SUPPORTING WHEEL

Abstract: A non-pneumatic supporting wheel includes a central part (10) and a wheel-rim (14-16) which is supported by the central part. The wheel-rim has an outer wheel-rim part (14, 15) which is intended to roll against an underlying surface, and an inner wheel-rim part (16) which is located radially inwards of the outer wheel-rim part. At least the inner of the two wheel-rim parts is constructed from a plurality of curved, elongated elements (16) which consist of a resilient material and which are spaced in the circumferential direction of the wheel. When seen in a section taken diametrically through the wheel, each of these elements presents parts (17, 18) which are curved in opposite directions. For the purpose of taking-up forces which act substantially radially between the wheel centre (11) and the region (15) of the wheel in contact with the underlying surface when the wheel is subjected to load, the elements (16) are elastically yielding in the radial direction of the wheel during increased bending of the elements. The circumferentially spaced and bendable elements (16) are constructed so that both the sum of the bending of each small longitudinal section ( DELTA 1k, DELTA 1m, DELTA 1j, DELTA 1n) of the elements when the elements are subject to load in the radial direction of the wheel and the sum of the product of the bending (vj, vn) of each such small section ( DELTA 1j, DELTA 1n) and the distance of this section (hj, hn) from the underlying surface when the wheel is subjected to normal load is at least essential zero.

Description: Supporting Wheel This invention relates to a non-pneumatic supporting wheel of the kind comprising a central part and a wheel- rim, which is carried by said central part and which has an outer wheel-rim part, which is intended to roll on an underlying surface, and an inner wheel-rim part, located radially inwards of said outer wheel-rim part, wherein at least the inner of the two wheel-rim parts is constructed from a plurality of curved elongated elements which consist of a resilient material and which are mutually separated in the circumferential direction of the wheel, and wherein each of said elongated elements, when seen in a section taken diametrically through the wheel, present parts which are curved in opposite directions, and which elements, for the purpose of taking-up forces which, when the wheel is subjected to load, act substantially radially between centre of the wheel and the region thereof in contact with the underlying surface, are elastically yielding in the radial direction of said wheel during increased bending of said elements. In the case of known non-pneumatic support wheels, see for instance US-A-2,436,844 and 4,350,196 and WO 87/05268, the outer wheel-rim part tends to move to one side upon contact with the underlying surface. This can result in drawbacks in the form of increased wear on the material which comes into contact with the underlying surface, increased stresses on wheel bearings, impaired road holding of a vehicle which is fitted with such non-pneumatic suppor¬ ting wheels, and, above all, higher internal losses as a result of propagation of the lateral movements of that wheel-rim region in contact with the underlying surface to adjacent regions of the wheel and resultant deformation of said regions. The object of the present invention is to provide a novel and useful supporting wheel in which the afore¬ said drawbacks are at least substantially avoided. To this end, it is proposed in accordance with the inven¬ tion that in the case of a supporting wheel of the kind described in the introduction, the bendable elements which are mutually spaced in the circumferential direction of the wheel are so constructed that both the sum of the bending of each small longitudinal section of the elements when said elements are subjected to load in the radial direction of the wheel, and the sum of the product of the bending of each such small section and the distance of this section from the underlying surface when the wheel is subjected to normal load is at least substantially zero. As a result of this arrangement, the supporting wheel will b deformed elastically substantially only in the radial direc¬ tion when in contact with the underlying surface. The aforedescribed, inventive construction of the elongated resilient elements can be achieved " in many different ways in practice. However, a preferred embodiment of the inven¬ tion is characterized in that the elements or the parts thereof which form the inner wheel-rim part of said wheel have, when seen in a section taken diametrically through the wheel, essentially the form or a recumbent S with the end of a radially outward convex part being located on one side of the wheel and connected to the central part of said wheel, and the end of a radially inward convex part being connected to the outer wheel-rim part on the opposite side of said wheel. When the outer wheel-rim part has the form of a cir- cu ferentially extending web, it is particularly advan- tageous to provide the web with radially through-passing holes. These holes, which extend through the outer wheel- rim part, have surprisingly been found to reduce the level of noise that is generated when the supporting wheel rolls against the underlying surface. It has been possible to achieve noise reductions as high as 10 dBA, with a suitable choice of hole size and shape. The invention will now be described in more detail with reference to the accompanying drawings. Figure 1 is a schematic axial-section partial view of an inventive non-pneumatic supporting wheel, with the wheel shown in a load-free state. Figures 2 and 3 are simplified axial-section partial views of a non-pneumatic supporting wheel similar to the wheel of Figure 1 and illustrate the principles of the invention, said wheel being shown in a loaded state in said Figures. In the drawings, the reference numral 10 identifies generally a central part of a non-pneumatic supporting wheel, for instance the wheel of an automotive vehicle, whose geometric axis is referenced 11. The central part 10 comprises two discs 12, which may be provided with holes (not shown) by means of which the wheel can be fitted, for instance, to a wheel hub, and a disc 13 which is held between the discs 12. The wheel also includes a wheel-rim which is carried by the part 10 and which has an outer, circumferentially extending wheel-rim part 14, having an outer surface layer 15 or tread made, for instance, of rubber or plastic material and intended for contact with the underlying surface, or rolling surface, and an inner wheel-rim part which is comprised of a plurality of elongated, curved elements 16. These elements 16, the inner ends of which connect with the disc 13, are mutually spaced in the circumferential direction of the wheel and, when seen in a section taken diametrically through the wheel, present, in the manner shown, oppositely curved parts 17, 18, which are located on respective sides of an imaginary plane extending through the loading centre CL (Figures 2 and 3) , this plane extending through the wheel at right angles to the axis 11 at a location. In a normal case, this location lies midway between the opposite sides of the wheel and the opposite sides of the outer layer 15 or tread in contact with the underlying rolling surface respectively. When the wheel is subjected to load, forces act substantially radially between the centre 11 of the wheel and that region of the outer layer which is in con¬ tact with the underlying surface. An essential part of these forces is taken-up by the elements 16 as bending of the curved parts 17, 18 increases. The resilient elements 16 have been constructed in a manner to fulfill the follow- ing two conditions simultaneously, by appropriate selec¬ tion of the material from which said elements are made coupled with suitable selection of their dimensions and shapes, these conditions being : a) that the sum of the extent to which each small lon¬ g'itudinal section Δlk. ,' Δlm,' Δl_. ,' Δln of the elements 16 bends when the elements are subjected to load (within the intended wheel loading range) is zero or at least substan¬ tially zero; and b) that the sum of the product of the extent to which each such small section Δl . , Δl bends and the dis- _ n tance h . , h of this section from the underlying surface is zero or at least substantially zero. The condition a) is illustrated (greatly exaggerated for the sake of clarity) with the loaded wheel shown in Figure 2, where a force or a load acting on the outer layer 15 in the region of its contact with the under¬ lying surface is assumed to be evenly distributed over the whole width of the contact region and has a force resultant which acts in the load centre CL perpendicularly to the underlying surface. The load exerted on the wheel causes each small p c iece or section Δl, , Δlm of the curved element 16 concerned to bend from a load-free state, shown in broken lines, through an additional angle of curvature vk, ,' vm to the loaded state illustrated in full lines. This additional angular value is, of course, contingent on the size of the load. This further bending v, of the elements 16 on one side of the load centre CL will therewith cause the outer wheel-rim part to be obliquely positioned in one direction as this wheel-rim part moves inwardly through a distance which, in the CL-plane, has the length r, , whereas the further bending v of the element 16 on the other side of the load centre CL will cause the outer wheel-rim part to be positioned obliquely rearwards in the other direction, as this part moves inwards through a distance which, in the CL-plane, has the length r . The sections Δl, and Δl are representative of other small length sections of the elements 16 on one or the other side respectively of the load centre CL. The result of the directive or condition a) is thus that the outer wheel-rim part will retain its parallelity with the underly¬ ing surface in the region of its contact with said surface, with the load uniformly distributed over the whole width of the wheel during radial movement. The condition a) , however, does not exclude lateral movement of the region of the outer wheel-rim part in contact with the underlying surface relative to adjacent regions of this wheel-rim part, and consequently the condition b) is prescribed in order to rectify this. The condition b) is illustrated (greatly exaggerated for the sake of clarity) with a loaded wheel in Figure 3, where a force or load acting on the outer layer 15 in the region of its contact with the underlying surface is assumed to be uniformly distributed over the with of the wheel and to have a force resultant which acts in load centre CL perpendicularly to the underlying surface. The load causes each small piece or section Δl., Δl of the curved element 16 concerned to bend through a further angle v., v , from a non-loaded state, shown in broken lines, to a loaded state shown in full lines. The size of this further angle is, of course, contingent on the size of the load. This further bending v. of the section Δl . of the element 16 on one side of the load 3 centre CL will therewith attempt to move the outer wheel- rim part laterally in one direction through a distance a . whose length is contingent on the product of the further bending v. and the distance h. of the section Δl . from the y 3 3 3 underlying surface, whereas the further bending v of the section Δl of the element 16 on the opposite side of the load centre CL will strive to move the outer wheel-rim part laterally, back in the opposite direction through a distance a , whose length is contingent on the product of the further bending J vn of this section Δln and the distance hn of said section from the underlying surface. The sections Δl . and Δl are representative of remaining small length-sections of the element 16 located on one and the other side of the load centre CL respectively. Thus, the result of condition b) is that the outer wheel-rim part will not be moved laterally in the region of its contact with the underlying surface, and consequently the result of condition b) in combination with the result of condition a) will result in substantially optimal function of the supporting wheel. In Figures 1-3, the elements 16, when seen in a section taken diametrically through the wheel, have substantially the form of a recumbent S, with the end 21 of a radially outward convex part 17 located on one side of the support¬ ing wheel and adjoining the centre part of said wheel, more specifically the adjoining radially outer region of the disc 13, and with the end 22 of a radially inward convex part 18 adjoining the outer wheel-rim part 14, 15 on the opposite side of the wheel. In this way, a relatively small space is required radially for the resilient elements 16. It is also possible, however, to give the resilient elements 16 essentially the form of an upstanding S, with convex, resilient parts located on a first and a second side respectively of said wheel, substantially on opposite sides of the load-centre plane CL and at different radial distances from the tread 15, although respect must be paid to the fact that when the resilient elements bend, those parts of the elements- 16 which are located far from the underlying surface will cause greater lateral movement of that region of the outer wheel-rim part in contact with the underlying surface than those parts of the elements 16 which are located close to said surface. For example, those parts which are distal from the underlying surface are made more rigid than those parts which are located close to said surface. The outer wheel-rim part 14, 15 may advantageously be constructed of radially outer end-parts 19 or continuations of the elongated elements 16 mutually spaced in the circum¬ ferential direction of the wheel, said end parts extending substantially horizontally from the region 22 on one side cf the wheel towards and past the CL-plane, to the other side of said wheel. These end parts or continuations 19 may be embedded in the tread material, such as rubber or plastic material, either individually or, as shown, commonly. In the former case, the tread will thus also consist of perpherally separated regions, while in the latter case the tread will extend continuously around the wheel. It is also possible to construct the outer wheel-rim part as a substantially cylindrical ring of resilient material which is clad with tread material and to which the regions 22 of the elements 16 connect. It is also possible to construct the wheel more or less completely from composite material. At least when the outer wheel-rim part 14, 15 is in the form of a circumferentially extending, continuous web, it is suitable to form radially through-passing holes 20 in said web, in the manner illustrated, in order to reduce the level of noise that is generated when the wheel runs on the underlying surface. More specifically, the outer wheel-rim part 14, 15, in accordance with Figure 1, is provided with rows of through-passing holes 20 which extend completely through both the tread material 15 and the tread-supporting structure 14, so as obtain "ventilation" between the outer surface of the outer wheel-rim part and the radially inwardly facing inner surface 23 of said wheel-rim part. The holes 20 are arranged in pattern cavities 24 in that side of the web or tread intended for contact with the underlying surface. Ths size, shape and number of the holes 20 used to reduce sound emission can vary from case to case and the holes may also have a cross-sectional area which varies along their respective lengths. The combined area of the holes 20 should, however, lie between 2 and 50% of the total area of the side of the web or tread intended for contact with the underlying surface. The holes may be from 100 to 1,000 in number and may have a combined hole-area of at least 3%, suitably at least 5% and preferably at least 7% of the area of said web or tread side, and at most 30% and suitably at most 25% of the area of said web side. An advantage is afforded when at least some of the holes 20 are arranged in the bottom of pattern cavities 24 in the web side intended for contact with the underlying surface, in the manner shown, and holes of different sizes and/or with irregular positioning in the outer wheel- rim part can be used, in order to avoid undesirable resonance phenomena, among other things. The holes may have any desired shape and at least some of the holes may have the form of slots or slits, wherein the holes or the slits may have a diameter or a smallest cross-dimension of 1-20 mm. At least some of the holes on the side 23 of the outer wheel-rim part 14 facing towards the wheel centre may open into cavities having a shape and size selected for the absorption of noise within a determined frequency range. Noise reductions as high as 10 dBA have been obtained in practice with hole arrangements of the aforedescribed kind. The invention is not restricted to the embodiments described above with reference to the drawings, but can be realized in any desired manner within the scope of the inventive concept defined in the following Claims.

Claims: Claims 1. A non-pneumatic supporting wheel comprising a central part (10) and a wheel-rim (14-16) which is carried by said central part and which has an outer wheel-rim part (14, 15) which is intended to roll on an underlying surface, and an inner wheel-rim part (16) located radially inwards of said outer wheel-rim part, wherein at least the inner of the two wheel-rim parts is constructed from a plurality of curved elongated elements (16) which consist of a reilient material and which are mutually separated in the circumferential direction of the wheel, and wherein each of said elongated elements, when seen in a section taken diametrically through the wheel, present parts (17, 18) which are curved in opposite directions, and which elements, for the purpose of taking-up forces which, when the wheel is subjected to load, act substantially radially between the centre (11) of the wheel and a region (15) thereof in contact with the underlying surface, are elastically resilient in the radial direction of said wheel during increased bending of said elements, c h a ¬ r a c t e r i z e d in that the bendable elements (16) which are mutually spaced in the circumferential direction of the wheel are so constructed that both the sum of the bending of each small longitudinal section (Δl, , Δl , Δlj. ,' Δln) of the elements when said elements are sub- jected to load in the radial direction of the wheel, and the sum of the product of the bending of each such small section (Δl j. , Δln) and the distance (h j. , hn) of this section from the underlying surface when the wheel is subjected to normal load is at least substantially zero. 2. A supporting wheel according to Claim 1, c h a ¬ r a c t e r i z e d in that the elements or the parts thereof forming the inner wheel-rim part (16) of said wheel have, when seen in a section taken diametrically through the wheel, substantially the form of a recumbent S with the end (21) of one radially outwards convex part (17) located on one side of the wheel and connecting with the central part (10, 12, 13) of said wheel, and the end (22) of a radially inward convex part (18) connecting with the outer wheel-rim part (14, 15) on the opposite side of the wheel. 3. A supporting wheel according to Claim 1 or 2, c h a r a c t e r i z e d in that the outer wheel-rim part (14, 15) is formed at least partially by radially outer end parts (19) of the elongated elements (16) . 4. A supporting wheel according to Claim 3, c h a r a c t e r i z e d in that the end parts (19) of the elongated elements (16) forming the outer wheel- rim part, or included in said outer wheel-rim part, are embedded in a material (15) , for instance a rubber or plastic material, intended for contact with the under¬ lying surface. 5. A supporting wheel according to any one of Claims 1-4, c h a r a c t e r i z e d in that the outer wheel- rim part (14, 15) has the form of a circumferentially extending web which is provided with radially through- passing holes (20) , which are suitably from between 100 and 1,000 in number. 6. A supporting wheel according to Claim 5, c h a r a c t e r i z e d in that the combined area os the holes (20) lies between 2 and 50% of the total area of the web-side (15) intended for contact with the underlying surface, said combined hole-area being at least 3%, suitably at least 5% and preferably at least 7% of the area of said web-side (15) ; an in that the combined hole area is advantageously at most 30%, suitably at most 25% of said web-side (15) . 7. A supporting wheel according to Claim 5 or 6, c h a r a c t e r i z e d in that at least some of the holes (20) are arranged in the bottom of pattern cavi¬ ties (24) provided in the web-side (15) intended for contact with the underlying surface. 8. A supporting wheel according to any one of Claims 5-7, c h a r a c t e r i z e d by holes (20) of different sizes and/or of irregular positioning in the outer wheel-rim part (14, 15) . 9. A supporting wheel according to any one of Claims 5-8, c h a r a c t e r i z e d in that at least some of the holes (20) open out on that side (23) of the outer wheel-rim part (14, 15) which faces towards the centre of said wheel into cavities whose shape and size are selected for absorption of noise within a deter¬ mined frequency range. 10. A supporting wheel according to any one of Claims 5-9, c h a r a c t e r i z e d in that the holes (20) have a smallest cross-dimension of 1-20 mm, and in that at least some of the holes (20) may have the form of slits.

Inventors: HANSSON HANS-ERIK, HANSSON, HANS-ERIK
Applicants: HE HANSSON AB, HE HANSSON AKTIEBOLAG
Application year: 1991
Main classification: B60B5
IPC codes: B60B5, B60B9, B60B21, B60C7