg / mm 2 : in other cases no more than 0.00015 kg / mm 2 , and in other cases, even less.
  • the wheel mass is calculated by adding the mass of the hub and outer tire portion of the wheel.
  • FIG. 10 depicts the track system comprising wheels of elastomer C, B, and A with metal reference from left to right on the chart from most compliant to least compliant.
  • Figure 10 shows a direct correlation between transmitted impact force and wheel stiffness. This further validated the empirical strain gauge measurements noted earlier. Compliant wheels reduced shock loading, which resulted in lower strain and stress in the undercarriage frame.
  • midroller and idler wheels A, B, and C used a monoelastomer architecture.
  • the inventors have found that, in certain cases, it may be advantageous to include a reinforcing ring extended in the circumferential direction of the annular beam. Such reinforcement may improve certain performances.
  • FIG 11 shows an exemplary embodiment of a reinforcing ring 500.
  • the reinforcing ring comprises a dovetail geometry 510 on the radially outward surface and a dovetail geometry 520 on the radially inward surface.
  • a protruding surface, extending away from the reinforcing ring in the radial outward or radially inward direction form the dovetail geometry 510 or 520, with each circumferentially facing wall of the dovetail geometry extending toward the adjacent facing wall of the dovetail geometry circumferentially adjacent to it.
  • a locating pin 530 extends in an axial direction which may contact a mold surface and serve to position and stabilize the reinforcing ring in a mold by contacting the lateral surfaces of the mold cavity for the annular beam into which the reinforcing ring is placed.
  • the material is allowed to pass around and envelope the reinforcing ring, with exception, perhaps, to the points of contact the reinforcing ring 500 has with the mold surfaces.
  • the locating pins maintain the position of the ring within the mold.
  • a pin 540 and a pin 550 may be configured with male and female axial extents respectively, thereby permitting two reinforcing rings to connect.
  • Radial extending locating pins 560 located on the radial extent of the reinforcing ring 500.
  • the radially extending locating pins 560 extend radially inwardfrom the radially inward facing radial extent of the reinforcing ring 500. Similar to the laterally positioned locating pin 530, the radial locating pin maintains the reinforcing ring 500 in position within the mold particularly during the injection of the material into the mold.
  • the wall thickness of the reinforcing ring was between 1 mm and 2 mm.
  • the scope of this invention is meant to encompass reinforcing ring thicknesses between 0.5 mm to 10 mm. Thicker rings may be used for larger tires; thinner rings may be used for smaller tires.
  • Figures 12 and 13 shows close-ups of the reinforcing ring depicting one embodiment of the mechanical locking features. It can be seen in Figure 12 that the angle 0 A and angle 0B formed by the circumferential facing wall surfaces of the dovetail and the circumferential direction is less than 90 degrees.
  • Figure 13 shows a view of two adjacent reinforcing rings 500 laterally separated but aligned to allow mating of the male end 540 of a locating pin on a first reinforcing ring with the female end 550 of a locating pin on a second reinforcing ring.
  • Figure 14 shows a mold surface 600 of an injection mold into which the reinforcing ring may be placed.
  • Pin 530 may be configured to insert into a mold recess 610. In this way, the reinforcing ring may be stabilized.
  • FIG. 15 Another exemplary example of a reinforcing ring 700 is shown in Figure 15.
  • the reinforcing ring 700 possesses apertures 710 which allow the annular beam forming material to pass through. Similar to the previously shown embodiments, this embodiment may have locating pins 730, 760 extending laterally or radially from the reinforcing ring.
  • Acceptable materials for the reinforcing ring may include nylon (PA) resin with glass reinforcement of 10%, 20%, 30% or even higher.
  • Other material choices include glass reinforced PET with glass or carbon reinforcement.
  • Still other choices include blends of PET and PBT.
  • Polycarbonate (PC) may be suitable with our without reinforcement.
  • FIG. 16 shows load vs. deflection curves for Tires D, E, and F.
  • Tire D is the least stiff tire.
  • the addition of the reinforcing ring in Tire E which still using the same elastomer stiffness of Tire D, increased stiffness by about 35%.
  • Tire F used a much stiffer elastomer, without a reinforcing ring.
  • Tires D and F had almost the same stiffness. Therefore, the addition of a reinforcing ring enabled the use of a softer elastomer in obtaining a stiffer tire.
  • Softer elastomers may have enhanced material characteristics - such as, improved crack propagation resistance, lower glass transition temperature, and improved processing characteristics. Therefore, Tire E may be preferred to Tire D.
  • Figure 17 shows a creep displacement as a function of time for Tires D and E.
  • the creep is a change in displacement while the tire is loaded to a static load. This simulates the condition of a vehicle that is left stationary for some period of time, during which the tire may develop a "flat" spot.
  • Those skilled in the art of tire design realize that minimal creep displacement is a positive design attribute.
  • a particular useful embodiment would be a tire having a reinforcing ring configured such that the creep when loaded to a design load in the radial direction over 100,000 seconds is no more than 0.6% of an initial wheel diameter.
  • Figure 18 is an NPT according to the invention where the annular beam further comprises a tread portion 250 disposed on the outer radial extent.
  • the tread may be smooth or may have a tread pattern.
  • the tread material may be any suitable material, usually of lower modulus than the elastomer used to form the annular beam and annular support.
  • the tread material may comprise rubber, a thermo-plastic urethane (TPU), a thermoplastic vulcanized elastomer (TPV), or other suitable materials.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Mechanical Engineering (AREA)
  • Tires In General (AREA)

Abstract

Un pneu non pneumatique destiné à être utilisé en tant que rouleau intermédiaire dans un système de rail comporte une poutre annulaire et comporte en outre un support annulaire s'étendant radialement vers l'intérieur à partir de la poutre annulaire, pour lequel une déviation au niveau d'une zone de contact de la poutre annulaire n'est pas inférieure à 0,5 % du diamètre de la poutre annulaire lorsque le pneu non pneumatique est chargé à une charge de conception, le support annulaire étant configuré pour développer des forces de tension lorsque le pneu non pneumatique est chargé à la charge de conception. Dans certains cas, la déviation peut être non inférieure à 1 % du diamètre; dans d'autres cas, à 2 %.
PCT/US2024/033187 2023-06-10 2024-06-10 Système de rail utilisant un pneu non pneumatique WO2024258760A1 (fr)

Applications Claiming Priority (2)

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US202363507451P 2023-06-10 2023-06-10
US63/507,451 2023-06-10

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011041704A1 (fr) * 2009-10-01 2011-04-07 Camoplast Inc. Ensemble chenille pour la traction d'un véhicule
US20120200149A1 (en) * 2011-01-27 2012-08-09 Irobot Corporation Resilient wheel assemblies
WO2017106750A1 (fr) * 2015-12-16 2017-06-22 Thompson Ronald H Système de chenille pour la traction d'un véhicule
EP3957491A1 (fr) * 2020-08-17 2022-02-23 Kässbohrer Geländefahrzeug AG Roue de chenille pour un véhicule à chenilles
WO2022104481A1 (fr) 2020-11-20 2022-05-27 Camso Inc. Système de chenille pour traction d'un véhicule

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2011041704A1 (fr) * 2009-10-01 2011-04-07 Camoplast Inc. Ensemble chenille pour la traction d'un véhicule
US20120200149A1 (en) * 2011-01-27 2012-08-09 Irobot Corporation Resilient wheel assemblies
WO2017106750A1 (fr) * 2015-12-16 2017-06-22 Thompson Ronald H Système de chenille pour la traction d'un véhicule
US20200277012A1 (en) 2015-12-16 2020-09-03 Ronald H. Thompson Track system for traction of a vehicle
EP3957491A1 (fr) * 2020-08-17 2022-02-23 Kässbohrer Geländefahrzeug AG Roue de chenille pour un véhicule à chenilles
WO2022104481A1 (fr) 2020-11-20 2022-05-27 Camso Inc. Système de chenille pour traction d'un véhicule

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