Patent Application
20100326579
The present invention relates to a studless tire to be attached to a vehicle for running on icy and snowy roads, and particularly to one capable of improving straight-running stability.
In order to enhance a driving performance on icy and snowy roads while maintaining drivability on dry roads, a studless tire is provided with multiple sipes and/or made of extremely soft rubber to suppress the tread rigidity (see JP 2007176417 A).
However, due to the low tread rigidity, the studless tire does not have sufficient straight-running stability, for which an improvement is demanded. However, if the tread rigidity is improved to be higher, a required driving performance on icy and snowy roads cannot be achieved.
The present invention addresses these drawbacks, and is intended to provide a studless tire capable of enhancing straight-running stability with a low tread rigidity.
In order to realize the above-mentioned object, a studless tire according to the present invention comprises an inner half portion and an outer half portion in a width direction of a vehicle under a condition where the tire is attached to the vehicle, wherein sectional shapes of the inner and outer half portions are formed so as to have a degree of asymmetricity within a given range. Such asymmetric tires have been known as summer tires, but have not yet realized as studless tires. High driving performances on icy and snowy roads are required for studless tires, so that modulus of elasticity of winter tires is remarkably smaller than that of summer tires. It is, therefore, difficult for studless tires to employ the means for asymmetrization applied to summer tires as it is. The object of the present is, thus, to provide a asymmetrizing means which is capable of enhancing a straight-running stability and further optimum for studless tires having remarkably low tread rigidities.
<1> A studless tire according to the present invention is characterized in that, in a section passing a central axis line under a condition where the tire is mounted on a predetermined rim and a predetermined inner pressure is charged therein, assuming that a distance A is measured from a position where a bladder ring is divided to a position where a maximum tire width is obtained along the tire radial direction and a distance B is measured from the position where the bladder ring is divided to a position where a tread ring is divide along the tire radial direction, a side-shape coefficient of the tire defined as a ratio A/B in a state where the tire is installed on a vehicle is between 0.52 and 0.55 in a widthwise half portion disposed at a widthwise outer side of the vehicle (hereinafter referred to as “vehicle installation outer side”) and between 0.45 and 0.50 in a widthwise half portion disposed at a widthwise inner side of the vehicle (hereinafter referred to as “vehicle installation inner side”), or between 0.5 and 0.55 in a widthwise half portion disposed at the vehicle installation outer side and between 0.45 and 0.48 in a widthwise half portion disposed at the vehicle installation inner side.
<2> In the studless tire described in <1>, a periphery length along an inner surface of the tire is preferably longer in the widthwise half portion in the vehicle installation outer side and shorter in the widthwise half portion in the vehicle installation outer side, and a difference between the periphery lengths is not more than 2%.
<3> In the studless tire described in <1> or <2>, it is preferred that a degree of asymmetricity of a side-shape X expressed by equation (1) and a degree of asymmetricity of a contact-shape Y expressed by equation (2) satisfy a relationship expressed by equation (3):
where Xd is a side-shape coefficient of the vehicle installation outer side, Xc is a side-shape coefficient of the vehicle installation inner side, C and D are ground contact lengths of a ground contact surface of the tire at the vehicle installation inner side and the vehicle installation outer side, respectively, measured at positions spaced 40% of a ground contact width from the width center of the ground contact surface under a condition that the tire contacts the ground with a camber angle of −0.5 degree while the predetermined inner pressure and a predetermined load are applied thereto.
According to the tire described in <1>, the degree of asymmetricity of the side-shape X is between 1.0 and 5.0, so that as described hereinafter in detail, straight-running stability can be improved without causing uneven wear.
According to the tire describe in <2>, the periphery length along the inner surface of the tire is longer in the widthwise half portion in the vehicle installation outer side and shorter in the widthwise half portion in the vehicle installation outer side, so that as described hereinafter in detail, straight-running stability can be further improved. Moreover, a difference between the periphery lengths at the vehicle installation inner and outer sides is not more than 2%, so that both of a ground contact performance and a transmission performance of a steering force to the road surface can be compatible with each other. Longer periphery length at the vehicle installation outer side may diminish the transmission performance of a steering force to the road surface.
According to the tire described in <3>, a tread rigidity factor Z defined as (Y−0.045)/X in equation (3) is between 0.7 and 1.0, so that as described hereinafter in detail, both of ice and snow performance and straight-running stability can be ensured.
The studless tire 10 according to the present invention is characterized in that, in a section passing a central axis line under a condition where the tire is mounted on the predetermined rim 11 and a predetermined inner pressure is charged therein, the inner sidewall portion and the outer sidewall portion in the width direction of the vehicle under a condition where the tire is attached to the vehicle have mutually different shapes. In particular, assuming that distances Ao and Ai are measured from a position where a bladder ring is divided to position Po, Pi where a maximum tire width is obtained along the tire radial direction and distances Bo, Bi are measured from the position where the bladder ring is divided to positions where a tread ring is divide along the tire radial direction, side-shape coefficients of the tire are defined as ratios Ao/Bo and Ai/Bi, the side-shape coefficient Ao/Bo of the widthwise half portion disposed at a vehicle installation outer side is between 0.52 and 0.55 and the side-shape coefficient Ai/Bio of the widthwise half portion disposed at a vehicle installation inner side is between 0.45 and 0.50, or the side-shape coefficient Ao/Bo of the widthwise half portion disposed at a vehicle installation outer side is between 0.5 and 0.55 and the side-shape coefficient Ai/Bio of the widthwise half portion disposed at a vehicle installation inner side is between 0.45 and 0.48.
Assuming that Xd (=Ao/Bo) is the side-shape coefficient of the vehicle installation outer side and Xc (=Ai/Bi) is the side-shape coefficient of the vehicle installation inner side, a degree of side asymmetricity X expressed by equation (1) can be used as a factor expressing a degree of asymmetricity of the shapes of the sidewall portions. The degree of side asymmetricity X is 0.05 for Xd of 0.55 and Xc of 0.45, 0.01 for Xd of 0.5 and Xc of 0.48, and 0.01 for Xd of 0.52 and Xc of 0.5, so that the degree of side asymmetricity X of the tire according to the present invention should be between 0.01 and 0.05.
It is noted that Po represents a point where the maximum tire width Wt is obtained at the vehicle installation outer side and Pi represents a point where the maximum tire width Wt is obtained at the vehicle installation inner side.
The above-mentioned predetermined inner pressure and rim are defined in the following manner. That is, the predetermined internal pressure refers to an air pressure corresponding to a predetermined at an applicable size load and specified in a predetermined industrial standard, and the predetermined rim refers to a standard rim (or “approved rim”, “recommended rim”) for an applicable size specified the same industrial standard. The above-mentioned predetermined load refers to a maximum load (maximum load capacity) of a single wheel of an applicable size specified in the same industrial standard.
Regarding the industrial standard, an effective standard is set in each region where the tire is manufactured or used. Examples of such standards are “The Tire and Rim Association Inc. Year Book” (including design guides) in the U.S.A., “The European Tyre and Rim Technical Organisation Standards Manual” in Europe, and “JATMA YEAR BOOK” edited by the Japan Automobile Tyre Manufacturer Association in Japan.
The term “a widthwise half portion” of the tire as used herein refers to each of left and right half portions defined by a plane CL passing through the width center of the rim and perpendicular to a central axis of rotation of the tire under a condition where the tire is attached to a vehicle and the predetermined internal pressure is charged thereto.
The term “a position where a bladder ring is divided” as used herein refers to a position on the surface of the tire corresponding to a border between the bladder ring and the side mold constituting the vulcanization mold for vulcanizing the tire. There is formed a minute projection extending along the circumferential direction due to the border.
The term “a position where a tread ring is divided” as used herein refers to a position on the surface of the tire corresponding to a border between the tread ring and the side mold constituting the vulcanization mold for vulcanizing the tire. There is formed a minute projection extending along the circumferential direction due to the border.
Next, an operation of the studless tire 10 according to the present invention will be discussed. In general, when tires are installed to a vehicle, the tires are inclined such that their lower parts contacting a road surface are toward the outer side of the vehicle and their upper parts are toward the inner side of the vehicle to ensure straight-running stability. As viewed from the front side of the vehicle, the tires have a chevron-shaped posture on the vehicle, i.e. are provided with so-called negative cambers.
When tires with zero side asymmetricity, i.e. tires having symmetric shapes of the sidewall portions with respect to the vehicle installation inner and outer sides are attached with providing negative cambers as discussed above, contacting pressure is distributed as shown in
As far as the tires are driven while maintaining the symmetric ground contact shapes, no lateral force is generated on each of the tires and thus no force laterally displacing the vehicle is generated even if a load balance between the right and left tires on the vehicle is changed due to a noise input force from the road surface. However, when the tires are driven with the above-mentioned asymmetric ground contact shapes, a lateral force is generated on each tire. The lateral forces generated on the right and left tires cancel each other to maintain the straight-running stability of the vehicle. In this condition, a noise input from the road surface to either one of the right and left tires loses the balance between the lateral forces of the right and left tires, so that a lateral force is apt to occur on the vehicle.
Thus, in order to improve the straight-running stability, it is necessary to improve the symmetry between the right and left ground contact shapes with respect to the central line of the ground contacting surface of the tire in the width direction. The present invention is completed in view of this fact and employs a means for improving the symmetry between the right and left ground contacting shapes in which the rigidity of the half portion at the vehicle installation outer side is smaller than that of the half portion at the vehicle installation inner side to protrude the tread half portion at the vehicle installation outer side more than the tread half portion at the vehicle installation inner side.
The first measure for differentiating the amounts of protrusion of the right and left tread half portions is as follows. The tire contacts the road surface with a camber angle of −0.5 degrees under a condition that the predetermined inner pressure and a predetermined load are applied, as shown in
In other words, the first measure lowers the rigidity of the half portion at the vehicle installation outer side by increasing the side shape coefficient of the half portion at the vehicle installation outer side. The mechanism is discussed in the next. That is, the half portion at the vehicle installation outer side, which has large side shape coefficient, has smaller radius of curvature Ro of the shoulder portion than radius of curvature Ri of the shoulder portion of the half portion at the vehicle installation inner side, as shown in
In this way, according to the first measure, the circumferential stress T of the radial carcass 4 of the half portion at the vehicle installation outer side can be reduced by making the side-shape coefficient Xd at the vehicle installation outer side bigger than the side-shape coefficient Xc at the vehicle installation inner side. As a result, the rigidity of the whole half portion at the vehicle installation outer side can be decreased to protrude the tread portion more than the half portion at the vehicle installation inner side.
It is noted that in equation (2) representing the degree of asymmetricity of the ground contact shape Y, C and D are defined as ground contact lengths of a ground contact surface of the tire at the vehicle installation inner side and the vehicle installation outer side, respectively, measured at positions spaced 40% of the entire ground contact width W from the width center M of the ground contact surface under a condition. If these lengths are the same, the degree of asymmetricity of the ground contact surface is zero.
As described above, straight-running stability can be improved by optimizing the side-shape coefficients Xd, Xc. Specific ranges of the optimum side-shape coefficients Xd, Xc of the studless tire are 0.52-0.55 for the side-shape coefficients Xd at the vehicle installation outer side and 0.45-0.5 for the side-shape coefficients Xc at the vehicle installation inner side; or 0.5-0.55 for the side-shape coefficients Xd at the vehicle installation outer side and 0.45-0.48 for the side-shape coefficients Xc at the vehicle installation inner side. In a case where Xd is below 0.52 and Xc is over 0.5 or where Xd is below 0.5 and Xc is over 0.48, the degree of asymmetricity of the side-shape X is too small to improve straight-running stability. On the other hand, in a case where Xd is over 0.55 or Xc is below 0.45, the degree of asymmetricity of the side-shape X is so large that the degree of asymmetricity of the ground contact shape Y becomes large, which deteriorates straight-running stability and likely cause uneven wear.
In the above description, the degree of asymmetricity of the side-shape X optimum for suppressing the degree of asymmetricity of the ground contact shape Y to improve the symmetry of the ground contact shape depends largely to the tread rigidity. Thus, a degree of asymmetricity of a side-shape X of a summer tire having high tread rigidity cannot be applied to a studless tire of which tread rigidity should be suppressed to secure an ice and snow performance. In addition, in a studless tire, the degree of asymmetricity of the side-shape X needs to be optimized in view of the fact that straight-running stability may be deteriorated only due to a low tread rigidity. Owing to these points, an optimization of the asymmetricity of a studless tire is far complicated than that of a summer tire.
As discussed above, the tread rigidity of the studless tire needs to be sufficient for securing a ice and snow performance. The relationship between the degree of asymmetricity of the ground contact shape Y and the degree of asymmetricity of the side-shape X greatly rely on the tread rigidity, which allows the tread rigidity of the studless tire to be set within a preferable range. More specifically, a rigidity factor Z which experimentally precisely represents the tread rigidity and is defined as (Y−0.045)/X in equation (3) is preferably between 0.7 and 1.0. It is noted that Y and X represent the above-mentioned degree of asymmetricity of the side shape and degree of asymmetricity of the ground contact shape.
The second measure for differentiating the amounts of protrusion of the right and left tread half portions is as follows. In the studless tire 10, the periphery length L2 along the inner tire surface of the half portion at the vehicle installation outer side (see
Studless tires, the difference of which was only the degree of asymmetricity of the side-shape, were experimentally prepared, and the degrees of asymmetricity of the side-shape Y and various motion performances of the tires were evaluated with the tires being installed to actual vehicles. The specifications of the tires and the results of evaluation are shown in Table 1. The experimentally prepared tires had a tire size of 195165R15.
When the tires were installed to the vehicle, the studless tires were mounted on rims with size of 6 J and a predetermined internal pressure which was 200 kPa was charged in the tires.
The degree of asymmetricity Y of the ground contact shape was measured under a condition of an applied load: 4.71 N and a camber angle: −0.5 degrees according to the definition.
After the tire of the above-mentioned size was installed to a rear-drive vehicle and then a load, which is a drive and a 60 kg weight on the passenger seat, was applied, the actual vehicle evaluation was conducted. In order to evaluate uneven wear resistance, the tire was driven on a drum testing machine at 80 km/h with the above-mentioned camber angle, and the amount of wear at the vehicle installation inner side was measured after running 400 km. The results are indicated in index values with the amount of wear of the comparative example being set to 100. The larger index value means the larger amount of wear and thus less uneven wear resistance.
The drivability on dry roads and snow roads were comprehensively evaluated by the driver based on preciseness of vehicle behaviors and response rates in corners on a scale of one to ten.
The straight-running stability on dry roads and snow roads were comprehensively evaluated by the driver based on stability of the vehicle in straight roads and response rate upon slightly steering on a scale of one to ten.
The braking performance on snow roads were evaluated with a vehicle equipped with anti-lock brake system by measuring the braking distance from 40 km/h at full brake application. The results are indicated in index values with the result of comparative example being set to 100. The larger the index value is, the higher the braking performance is.
| Number | Date | Country | Kind |
|---|---|---|---|
| 2008-023920 | Feb 2008 | JP | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/JP2009/051899 | 2/4/2009 | WO | 00 | 8/3/2010 |
