JP2008273303A - Non-pneumatic tire - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a non-pneumatic tire which is free from any possibility of degradation or loss of the tire internal pressure, and easily adjusting the vertical rigidity, the longitudinal rigidity and the transverse rigidity of the tire as desired under the relationships independent from each other. <P>SOLUTION: The tire 1 is a non-pneumatic tire having a rim 2 and an elastic ring 3 arranged on the outer side of the rim 2 with a space therebetween. A plurality of link mechanisms 4 are arranged between the rim 2 and the ring 3 with a space formed along the circumferential direction. Each of the link mechanisms 4 has two links L1, L2 arranged with a space along the width direction. The link L1 (L2) comprises a first link member 4a to be rockingly connected to the rim 2 via a joint C1, and a second link member 4b to be rocking connected to the first link member 4a via a hinge connection part C2. The hinge connection part C2 is connected by an elastic means 5, the second link member 4b is integrally connected to the second link member 4b by a rocking segment 6 via a joint C3, and the segment 6 is joined with the elastic ring 3. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a non-pneumatic tire that does not need to be filled with pressurized air and can easily provide vertical rigidity, front-rear rigidity, and lateral rigidity having magnitudes according to the state of the vehicle.

  A pneumatic tire is generally used as a tire for an automobile or the like. However, a pneumatic tire has a problem that its filling air pressure decreases or disappears due to puncture or the like.

For this reason, for example, a solid tire having a solid structure has been proposed as a non-pneumatic tire that does not use air pressure (see, for example, Patent Document 1).
JP-A-6-293203

  However, solid tires are large in both weight and hardness, and cannot ensure sufficient riding comfort and maneuverability compared to pneumatic tires. Moreover, since rolling resistance also becomes large, it exists in the condition which is not used except for a special use.

  In contrast, pneumatic tires, which are important characteristics for tires, can be adjusted to some extent according to the type of vehicle, usage environment, driver requirements, etc. Each of them is difficult to adjust as desired under an independent relationship. In this specification, “rigidity” refers to the strength of elasticity against displacement deformation.

  The present invention has been made to solve these problems, and the object of the present invention is to eliminate the need for filling the tire with pressurized air or other gases, thereby reducing the tire internal pressure and the risk of disappearance. An object of the present invention is to provide a non-pneumatic tire that can be sufficiently removed and that can easily adjust the vertical and longitudinal rigidity, longitudinal rigidity, and lateral rigidity of the tire as desired under a mutually independent relationship.

  A non-pneumatic tire according to the present invention has a rim-like member connected to a rotating shaft, and an elastic ring arranged at intervals on the outside of the rim-like member, and extends in the circumferential direction and the meridian direction. A non-pneumatic tire that can be deformed and restored, and is provided with a plurality of link mechanisms that are arranged at intervals along the circumferential direction between the rim-like member and the elastic ring. Each of the links has two links arranged at intervals along the width direction, and each of the links is swingably connected to the rim-shaped member, and the first link member swings. The second link member is movably connected, and the connecting portion between the first link member and the second link member is connected by elastic means, and the second link member is connected to the second link member, respectively. Can swing against Be linked together by preparative, further it is characterized in that it has joined the segment to the elastic ring.

  In the present invention, “circumference”, “width”, and “radius” refer to “circumference”, “width”, and “radius” of a tire (also synonymous with a rim-like member or an elastic ring), and “meridian” The direction refers to a line along the external shape that appears when the tire is viewed in a cross section orthogonal to the circumferential direction.

  In the present invention, “the first link member is swingably connected to the rim-shaped member” means that at least the first link member has one end connected to the rim-shaped member and the one end is a base point. This means that it is only necessary to be able to swing in the circumferential direction and the width direction.

  For this reason, it is preferable to employ a universal joint (universal joint) that allows rocking in at least the circumferential direction and the width direction for the connection between the rim-shaped member and the first link member.

  In the present invention, “the second link member is swingably connected to the first link member” means that at least the second link member has one end connected to the other end of the first link member. This means that it is only necessary to be able to swing in the width direction around the one end.

  For this reason, although the hinge connection part which connects rotatably using a pin etc. can be employ | adopted for the connection of a 1st link and a 2nd link member, you may employ | adopt a universal joint.

  In the present invention, “the second link member is integrally connected to each of the second link members by a swingable segment,” means at least the free end (the other end) of the second link member. Each means that the other end rotates around the base and swings in the circumferential direction and is connected integrally by a segment swingable in the width direction.

  For this reason, a universal joint that allows at least the segment to rotate with respect to the second link member and swing in the circumferential direction and swing in the width direction is used to connect the second link member and the segment. It is preferable to do.

  In addition, the elastic means for connecting the connecting portions of the first link member and the second link member, respectively, is an elastic member having a natural length in an unloaded state, for example, a rubber elastic body, a fiber elastic reinforcement of a rubber elastic body , Coil springs, air springs and the like.

  Further, in addition to such elastic means, when the two links are oscillated and displaced in the circumferential direction independently of each other, a return means having a torsion spring member that provides rigidity with respect to the oscillating displacement and promotes return to the initial position. May be provided separately.

  Examples of the torsion spring member include a torsion spring, a rubber bush, and a torsion bar. When the return means is provided, the rim-like member and the elastic ring are subjected to relative displacement in the circumferential direction. The torsional reaction force can appropriately increase the longitudinal rigidity of the tire.

  In particular, when a torsion bar is used as the torsion spring member of the return means, a connecting rod is provided at each of the connecting portions of the two links, and these connecting rods are juxtaposed in the width direction via the moment arm, respectively. If connected to both ends of the bar, part of the function as elastic means can be achieved.

  In the present invention, the segment may include a plate member extending in the width direction and at least two bracket portions provided at intervals along the extending direction of the plate member.

  Moreover, according to this invention, it is preferable to provide the said bracket part in the inner surface of the said plate member, and to join an elastic ring to the outer surface of the said plate member.

  The segment may be formed by arranging a plurality of plate members at intervals along the circumferential direction.

  Moreover, the said plate member shall be joined in the state installed vertically to at least one of the front surface and rear surface of these bracket parts.

  Furthermore, the plate member may include reinforcing plates at both ends in the width direction.

  Moreover, according to this invention, the notch which forms a clearance gap between the said plate member or the said elastic ring can be provided in the outer surface of the said bracket part.

  Furthermore, according to this invention, it is preferable that the said elastic ring has a groove | channel extended in the circumferential direction, and arrange | positions the said bracket part in the position aligned with the said groove | channel.

  According to the present invention, by providing a plurality of link mechanisms at intervals along the circumferential direction between the elastic ring and the rim-like member, filling with pressurized air or other gas becomes unnecessary. Further, it is possible to sufficiently eliminate the fear of a decrease or disappearance of the tire internal pressure. Further, according to the present invention, the connecting portions of the first link member and the second link member are connected by the elastic means, respectively, so that the vertical rigidity, the longitudinal rigidity, and the lateral rigidity of the tire are independent from each other. Below, it can be easily adjusted as desired.

  Furthermore, according to the present invention, the second link member is integrally connected to each other by a swingable segment with respect to the second link member, and further, the segment is joined to the elastic ring, so that the circumferential direction As the whole tire functions as a single unit, the gripping force is improved by ensuring a larger contact area, In this case, the ground pressure distribution can be made more uniform.

  Further, in the present invention, if the segment includes a plate member extending in the width direction and at least two bracket portions provided at intervals along the extending direction of the plate member, the segment is simple. With this configuration, it is possible to achieve uniform contact pressure distribution while reducing the weight of the entire tire.

  Further, according to the present invention, the arrangement of the bracket portion with respect to the plate member and the arrangement of the elastic ring with respect to the plate member can be selected as appropriate, but the bracket portion is arranged on the inner surface of the plate member (a surface located on the radially inner side). If the elastic ring is joined to the outer surface of the plate member (the surface located on the outer side in the radial direction), the surface pressure from the elastic ring can be transmitted directly from the plate member to the link mechanism, thereby ensuring a larger installation area. Thus, a more uniform contact pressure distribution can be efficiently realized.

  By the way, when a plate member is used for the segment, the front surface (the surface located on one side in the circumferential direction) or the rear surface (the surface located on the other side in the circumferential direction) of each plate member When moving, it is preferable not to interfere with the elastic ring as an edge.

  In view of this, the plate member used for the segment may have a curved shape so that the vicinity of the center in the circumferential direction becomes a minute convex toward the outside in the radial direction.

  However, if the shape of the plate member is curved so that the vicinity of the center in the circumferential direction is slightly convex outward in the radial direction, the vicinity of the center in the circumferential direction may be deformed radially inward. It is done.

  Accordingly, in the present invention, if a plurality of plate members are used and spaced apart along the circumferential direction, the concentration of the ground pressure that occurs near the center in the circumferential direction is alleviated. Distribution can be realized.

  In addition, the plate member can be provided at various positions of the bracket part, but the front part (surface located on one side in the circumferential direction) and the rear part (the other side in the circumferential direction) of the bracket part. If the plate member is joined in a state in which it is vertically placed, the rigidity of the plate member against bending in the thickness direction (radial direction) along the longitudinal direction (width direction) is secured. A uniform contact pressure distribution can be realized.

  Further, in the present invention, if reinforcing plates are provided at both ends of the plate member in the width direction, the plate member is secured against bending in the thickness direction (radial direction) along the short direction (circumferential direction). Therefore, a more uniform contact pressure distribution can be realized.

  Further, according to the present invention, the notch that forms a gap between the plate member or the elastic ring is provided on the outer surface of the bracket portion, so that the plate member is arranged at intervals along the circumferential direction. As in the case of (Claim 4), since the concentration of the contact pressure generated near the center in the circumferential direction is relieved, a more uniform contact pressure distribution can be realized.

  In addition, if the elastic ring has a groove extending in the circumferential direction, and the bracket portion is arranged at a position aligned with the groove, the ground pressure due to the transmission of the ground pressure from the tread portion directly to the bracket portion. Since the concentration of is relaxed, a more uniform contact pressure distribution can be realized.

  Hereinafter, a non-pneumatic tire according to the present invention will be described in detail with reference to the drawings.

  1A and 1B are a perspective view schematically showing a mechanical tire (hereinafter referred to as “tire”) 1 which is an embodiment of the present invention, and a tire 1 shown in FIG. It is a perspective view which shows typically the state which removed the elastic ring 3. FIG. 2A and 2B are a perspective view schematically showing a state in which a later-described segment is removed from the state shown in FIG. 1B, and a cross-sectional view taken along line AA in FIG.

  In FIG. 1, reference numeral 2 denotes a cylindrical rim-like member (hereinafter referred to as “rim”) connected to an axle (rotary shaft). The rim 2 is made of a metal material such as aluminum or an aluminum alloy.

  Reference numeral 3 denotes an elastic ring that is disposed outside the rim 2 with a space therebetween. This elastic ring 3 corresponds to a tire in its original meaning. The elastic ring 3 according to the present embodiment has a planar shape including only a crown portion. However, similarly to the tire in the original sense, a shoulder portion and a side portion may be provided to be wound inside the rim 2. Good.

  Reference numeral 4 denotes a plurality of link mechanisms arranged at intervals along the circumferential direction S (of the tire 1) between the rim 2 and the elastic ring 3. As shown in FIG. 2, each of the link mechanisms 4 has two links L1 and L2 that are spaced apart along the width direction W (of the tire 1).

  As shown in FIG. 2 (b), the link L1 has a first end portion connected to the side surface portion of the rim 2 via a universal joint C1, and is swingable with the universal joint C1 at the one end portion as a base point. The link member 4a and a second link member that has one end connected to the other end of the first link member 4a via a hinge connecting portion C2 and can swing around the hinge connecting portion C2 of the one end 4b, and is made of a metal material such as aluminum or an aluminum alloy.

  Similarly, the link L2 is a first link member 4a connected to the rim 2 via a universal joint C1, and a second link connected to the first link member 4a so as to be swingable via a hinge connecting portion C2. And a member 4b, and is made of a metal material such as aluminum or an aluminum alloy.

  The universal joint C1 connects the rim 2 and the first link member 4a so as to allow at least the first link member 4a to swing in the circumferential direction S and the width direction W, and is made of aluminum or aluminum alloy. It is made of a metal material.

  Further, the hinge connecting portion C2 is, for example, for connecting the first link member 4a and the second link member 4b so as to be rotatable using a pin, and the rotation direction thereof is the first link member 4a and the second link. This is a direction in which the member 4b is swung in the width direction W. The hinge connecting portion C2 is also made of a metal material such as aluminum or aluminum alloy, and may be replaced with a universal joint C1.

  Reference numeral 5 denotes an elastic means for connecting the hinge connecting portion C2 of the link L1 and the hinge connecting portion C2 of the link L2. The elastic means 5 has a required rigidity (for example, vehicle type, usage environment, or Rigidity) determined by the driver's request.

  The elastic means 5 is an elastic member having a natural length in which no compression reaction force or tensile reaction force is generated in a state where there is no load on the tire 1 (no load state), for example, a rubber elastic body or a rubber elastic body. Reinforced ones, coil springs, air springs and the like can be mentioned, and one of these can be used alone, or two or more of these can be combined.

  Reference numeral 6 denotes a segment that integrally connects the other end of the second link member 4b via a universal joint C3 so as to be swingable.

  As shown in FIG. 2 (b), the segment 6 includes a plate member 6a extending in the width direction W and two bracket portions 6b provided integrally with a space along the extending direction of the plate member 6a. It is comprised with metal materials, such as aluminum and aluminum alloy.

  The universal joint C3 is the same as the universal joint C1, and at least the segment 6 rotates with respect to the second link member 4b and swings in the circumferential direction S and swings in the width direction W. The second link member 4b and the bracket portion 6b are connected so as to allow.

  That is, the link mechanism 4 includes links L1, l2 connected to the rim 2, elastic means 5 for associating the links L1, l2, and a segment 6. The outer surface of the plate member 6a of the segment 6 (surface located radially outward). The elastic ring 3 is joined to f1.

  In joining the segment 6 to the elastic ring 3, the size of the segment 6 or the arrangement of the link mechanism 4 is determined so that the adjacent segments 6 form a small gap along the circumferential direction.

  Thus, each of the link mechanisms 4 holds the elastic ring 5 with a small gap along the circumferential direction by the segment 6. It should be noted that the allowance interval can be appropriately set according to the vehicle type, usage environment, driver's request, and the like.

  Therefore, for example, when the rim 2 and the elastic ring 3 are displaced so as to approach each other along the radial direction R, as indicated by the phantom line, immediately below the load, from the state shown by the solid line in FIG. The links L1 and L2 are bent so as to approach each other with the hinge connecting portion C2 as a base point, and the elastic means 5 is compressed and deformed in the width direction W.

  However, the compressive deformation of the elastic means 5 simultaneously applies a reaction force that separates the links L1 and L2 to the hinge connecting portion C2. That is, each of the link mechanisms 4 can generate the required vertical rigidity (rigidity in the radial direction) when the rim 2 and the elastic ring 3 approach in the radial direction R due to the presence of the elastic means 5.

  3B, when the rim 2 and the elastic ring 3 are displaced relative to each other along the circumferential direction S as indicated by the phantom line, the entire link mechanism 4 is extended. Directly, the total length of the links L1 and L2 is increased, thereby causing the elastic means 5 to undergo tensile deformation.

  However, the tensile deformation of the elastic means 5 simultaneously causes a reaction force that causes the links L1 and L2 to approach the circumferential direction S to act on the hinge connecting portion C2. That is, each of the link mechanisms 4 causes the required longitudinal rigidity (rigidity in the circumferential direction) when the rim 2 and the elastic ring 3 are relatively displaced in the circumferential direction S due to the presence of the elastic means 5. it can.

  3C, when the rim 2 and the elastic ring 3 are relatively displaced in the width direction W as shown by the phantom line, the entire link mechanism 4 is oscillated and displaced. Directly, the links L1 and L2 are oscillated and displaced with the universal joint C1 and the hinge connecting portion C2 as base points, thereby causing the elastic means 5 to be tensilely deformed.

  However, the tensile deformation of the elastic means 5 simultaneously causes a reaction force that causes the links L1 and L2 to approach in the width direction W to act on the hinge connecting portion C2. That is, each of the link mechanisms 4 can generate required lateral rigidity (stiffness in the width direction) when the rim 2 and the elastic ring 3 are relatively displaced in the width direction due to the presence of the elastic means 5.

  In the above description, the case where displacements in the circumferential direction S, the width direction W, and the radial direction R are independently generated between the rim 2 and the elastic ring 3 has been described. Of course, even if two or more of these relative displacements occur at the same time, the tire can provide the required rigidity as a composite at the same time.

  In addition, according to the tire 1, each of the link mechanisms 4 functions independently of each other while each of the plurality of link mechanisms 4 holds the elastic ring 5 at a small interval along the circumferential direction. Therefore, when a large load is applied to the elastic ring 3 due to load rolling of the tire 1 or the like, the individual link mechanisms 4 oscillate / displace around the plurality of link mechanisms 4 in that portion. A larger ground contact area can be secured while suppressing the bias.

  That is, according to the tire 1, a plurality of link mechanisms 4 are provided between the rim 2 and the elastic ring 3 at intervals along the circumferential direction S, so that pressurized air or other gas filling is unnecessary. As a result, the fear of a decrease or disappearance of the tire internal pressure can be sufficiently removed. Further, according to the tire 1, the hinge connecting portions C2 are connected by the elastic means 5, respectively, so that the vertical stiffness, the longitudinal stiffness, and the lateral stiffness of the tire 1 can be simply and as desired in a relationship independent of each other. Can be adjusted.

  Further, according to the tire 1, the other end of the second link member 4b is rotated with the universal joint C3 as a base point, and the other end of the second link member 4b swings in the circumferential direction and can swing in the width direction. In addition, the segments 6 are joined to the elastic ring 3 so that the link mechanisms 4 arranged at intervals along the circumferential direction S can function independently of each other. Since the whole 1 functions as a single body, a larger ground contact area is ensured to improve gripping force, and the ground pressure distribution in that case can be made more uniform.

  In this embodiment, the segment 6 has a plate member 6a extending in the width direction W and two bracket portions 6b provided at intervals along the extending direction of the plate member 6a. Thus, the ground pressure distribution can be made uniform while reducing the weight of the entire tire 1 with a simple configuration.

  4 (a) to 4 (c) are perspective views showing the second form of the segment 6 from the outer surface f1 of the plate member 6a, and from the inner surface (surface located radially inside) f2 of the plate member 6a. It is the side view shown from the perspective view and width direction W which show.

  In the following description of each embodiment, the same parts as those in FIGS.

  The segment 6 of this embodiment is composed of four bracket portions 6b, and each bracket portion 6b is provided with a bearing B that receives the shaft of the universal joint C3.

  By the way, according to the present invention, the arrangement of the bracket portion 6b with respect to the plate member 6a and the arrangement of the elastic ring 3 with respect to the plate member 6a can be appropriately selected. By providing the inner surface f2 of the plate member 6a and joining the elastic ring 3 to the outer surface f1 of the plate member 6a, the surface pressure from the elastic ring 3 can be transmitted directly from the plate member 6a to the link mechanism 4, so a larger installation area. And more uniform contact pressure distribution can be efficiently realized.

  5 (a) to 5 (c) are perspective views showing the third form of the segment 6 from the outer surface f1 of the plate member 6a, a perspective view showing the inner surface f2 of the plate member 6a, and a width direction W, respectively. FIG.

  The segment 6 of the present embodiment is formed by joining two plate members 6a along the circumferential direction S with four bracket portions 6b with an interval ΔX1.

  When the plate member 6a is used for the segment 6, the front surface (surface located on one side in the circumferential direction) e1 (see FIG. 4) or the rear surface (positioned on the other circumferential side) of the plate member 6a. It is preferable that e2 (see FIG. 4) does not interfere with the elastic ring 3 as an edge when the tire 1 rolls.

  Therefore, the plate member 6a employed in the segment 6 may be formed in a shape curved with a large curvature radius r so that the vicinity of the center in the circumferential direction becomes a minute convex toward the outside in the radial direction R. (See FIG. 4 (c)).

  However, when the shape of the plate member 6a is curved so that the vicinity of the center in the circumferential direction becomes a minute convex toward the outside of the radial direction R, the vicinity of the center in the circumferential direction S is caused by the ground pressure. It is also conceivable to deform inward in the radial direction R.

  Therefore, as in this embodiment, if the two plate members 6a are used and arranged with a gap ΔX1 along the circumferential direction S, the concentration of the contact pressure generated near the center in the circumferential direction S is alleviated. A more uniform contact pressure distribution can be realized.

  6A to 6C are perspective views showing the fourth to sixth forms of the segment 6 from the inner surface f2 of the plate member 6a.

  The plate member 6a can be provided at various positions on the bracket portion 6b. However, the plate member 6a in FIG. 6A is a front portion of these bracket portions 6b (a surface located on one side in the circumferential direction). ) And the rear part (surface located on the other side in the circumferential direction) are joined in a vertically placed state.

  Moreover, the segment 6 of FIG.6 (b) makes the plate member 6a an angle iron-like thing, and enlarged the surface area of the outer surface f1 to which the elastic ring 3 is joined, Furthermore, FIG.6 (c) The plate member 6a is formed into a grooved steel shape having a U-shaped cross section (including a U shape).

  6 (a) to 6 (c), the plate member 6a is bent in the thickness direction (radial direction R) along the longitudinal direction (width direction W), particularly in the outer surface side direction (outside of the radial direction R). ) (See arrow M in FIG. 4A) is ensured, and a more uniform contact pressure distribution can be realized.

  In order to place the plate member 6a vertically, it is preferable to provide the plate member 6a on both the front part and the rear part of the plate member 6a. However, at least one of the front part and the rear part may be provided.

  7 (a) and 7 (b) are perspective views showing the seventh form of the segment 6 from the inner surface f2 of the plate member 6a. FIGS. FIG. 16 is a perspective view showing the eighth form from the inner surface f2 of the plate member 6a.

  The segment 6 in FIG. 7 is provided with reinforcing plates 6s that are integrally connected to each other in the width direction W of the plate member 6a in FIG. 6B, and the segment 6 in FIG. Reinforcing plates 6s are integrally provided at both ends in the width direction W of the plate member 6a in FIG. 6 (c).

  If a reinforcing plate 6s is provided at the end in the width direction W of the plate member 6a as shown in FIGS. 7 and 8, the plate member 6a is bent in the thickness direction along the short direction (circumferential direction S). Therefore, a more uniform contact pressure distribution can be realized.

  In order to provide the reinforcing plate 6s at the end in the width direction W of the plate member 6a, it is preferable to provide it at both ends of the plate member 6a, but it may be provided at at least one of both ends.

  Further, according to the present invention, a notch can be provided on the outer surface of the bracket portion 6a.

  FIGS. 9A to 9G are side views each showing a form in which a notch C is provided in the segment 6 shown in FIGS.

  In the segment 6 of FIG. 9A, the notch C is provided on the outer surface of the bracket portion 6b, thereby forming a gap ΔX2 extending along the width direction W between the plate member 6a.

  In each segment 6 of FIGS. 9B and 9C, a notch C is provided on the outer surface of the bracket portion 6b, so that a gap ΔX3 extending along the width direction W is formed between the elastic ring 3 and each other. Form.

  In the segment 6 of FIG. 9D, the notch C is provided on the outer surface of the bracket portion 6b, thereby forming a gap ΔX2 extending along the width direction W between the plate member 6a.

  In each segment 6 of FIGS. 9 (e) and 9 (f), a notch C is provided on the outer surface of the bracket portion 6b, so that a gap ΔX3 extending along the width direction W is formed between the elastic ring 3 and each other. Form. FIG. 10 is a perspective view showing the segment 6 of FIG. 9F from the outer surface f1 of the plate member 6a.

  In the segment 6 of FIG. 9 (g), a notch C is provided on the outer surface of the bracket portion 6b, thereby forming a gap ΔX2 extending along the width direction W between the plate member 6a.

  According to each form of FIG. 9, the notch C which forms clearance gap (DELTA) X2 or (DELTA) X3 between the plate member 6a or the elastic ring 3 is provided in the outer surface of the bracket part 6b, and the plate member 6a is made into a circumference. Similar to the case where the gap ΔX2 is arranged along the direction S (claim 4), the concentration of the contact pressure generated near the center in the circumferential direction S is alleviated, so that a more uniform contact pressure distribution can be realized.

  Next, FIGS. 11 (a) and 11 (b) are a perspective view schematically showing the tire 1 in which a plurality of tread portions 3a are formed on the surface of the elastic ring 3, and an AA cross section of FIG. 11 (a). It is principal part sectional drawing.

  In the tire 1 according to this embodiment, the elastic ring 3 has a plurality of grooves 3b extending in the circumferential direction S to define a plurality of tread portions 3a, as shown in FIG. 11 (a). As shown in b), the bracket portion 3b is arranged with respect to the plate member 6a so as to align with the groove 3b.

  If the elastic ring 3 has a groove 3b extending in the circumferential direction S as in this embodiment, and the bracket portion 6b is arranged at a position aligned with the groove 3b as shown in FIG. Since the concentration of the ground pressure accompanying the transmission of the ground pressure from the portion 3a directly to the bracket portion 6b is alleviated, a more uniform ground pressure distribution can be realized.

  By the way, in the link mechanism 4, as indicated by reference numeral 4 ′ in FIG. 12, the hinge connecting portions C <b> 2 of the links L <b> 1 and L <b> 2 protrude outward in the width direction W, contrary to the form shown in FIG. It can also be set as the structure to do.

  In this case, when the rim 2 and the segment 6 (elastic ring 3) are displaced so as to approach each other along the radial direction R, the links L1 and L2 bend away from each other with the hinge connecting portion C2 as a base point, and are elastic. The means 5 is pulled and deformed in the width direction W. This tensile deformation simultaneously applies a reaction force that causes the links L1 and L2 to approach the hinge connecting portion C2. For this reason, when the rim 2 and the elastic ring 3 approach each other in the radial direction R, the link mechanisms 4 ′ can also generate required vertical rigidity.

  Further, when the rim 2 and the elastic ring 3 are relatively displaced in the circumferential direction S, the entire link mechanism 4 'is extended to cause the elastic means 5 to undergo compressive deformation. This compressive deformation is simultaneously performed by the link L1. , A reaction force that causes L2 to move away from each other in the circumferential direction S is applied to the hinge connecting portion C2. For this reason, when the rim 2 and the elastic ring 3 are relatively displaced in the circumferential direction S, the link mechanism 4 ′ can also generate the required longitudinal rigidity.

  Then, when the rim 2 and the elastic ring 3 are relatively displaced in the width direction W, the entire link mechanism 4 ′ is oscillated and displaced, thereby causing the elastic means 5 to undergo compressive deformation. A reaction force for separating L1 and L2 in the width direction W is applied to the hinge connecting portion C2. For this reason, when the rim 2 and the elastic ring 3 are relatively displaced in the width direction W, the link mechanism 4 ′ can also generate the required lateral rigidity.

  Furthermore, according to the tire of the present invention, in addition to the elastic means 5, when the two links L1 and L2 are oscillated and displaced in the circumferential direction S independently of each other, rigidity is provided for the oscillating displacement. A torsion spring member may be separately provided as a return means for urging return to the initial positions of L1 and L2.

  The return means includes the first link member 4a and the second link member 4b at the hinge connection part C2 of at least one of the link L1 and the link L2 or at least one of the link L1 and the link L2. Of at least one of the above.

  Examples of the torsion spring member include a torsion spring, a rubber bush, and a torsion bar. When a return means is provided, the rim 2 and the elastic ring 3 are circumferentially arranged as will be described later with reference to FIG. In the relative displacement in the direction S, the torsional reaction force of the torsion spring member 7 can appropriately increase the longitudinal rigidity of the tire 1, which is a relative displacement opposite to the direction shown in FIG. The same applies to.

  FIG. 13 is a perspective view of a main part showing a form in which a return means 7 is added to the tire 1 of FIG. 1 and a torsion bar 8 is adopted as a torsion spring member 7a of the return means 7. FIG.

  When the torsion bar 8 is employed, connecting rods 7b are provided at the connecting portions C1 and C2 of the two links L1 and L2, respectively, and these connecting rods 7b are juxtaposed in the width direction via the moment arm 7c. The bar 8 is connected to both ends. Reference symbol C4 is a ball joint.

  In this case, when the rim 2 and the elastic ring 3 are relatively displaced from the state shown by the solid line in FIG. 14 (a) in the width direction W as shown by the phantom line, the hinge connecting portion C2 of the link L1 and the link L1 A change in height along the radial direction R as indicated by the phantom line occurs in the hinge connecting portion C2, and the torsion bar 12 is twisted and deformed as shown in FIG. 14 (b).

  However, the torsion bar 8 simultaneously applies a reaction force against this torsional deformation to the hinge connecting portion C2. That is, the return means 7 increases the lateral rigidity of the tire 1 as required when the rim 2 and the elastic ring 3 are relatively displaced in the width direction W due to the presence of the torsion bar 8 as a torsion spring member. Can do. Of course, the torsion bar 8 can function in the same manner for occurrence of relative displacement in the width direction opposite to that shown in the figure.

  Further, in relation to the use of the torsion spring member, the tire according to the present invention is adapted to the swing displacement in the meridian direction of the links L1 and L2 at the hinge connecting portion C2 instead of providing the elastic means 5, respectively. It is also possible to provide a torsion spring member (not shown) that provides rigidity to the device.

  In this case, when the rim 2 and the elastic ring 3 are displaced close to each other in the radial direction R, the length of the link L1 and the link L2 in the radial direction R is shortened, so that the torsion spring member generates a torsional reaction force. In addition, when the rim 2 and the elastic ring 3 are relatively displaced in the circumferential direction S, conversely, the torsion spring member generates a torsional reaction force by increasing the total length of the link L1 and the link L2. Then, when the rim 2 and the elastic ring 3 are relatively displaced in the width direction W, the link intersection angle at the hinge connecting portions C1 and C2 of the link L1 and the link L2 is shown in FIGS. 3 (c) and 14 (a). ), Each of the torsion spring members generates a torsional reaction force, thereby providing vertical rigidity, longitudinal rigidity, and lateral rigidity.

  That is, when the hinge connecting portion C2 is restricted by the torsion spring member instead of the elastic means 5, the tire 1 is required to be based on the swinging displacement of the links L1 and L2 as in the case where the elastic means 5 is restricted. Vertical rigidity, longitudinal rigidity and lateral rigidity can be provided.

  Further, in such a tire in which the hinge connecting portion C2 is replaced with a torsion spring member (not shown), when the two links L1 and L2 swing and displace in the circumferential direction S independently of each other, the swing displacement is not affected. When a torsion spring member is provided that provides rigidity and facilitates the return of each of the links L1 and L2 to the initial position, the circumferential direction S between the rim 2 and the elastic ring 3 as shown in FIG. With respect to relative displacement, the torsional reaction force generated in the torsion spring member can increase the longitudinal rigidity of the tire as required.

  Here, instead of or in addition to the torsion spring member as the return means described above, the return means 7 using the torsion bar 8 described in FIG. 13 as the torsion spring member 7a can be further added. Accordingly, as described in FIG. 14, the lateral rigidity of the tire can be appropriately increased by the torsional reaction force generated in the torsion bar 8.

  Further, when the return means 7 shown in FIG. 13 is employed, each of the link mechanisms 4 is replaced with the elastic means 5 in the radial direction R and the circumferential direction S of the rim 2 and the elastic ring 3, respectively. Appropriate elastic means for providing rigidity with respect to the relative displacement can be provided independently. That is, the tire in this embodiment corresponds to one in which one elastic means 5 in FIG. 13 is replaced with appropriate elastic means (not shown) that regulates three directions.

  Also here, the elastic means is arranged at one end of the link member 4a, 4b of each of the links L1, L2, respectively, in the circumferential direction, the width direction and the radial direction, Alternatively, it can be constituted by a torsion spring member that provides rigidity with respect to both the meridional direction and the circumferential displacement, and one end portion of any one of the link members 4a and 4b of each of the links L1 and L2. And a torsion spring member that provides rigidity against swing displacement in the meridian direction of the link and a connection portion of one end of the other link member, It can also be configured by each of the other torsion spring members that provide rigidity against dynamic displacement.

  For this reason, in this tire, each of the vertical rigidity and the longitudinal rigidity of the tire can be brought about by a deformation reaction force of elastic means made of a torsion spring member or the like, and the lateral rigidity is brought about by a torsion reaction force of the torsion bar 8. be able to.

  Although the above description is to describe the preferred embodiment of the present invention, various modifications can be made within the scope of the claims. For example, the above-described embodiments and various configurations included therein can be appropriately combined according to the vehicle type, usage environment, driver's request, or the like.

  Comparative Example 1 shows a state in which a load of 4.0 kN is applied to a conventional pneumatic tire (filling air pressure 230 kPa) having a size of 225 / 55ZR17, and a load of 4.0 kN is applied to a mechanical tire of the same size in which segments are connected in an annular shape. When the ground contact area and the ground pressure standard deviation in a state where a load of 4.0 kN was applied were obtained for each Example of the mechanical tire of the same size according to the present invention with the state as Comparative Example 2, the results shown in Table 1 were obtained. It was.

  Here, in Examples 1 to 3, the result of the tire 1 shown in FIG. 1 with the segment 6 shown in FIG. 4 applied and a load of 4.0 kN applied, and the tire 1 shown in FIG. The result of using the segment 6 of b) with a load of 4.0 kN, and the tire 1 shown in FIG. 1 adopting the segment 6 shown in FIG. 9 (f) (FIG. 10) and the load of 4.0 kN. It is a result in the state which loaded.

  In addition, the ground contact area and the ground pressure standard deviation shown in Table 1 are expressed as a ratio when the value in Comparative Example 1 is 100. In the ground contact area, the larger the value, the wider the ground contact area. The ground pressure standard deviation is evaluated as a good state, and as the numerical value is smaller, the ground pressure distribution is evaluated to be more uniform.

  As apparent from Table 1, according to the tire according to the present invention, it is possible to secure a wide contact area as compared with the pneumatic tire and to make the contact pressure distribution uniform. In addition, it is clear that a large contact area can be secured while maintaining a substantially uniform contact pressure distribution even when the segments are connected in a ring shape.

  The present invention can be applied as a wheel of a vehicle such as a passenger car, a truck, a work vehicle such as a crane or a power shovel, or a carriage on which luggage or the like is loaded.

(a), (b) is the perspective view which shows typically the mechanical tire which is one form of this invention, and shows the state which removed the below-mentioned elastic ring from the tire 1 of the figure (a), respectively. It is a perspective view. (a), (b) is the perspective view which shows typically the state which removed the below-mentioned segment from the state of FIG.1 (b), and AA sectional drawing of FIG. (a) to (c) are skeleton diagrams for explaining the vertical rigidity generated in the tire of the same form when a load is applied directly from an unloaded state, and the longitudinal rigidity generated in the tire of the same form is described. It is a skeleton figure explaining the right-and-left rigidity which generate | occur | produces in the tire skeleton figure and tire of the same form. (a)-(c) is the perspective view which shows the 2nd form of the segment based on this invention from the outer surface of a plate member, the perspective view shown from the inner surface of a plate member, and the side view shown from the width direction, respectively. (a)-(c) is the perspective view which shows the 3rd form of the segment based on this invention from the outer surface of a plate member, the perspective view shown from the inner surface of a plate member, and the side view shown from the width direction, respectively. (a)-(c) is a perspective view which respectively shows the 4th-6th form of the segment which concerns on this invention from the inner surface of a plate member. (a), (b) is a perspective view which respectively shows the 7th form of the segment based on this invention from the inner surface of a plate member. (a), (b) is a perspective view which respectively shows the 8th form of the segment based on this invention from the inner surface of a plate member. (a)-(g) is a side view which shows the form which provided the notch in the segment shown to FIGS. 4-8, respectively. FIG. 10 is a perspective view showing the segment of FIG. 9F from the outer surface of the plate member. (a), (b) is the perspective view which shows typically the tire which concerns on this invention which formed the several tread part on the surface of the elastic ring, respectively, and the principal part cross section in the AA cross section of the same figure (a) FIG. It is a partial cross section figure which shows typically the other form of the link mechanism employ | adopted as the tire which concerns on this invention. FIG. 2 is a perspective view of an essential part showing a form in which a return means employing a torsion bar as a torsion spring member is provided on the tire shown in FIG. 1. FIGS. 14A and 14B are a skeleton diagram for explaining left-right rigidity generated in the tire of FIG. 13 and a skeleton diagram for explaining a force relationship acting on a torsion bar according to the tire of FIG.

Explanation of symbols

1 Mechanical tire (non-pneumatic tire)
2 Rim-shaped member 3 Elastic ring 4 Link mechanism
4a First link member
4b Second link member 5 Elastic means 6 Segment
6a Plate material
6b Bracket (bearing base)
7 Return means
7a (8) Torsion bar
7b connecting rod
7c Moment arm
C1 universal joint
C2 Hinge connection
C3 universal joint
C4 ball joint
L1, L2 link
f1 Plate member outer surface
f2 Plate member inner surface

Claims (8)

Non-pneumatic that has a rim-like member connected to the rotating shaft and an elastic ring that is spaced apart from the rim-like member and that can be deformed and restored in the circumferential and meridian directions Tire,
Provided with a plurality of link mechanisms arranged at intervals along the circumferential direction between the rim-shaped member and the elastic ring,
Each of the link mechanisms has two links spaced apart along the width direction,
Each of the links includes a first link member that is swingably connected to the rim-like member, and a second link member that is swingably connected to the first link member.
Each of the connecting portions of the first link member and the second link member is connected by elastic means,
Each of the second link members is integrally connected with a swingable segment with respect to the second link member,
Furthermore, the non-pneumatic tire characterized by joining the said segment to the elastic ring.   The non-pneumatic tire according to claim 1, wherein the segment includes a plate member extending in the width direction and at least two bracket portions provided at intervals along the extending direction of the plate member.   The non-pneumatic tire according to claim 2, wherein the bracket portion is provided on an inner surface of the plate member, and an elastic ring is joined to the outer surface of the plate member.   The non-pneumatic tire according to claim 2 or 3, wherein the segment is formed by arranging a plurality of plate members at intervals along the circumferential direction.   The non-pneumatic tire according to any one of claims 1 to 4, wherein the plate member is joined in a state of being placed vertically on at least one of a front surface and a rear surface of the bracket portion.   The non-pneumatic tire according to any one of claims 2 to 5, wherein the plate member includes reinforcing plates at both ends in the width direction.   The non-pneumatic tire according to any one of claims 2 to 6, further comprising a notch that forms a gap between the plate member and the elastic ring on an outer surface of the bracket portion.   The non-pneumatic tire according to any one of claims 2 to 7, wherein the elastic ring has a groove extending in a circumferential direction, and the bracket portion is arranged at a position aligned with the groove.

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