JP4143015B2 - Automotive reinforcement - Google Patents
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- JP4143015B2 JP4143015B2 JP2003345627A JP2003345627A JP4143015B2 JP 4143015 B2 JP4143015 B2 JP 4143015B2 JP 2003345627 A JP2003345627 A JP 2003345627A JP 2003345627 A JP2003345627 A JP 2003345627A JP 4143015 B2 JP4143015 B2 JP 4143015B2
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- 238000005452 bending Methods 0.000 claims description 31
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- 239000000956 alloy Substances 0.000 description 1
- 229910045601 alloy Inorganic materials 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
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Description
本発明は優れた変形初期の曲げ反力特性を発揮することができる自動車用補強部材に関するものである。 The present invention relates to an automotive reinforcing member capable of exhibiting excellent bending reaction force characteristics at the initial stage of deformation.
近年、自動車業界では衝突安全性を確保しつつ、環境問題の観点から自動車の燃比向上が指摘されており、車両の軽量化が大きな課題となっている。衝突安全性の観点から、例えば特許文献１に開示されているように、自動車の側面衝突事故において、車両内の乗員の安全を確保するために自動車ドア補強材用角管が提案されている。これは角管のコ−ナ−部の外側にはＲを設けないか或るは板の肉厚未満の大きさのＲを設け、内面には外側より大きいＲを設けるというものである。
In recent years, the automobile industry has been pointed out to improve the fuel ratio of automobiles from the viewpoint of environmental problems while ensuring collision safety, and the weight reduction of vehicles has become a major issue. From the viewpoint of collision safety, for example, as disclosed in
近年、自動車業界において衝突安全性の基準がさらに厳しくなり、従来の曲げ性能を有する部材では基準を満足することが困難となりつつある。上記に述べた角管は、曲げ特性は確かに有利ではあるが、今後、ますます自動車の衝突性能向上のニーズが高まるとの観点から、上記に述べた角管に比較してより優れた曲げ特性を有する部材が要求されつつある。本発明は従来よりも更に優れた曲げ特性を発揮することができる自動車用補強部材を提供するものである。 In recent years, standards for collision safety have become more stringent in the automobile industry, and it has become difficult to satisfy the standards for members having conventional bending performance. Although the above-mentioned square tube is surely advantageous in bending properties, it is better than the above-mentioned square tube from the viewpoint that the needs for improving the collision performance of automobiles will increase in the future. A member having characteristics is being demanded. The present invention provides a reinforcing member for automobiles that can exhibit bending properties further superior to those of the prior art.
本発明は、従来の角管と異なり外側が正方形もしくは長方形で、内側の形状が真円あるいは楕円形状なので各辺に肉厚一定の部位がなくコ−ナ−部が最も肉厚が厚く、以下辺の中央部に向かって徐々に肉厚が小さくなる形状である。そうすることによってコ−ナ−部の肉厚を厚くし、外側断面は角型であることで変形初期の曲げ反力特性に優れ、かつ内側断面を円形状もしくは楕円形状とすることで変曲部が無く動的な応力波を分散することで局部座屈を抑制することができ優れた曲げ特性を発揮可能とした自動車用補強部材及びそれに供する角型管を得ることが出来る。 The present invention is different from conventional square tubes in that the outside is square or rectangular and the inside shape is a perfect circle or ellipse, so there is no constant thickness on each side and the corner is the thickest, The thickness gradually decreases toward the center of the side. By doing so, the corner is thickened, the outer cross section is square, and it has excellent bending reaction force characteristics at the initial stage of deformation. By dispersing the dynamic stress wave without any part, local buckling can be suppressed, and an automotive reinforcing member capable of exhibiting excellent bending characteristics and a square tube used for the same can be obtained.
本発明は以下の構成を要旨とするものである。 The gist of the present invention is as follows.
（１） 外側の断面形状が正方形もしくは長方形であり、コーナー部の外側にはＲが設けられてないか肉厚の５倍以下のＲが設けられており、内側の断面形状が外側の断面と同心である真円あるいは、外側の断面と同心かつ外側の断面の辺に平行な中心軸を持つ楕円形状であることを特徴とする自動車用補強部材用の角型管。 (1) The outer cross-sectional shape is a square or a rectangle, R is not provided on the outer side of the corner portion, or R of 5 times or less the wall thickness is provided, and the inner cross-sectional shape is the outer cross-section. A rectangular tube for a reinforcing member for an automobile, which is a concentric perfect circle or an elliptical shape having a central axis that is concentric with an outer cross section and parallel to a side of the outer cross section.
（２） 上記（１）項の自動車用補強部材用の角型管において、その断面形状が（１）〜（４）式の条件を満たすことを特徴とする自動車用補強部材用の角型管。
２ｍｍ≦（Ｌ−Ｄ1）≦１０ｍｍ ・ ・ ・（１）
２ｍｍ≦（Ｌ−Ｄ2）≦１０ｍｍ ・ ・ ・（２）
ｔ1、ｔ2、ｔ3、ｔ4≧１ｍｍ ・ ・ ・（３）
Ｒ≦５・ｔmin ・ ・ ・（４）
Ｌ1；１辺の外側の辺長さ（ｍｍ）、Ｌ2；当該１辺と垂直な外側の辺長さ（ｍｍ）、Ｄ1；当該１辺と平行な方向の内側の内径（ｍｍ）、Ｄ2；当該１辺と垂直方向の内側の内径（ｍｍ）、ｔ1、ｔ3；Ｄ2と平行な辺の最小肉厚（ｍｍ）、ｔ2、ｔ4；Ｄ1と平行な辺の最小肉厚（ｍｍ）、ｔmin；ｔ1、ｔ2、ｔ3、ｔ4の最小値（ｍｍ）、Ｒ；外側コ−ナ−曲率半径（ｍｍ）
(2) The square tube for a reinforcing member for automobiles according to (1), wherein the cross-sectional shape satisfies the conditions of the expressions (1) to (4). .
2 mm ≦ (LD 1 ) ≦ 10 mm (1)
2 mm ≦ (L−D 2 ) ≦ 10 mm (2)
t 1 , t 2 , t 3 , t 4 ≧ 1 mm (3)
R ≦ 5 ・ t min・ ・ （4）
L 1 ; outer side length (mm) of one side, L 2 ; outer side length (mm) perpendicular to the one side, D 1 ; inner inner diameter (mm) in a direction parallel to the one side , D 2 ; inner diameter (mm) perpendicular to the one side, t 1 , t 3 ; minimum thickness (mm) of the side parallel to D 2 , t 2 , t 4 ; side parallel to D 1 Minimum thickness (mm), t min ; minimum value of t 1 , t 2 , t 3 , t 4 (mm), R; radius of curvature of outer corner (mm)
（３） 上記（１）または（２）項の自動車用補強部材用の角型管のうち、隣り合う辺の最小肉厚が異なるものを、該最小肉厚のより厚い辺が曲げ入力方向に平行となるように配置したことを特徴とする自動車用補強部材。 (3) Among the rectangular tubes for automotive reinforcing members of the above (1) or (2), those having different minimum thicknesses of adjacent sides, the thicker side of the minimum thickness being bent in the input direction A reinforcing member for an automobile characterized by being arranged in parallel.
以上の本発明の自動車用補強部材は、動的な曲げ入力に対して断面扁平しにくく丸鋼管や角鋼管に対して大きな初期の反力特性を有することで、従来の鋼管よりも軽量にすることが可能になる。また本発明は、アルミ管のような押し出し材や鋳造材、アルミやマグネシウム等のダイキャスト材等でも有効である。 The above-described automotive reinforcing member of the present invention is lighter than a conventional steel pipe by having a large initial reaction force characteristic against a round steel pipe or a square steel pipe, which is less likely to be flattened against a dynamic bending input. It becomes possible. The present invention is also effective for extruded materials such as aluminum tubes, cast materials, die-cast materials such as aluminum and magnesium, and the like.
以下、本願発明を詳細に説明する。 Hereinafter, the present invention will be described in detail.
一般に角管と言われるものに、その断面が正方形のものと長方形のものとがある。本願発明では製造の容易さという観点から正方断面の角管が望ましいが、長方断面であっても構わない。 In general, a rectangular tube has a square section and a rectangular section. In the present invention, a square tube having a square section is desirable from the viewpoint of ease of manufacture, but a rectangular section may be used.
角管を自動車用の例えばドア用ビームに使用する場合などは、角管に対し曲げの力が働く。通常、角管を曲げた場合、曲げ入力方向と平行な辺の入力側のコ−ナ−部に直接その荷重が負荷されるが、角管では曲げ入力を受ける面に対し外側断面の縦壁に当たる部位が垂直であることが有効であるため、丸管やその他の多角形に比較して断面偏平を起こしにくい構造となっている。角型管のコ−ナ−部を強化し、さらに曲げ特性を向上させるためには、コ−ナ−部の肉厚を増加させることが効果的である。角型管の断面形状を外側が正方形あるいは長方形で、内側が真円あるいは楕円形状にすることで、コ−ナ−部の肉厚を厚くし、各辺もコ−ナ−部に近いほど肉厚を厚くするので合理的な曲げ特性を有するとともに、内側に変曲点を有さないため動的曲げ入力を効果的に分散し受け止めることが出来る自動車用補強部材用の角型管が得られる。 When the square tube is used for an automobile beam such as a door beam, a bending force acts on the square tube. Normally, when a square tube is bent, the load is directly applied to the corner on the input side of the side parallel to the bending input direction. Since it is effective that the portion corresponding to is vertical, the structure is less likely to cause cross-sectional flattening than a round tube or other polygons. In order to strengthen the corner portion of the rectangular tube and further improve the bending characteristics, it is effective to increase the wall thickness of the corner portion. By making the cross-sectional shape of the square tube square or rectangular on the outside and round or oval on the inside, the corners are thickened, and the sides are closer to the corners. Since the thickness is increased, there is a rational bending characteristic, and since there is no inflection point on the inside, a rectangular tube for a reinforcing member for an automobile that can effectively disperse and receive dynamic bending input can be obtained. .
図１（ａ）、（ｂ）、（ｃ）、（ｄ）、（ｅ）は、本願発明の実施例である角型管の断面を示した図である。 1 (a), (b), (c), (d), and (e) are cross-sectional views of a rectangular tube that is an embodiment of the present invention.
図１（ａ）は、外側断面が正方形で内側断面が円形、図１（ｂ）は外側断面が長方形で内側断面が円形、図１（ｃ）は外側断面が正方形で内側断面が楕円形、図１（ｄ）は外側断面が長方形で内側断面が楕円形、そして図１（ｅ）は外側断面が長方形で内側断面が円形である角型管をそれぞれ示している。そして図１（ｂ）（ｄ）は長方形の長手方向が曲げ方向となる例で、図１（ｅ）は長方形の長手方向と直角方向が曲げ方向となる例である。 1A is a square outer cross section and a circular inner cross section, FIG. 1B is a rectangular outer cross section and a circular inner cross section, FIG. 1C is a square outer cross section and an elliptical inner cross section, FIG. 1 (d) shows a rectangular tube whose outer cross section is rectangular and whose inner cross section is elliptical, and FIG. 1 (e) shows a rectangular tube whose outer cross section is rectangular and whose inner cross section is circular. FIGS. 1B and 1D are examples in which the longitudinal direction of the rectangle is the bending direction, and FIG. 1E is an example in which the direction perpendicular to the longitudinal direction of the rectangle is the bending direction.
図１に示すこれらの角型管は、以下の条件を満足している。
２ｍｍ≦（Ｌ1−Ｄ1）≦１０ｍｍ
２ｍｍ≦（Ｌ2−Ｄ2）≦１０ｍｍ
ｔ1、ｔ2、ｔ3、ｔ4≧１ｍｍ
Ｒ≦５・ｔmin
ここで、Ｌ1；１辺の外側の辺長さ（ｍｍ）、Ｌ2；当該１辺と垂直な外側の辺長さ（ｍｍ）、Ｄ1；当該１辺と平行な方向の内側の内径（ｍｍ）、Ｄ2；当該１辺と垂直方向の内側の内径（ｍｍ）、ｔ1、ｔ3；Ｄ2と平行な辺の最小肉厚（ｍｍ）、ｔ2、ｔ4；Ｄ1と平行な辺の最小肉厚（ｍｍ）、ｔmin；ｔ1、ｔ2、ｔ3、ｔ4の最小値（ｍｍ）、Ｒ；外側コ−ナ−曲率半径（ｍｍ）である。なお、ｔＲはコーナー部の板厚（ｍｍ）を示している。
These square tubes shown in FIG. 1 satisfy the following conditions.
2 mm ≦ (L 1 −D 1 ) ≦ 10 mm
2 mm ≦ (L 2 −D 2 ) ≦ 10 mm
t 1 , t 2 , t 3 , t 4 ≧ 1 mm
R ≦ 5 ・ t min
Here, L 1 ; outer side length (mm) of one side, L 2 ; outer side length (mm) perpendicular to the one side, D 1 ; inner diameter in the direction parallel to the one side (Mm), D 2 ; inner diameter (mm) perpendicular to the one side, t 1 , t 3 ; minimum wall thickness (mm) of the side parallel to D 2 , t 2 , t 4 ; D 1 Minimum thickness (mm) of parallel sides, t min ; minimum value (mm) of t 1 , t 2 , t 3 , t 4 , R: outer corner radius of curvature (mm). Incidentally, t R denotes a plate thickness of the corner portions (mm).
上記条件を満足することが好ましい理由を以下に述べる。 The reason why it is preferable to satisfy the above conditions will be described below.
（Ｌ1−Ｄ1）および（Ｌ2−Ｄ2）は、互いに向かいあった一対の辺の最小板厚の合計値を示す。この値が１０ｍｍより大きい場合、コ−ナ−部の肉厚、各辺の最小肉厚が大きくなり、曲げ特性は向上するものの、部材重量が増加し、軽量化の要請には十分応えることが難しくなる。また逆に、２ｍｍよりも小さい場合は最小肉厚部位置で座屈が発生し、十分な曲げ特性が得られにくくなる。また、あまりにも肉厚が小さいと製造時最小肉厚部位置で破断し易くなる。更に同様の理由でｔ1、ｔ2、ｔ3、ｔ4それぞれの肉厚を１ｍｍ以上とすることが望ましい。 (L 1 -D 1 ) and (L 2 -D 2 ) indicate the total value of the minimum plate thicknesses of a pair of sides facing each other. When this value is larger than 10 mm, the corner thickness and the minimum thickness of each side are increased, and the bending characteristics are improved, but the weight of the member is increased and the demand for weight reduction can be sufficiently met. It becomes difficult. Conversely, if it is smaller than 2 mm, buckling occurs at the position of the minimum thickness portion, and it becomes difficult to obtain sufficient bending characteristics. On the other hand, if the wall thickness is too small, it is easy to break at the position of the minimum wall thickness at the time of manufacture. Furthermore, for the same reason, it is desirable that the thickness of each of t 1 , t 2 , t 3 and t 4 be 1 mm or more.
次に、外側コ−ナ−曲率半径Ｒは各辺のｔ1、ｔ2、ｔ3、ｔ4の中で最も小さい肉厚ｔminの５倍以下とする。この理由は、外側コ−ナ−曲率半径Ｒはできるだけ小さい方が曲げ特性には有利であるが、逆にＲがｔminの５倍より大きくなると、曲げ力がコ−ナ−部に直接負荷されず、辺の中央部のみが押され中央部周辺で座屈が発生し易くなり、優れた曲げ特性が得られにくくなるからである。従って、その影響の小さい範囲としてＲ≦５・ｔminとする。 Next, the outer corner radius of curvature R is set to be not more than 5 times the smallest thickness t min among t 1 , t 2 , t 3 and t 4 of each side. The reason for this is that the outer corner radius of curvature R is as small as possible for the bending characteristics, but conversely when R is greater than 5 times tmin , the bending force is applied directly to the corner. This is because only the central portion of the side is pushed and buckling is likely to occur around the central portion, making it difficult to obtain excellent bending characteristics. Therefore, R ≦ 5 · t min is set as a range where the influence is small.
もちろん本発明の角型管の自動車への配置は曲げ特性を最大限に発揮するように取り付け方向を考慮することが更に望ましい。内側が楕円形状の角型管の場合、自動車へ取り付けたときの動的曲げ入力に対し変形が厳しく制限される部位に使用される場合、曲げ入力側の両端のコ−ナ−の肉厚が厚く、かつ曲げ入力方向と平行な辺の肉厚をできるだけ厚くなるように配置することが望ましいので、例えば楕円の内側断面を有する場合に長軸方向が曲げ入力方向と一致するように取り付ける等、最小肉厚が隣り合う辺で異なる場合に、より厚い辺が曲げ入力方向に平行となるように取り付けることが有利である。一方、変形がある程度許容され衝撃を吸収すべき部位に使用される場合、逆に楕円の短軸方向が曲げ入力方向と一致するように配置する等、最小肉厚がより薄い辺が曲げ入力方向に平行となるように取り付けることが有利である。 Of course, it is more desirable to consider the mounting direction so that the bending of the square tube of the present invention to the automobile can be maximized. In the case of a rectangular tube with an elliptical shape on the inside, if it is used in a part where deformation is severely restricted with respect to dynamic bending input when it is attached to an automobile, the thickness of the corners at both ends on the bending input side will be Since it is desirable to arrange it so that the thickness of the side parallel to the bending input direction is as thick as possible, for example, when having an inner cross section of an ellipse, it is attached so that the major axis direction matches the bending input direction, etc. When the minimum thickness is different between adjacent sides, it is advantageous to attach the thicker side parallel to the bending input direction. On the other hand, when the deformation is allowed to some extent and it is used for a part that should absorb impact, the side with the thinner minimum thickness is conversely arranged such that the minor axis direction of the ellipse coincides with the bending input direction. It is advantageous to mount so that it is parallel to
本発明の自動車用補強部材である角型管を製造する方法としては、引き抜き、押し出し、鍛造、ロ−ル成形等があり、いずれでも製造可能であり、本願発明を限定するものではない。また、本発明の自動車用補強部材を形成する材料としては、鋼材やアルミニウム、チタン、マグネシウムやそれぞれの合金の軽金属材料等の軽量材料を用いても製造可能である。 Examples of a method for producing a rectangular tube that is a reinforcing member for an automobile according to the present invention include drawing, extrusion, forging, and roll forming. Any of these methods can be produced, and the present invention is not limited thereto. Moreover, as a material which forms the reinforcement member for motor vehicles of this invention, even if it uses light materials, such as steel materials, aluminum, titanium, magnesium, and light metal material of each alloy, it can manufacture.
自動車の側面衝突事故等において、車両内の乗員の安全を確保するための自動車用補強部材としては、乗員に対する進入を押さえる必要があり、曲げ特性としては特に初期座屈開始反力が重要であることから鋼管の断面座屈反力を動的に調べることを行った。試験条件は、試験片の長手方向長さＬ＝１５０ｍｍで落錘試験機により落下速度１３．９ｍ／ｓｅｃ、落重重量３００ｋｇ、曲げスパン長さＬ＝１２０ｍｍとし両端の支持部は自由端とした。 In automobile side collision accidents, etc., it is necessary to suppress the approach to the occupant as an automobile reinforcement member for ensuring the safety of the occupant in the vehicle, and the initial buckling start reaction force is particularly important as a bending characteristic. Therefore, the cross-sectional buckling reaction force of the steel pipe was examined dynamically. The test conditions were a longitudinal length L = 150 mm of the test piece, a drop speed of 13.9 m / sec, a drop weight of 300 kg, a bending span length L = 120 mm by a drop weight tester, and the support portions at both ends were free ends. .
表１に示す各種の自動車用補強部材試験片を示す。本発明の比較材として、材料強度を高めたドアガードバー等によく使用されている高周波焼入れにより引張強度１５０ｋｇf／ｍｍ3とした丸鋼管と角型鋼管を用意した。試験条件及び試験結果等を併せて表１に示す。 Various automotive reinforcing member test pieces shown in Table 1 are shown. As comparative materials of the present invention, round steel pipes and square steel pipes having a tensile strength of 150 kgf / mm 3 by induction hardening that are often used for door guard bars and the like with increased material strength were prepared. The test conditions and test results are also shown in Table 1.
表１に示す実施例１〜２は、図２に示すように比較例１〜２の正方断面角鋼管に対しても、比較例３丸断面鋼管に対しても、大きな初期の反力を示しており、単位質量当りの反力特性が優れていると言える。 Examples 1 and 2 shown in Table 1 show a large initial reaction force for both the square section square steel pipe of Comparative Examples 1 and 2 and the comparative example 3 round section steel pipe as shown in FIG. It can be said that the reaction force characteristic per unit mass is excellent.
Ｌ1 １辺の外側の辺長さ（ｍｍ）
Ｌ2 当該１辺と垂直な外側の辺長さ（ｍｍ）
Ｄ1 当該１辺と平行な方向の内側の内径（ｍｍ）
Ｄ2 当該１辺と垂直方向の内側の内径（ｍｍ）
ｔ1、ｔ3 Ｄ2と平行な辺の最小肉厚（ｍｍ）
ｔ2、ｔ4 Ｄ1と平行な辺の最小肉厚（ｍｍ）
Ｒ 外側コ−ナ−曲率半径（ｍｍ）
ｔＲ コーナー部の板厚（ｍｍ）
L 1 Length of outer side of one side (mm)
L 2 Outer side length perpendicular to the one side (mm)
D 1 Inner inner diameter (mm) in the direction parallel to the one side
D 2 Inner diameter in the direction perpendicular to the one side (mm)
Minimum thickness (mm) of sides parallel to t 1 and t 3 D 2
Minimum thickness (mm) of the side parallel to t 2 and t 4 D 1
R Outer corner radius of curvature (mm)
t R Corner thickness (mm)
Claims (3)
２ｍｍ≦（Ｌ1−Ｄ1）≦１０ｍｍ
２ｍｍ≦（Ｌ2−Ｄ2）≦１０ｍｍ
ｔ1、ｔ2、ｔ3、ｔ4≧１ｍｍ
Ｒ≦5×ｔmin
Ｌ1；１辺の外側の辺長さ（ｍｍ）
Ｌ2；当該１辺と垂直な外側の辺長さ（ｍｍ）
Ｄ1；当該１辺と平行な方向の内側の内径（ｍｍ）
Ｄ2；当該１辺と垂直方向の内側の内径（ｍｍ）
ｔ1、ｔ3；Ｄ2と平行な辺の最小肉厚（ｍｍ）
ｔ2、ｔ4；Ｄ1と平行な辺の最小肉厚（ｍｍ）
ｔmin；ｔ1、ｔ2、ｔ3、ｔ4の最小値（ｍｍ）
Ｒ；外側コ−ナ−曲率半径（ｍｍ） The rectangular tube for a reinforcing member for automobiles according to claim 1, wherein the cross-sectional shape satisfies the following conditions.
2 mm ≦ (L 1 −D 1 ) ≦ 10 mm
2 mm ≦ (L 2 −D 2 ) ≦ 10 mm
t 1 , t 2 , t 3 , t 4 ≧ 1 mm
R ≦ 5 × t min
L 1 ; side length outside one side (mm)
L 2 ; outside side length perpendicular to the one side (mm)
D 1 ; Inner inner diameter (mm) in the direction parallel to the one side
D 2 ; inner diameter in the direction perpendicular to the one side (mm)
t 1 , t 3 ; minimum thickness (mm) of the side parallel to D 2
t 2 , t 4 ; the minimum thickness (mm) of the side parallel to D 1
t min ; minimum value (mm) of t 1 , t 2 , t 3 , t 4
R: Outer corner radius of curvature (mm)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003345627A JP4143015B2 (en) | 2003-10-03 | 2003-10-03 | Automotive reinforcement |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2003345627A JP4143015B2 (en) | 2003-10-03 | 2003-10-03 | Automotive reinforcement |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JP2005112032A JP2005112032A (en) | 2005-04-28 |
| JP4143015B2 true JP4143015B2 (en) | 2008-09-03 |
Family
ID=34538840
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP2003345627A Expired - Fee Related JP4143015B2 (en) | 2003-10-03 | 2003-10-03 | Automotive reinforcement |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP4143015B2 (en) |
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2003
- 2003-10-03 JP JP2003345627A patent/JP4143015B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JP2005112032A (en) | 2005-04-28 |
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