JP3055446B2 - Screw part fastening structure - Google Patents
Screw part fastening structureInfo
- Publication number
- JP3055446B2 JP3055446B2 JP7317682A JP31768295A JP3055446B2 JP 3055446 B2 JP3055446 B2 JP 3055446B2 JP 7317682 A JP7317682 A JP 7317682A JP 31768295 A JP31768295 A JP 31768295A JP 3055446 B2 JP3055446 B2 JP 3055446B2
- Authority
- JP
- Japan
- Prior art keywords
- members
- sleeve
- fastening structure
- size
- thermal expansion
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
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- Connection Of Plates (AREA)
Description
【０００１】[0001]
【発明の属する技術分野】本発明は、ねじ部品よりも大
きい熱膨張率を有する複数の部材にそれぞれ形成された
穴同士を上記ねじ部品で連結して当該部材同士を締結す
るねじ部品締結構造に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a screw component fastening structure in which holes formed in a plurality of members having a larger coefficient of thermal expansion than a screw component are connected to each other by the screw component and the members are fastened to each other. .
【０００２】[0002]
【従来の技術】自動車のエンジンなどのような発熱する
機器をフレームなどの支持部材にボルトなどで締結する
と、上記機器の作動に伴って、当該機器のケーシングが
熱膨張し、当該締結部分が歪んでしまう場合がある。こ
のため、例えば、実開平３−１０４１２９号では、上記
機器のケーシング側のボルト穴を大径にして、当該穴に
ゴム製のリングを嵌合することにより、当該締結部分の
ボルトの径方向の歪みを緩衝することが提案されてい
る。2. Description of the Related Art When a heat-generating device such as an automobile engine is fastened to a support member such as a frame by a bolt or the like, the casing of the device thermally expands with the operation of the device, and the fastening portion is distorted. In some cases. For this reason, for example, in Japanese Utility Model Laid-Open No. 3-104129, a bolt hole on the casing side of the device is made large in diameter, and a rubber ring is fitted into the hole, so that the bolt in the radial direction of the fastening portion is formed. It has been proposed to buffer the distortion.
【０００３】[0003]
【発明が解決しようとする課題】しかしながら、車重の
軽量化のために前記機器や前記支持部材などにアルミニ
ウム系金属材料を用いる一方、十分な締結力を得るため
に鉄系金属材料のボルトで上記機器と上記支持部材とを
締結する、即ち、例えば、図３（ａ）に示すように、ア
ルミニウム製の部材１，２に形成されたねじ穴１ａ，２
ａにスチール製のボルト５を螺合して部材１，２を締結
したり、図３（ｂ）に示すように、アルミニウム製の部
材３，４に形成された貫通穴３ａ，４ａにスチール製の
ボルト６を挿通し、当該ボルト６にスチール製のワッシ
ャ７を介してスチール製のナット８を螺合することで部
材３，４を締結したりした場合には、アルミニウムの方
がスチールよりも大きな熱膨張率を有している（約２
倍）ことから、当該締結部分に熱が加わると、ボルト
５，６の軸心方向に負荷を生じるようになるため、前述
した実開平３−１０４１２９号で提案されたものでは当
該負荷を緩衝することができない。However, while aluminum-based metal materials are used for the equipment and the support members to reduce the weight of the vehicle, bolts of iron-based metal materials are used to obtain a sufficient fastening force. The device and the support member are fastened, that is, for example, as shown in FIG. 3 (a), screw holes 1a, 2 formed in aluminum members 1, 2
3a, the members 1 and 2 are fastened by screwing a steel bolt 5 to the steel bolts 5, and as shown in FIG. 3 (b), steel members 5 are inserted into through holes 3a and 4a formed in aluminum members 3 and 4, respectively. When the members 3 and 4 are fastened by inserting a steel nut 8 into the bolt 6 through a steel washer 7, the aluminum is better than the steel. It has a large coefficient of thermal expansion (about 2
Therefore, when heat is applied to the fastening portion, a load is generated in the axial direction of the bolts 5 and 6, and the load proposed in Japanese Utility Model Laid-Open No. 3-104129 is buffered. Can not do.
【０００４】このため、上述したような締結部分が熱を
繰り返し受けてしまうと、ボルト５，６やワッシャ７の
座面が部材１，３，４に喰い込んで当該部材１，３，４
の上記座面との当接部分に窪を形成してしまい、ボルト
５，６やナット８による締結力を低下させてしまう恐れ
がある。このような問題は、上述した機器や支持部材の
締結部分に限らず、ねじ部品よりも大きい熱膨張率を有
する複数の部材にそれぞれ形成された穴同士を上記ねじ
部品で連結して当該部材同士を締結するねじ部品締結構
造であれば、上述と同様にして起こる恐れがある。この
ようなことから、本発明は、上述したような締結力の低
下を防ぐことができるねじ部品締結構造を提供すること
を目的とした。For this reason, when the above-mentioned fastening portion receives heat repeatedly, the seat surfaces of the bolts 5, 6 and the washer 7 bite into the members 1, 3, 4 and the members 1, 3, 4
Of the bolts 5, 6 and the nut 8 may be reduced. Such a problem is not limited to the above-described fastening portion of the device or the support member, and the holes formed in a plurality of members having a larger coefficient of thermal expansion than the screw component are connected to each other by the screw component. May be caused in the same manner as described above if the screw component fastening structure is used to fasten the above. In view of the above, an object of the present invention is to provide a screw component fastening structure capable of preventing a decrease in the fastening force as described above.
【０００５】[0005]
【課題を解決するための手段】前述した課題を解決する
ための、本発明によるねじ部品締結構造は、ねじ部品よ
りも大きい熱膨張率を有する複数の部材にそれぞれ形成
された穴同士を上記ねじ部品で連結して当該部材同士を
締結するねじ部品締結構造であって、締結方向外側に位
置する前記部材の前記穴と前記ねじ部品との間に当該ね
じ部品と同等の熱膨張率を有するスリーブを介装すると
共に、当該スリーブの締結方向外側の端部に当該スリー
ブの締結方向内側の端部よりも大径をなす大径部を設け
る一方、前記部材の前記穴の周面の周方向に沿って隙間
を設けたことを特徴とする。SUMMARY OF THE INVENTION In order to solve the above-mentioned problem, a threaded component fastening structure according to the present invention is characterized in that holes formed in a plurality of members having a larger coefficient of thermal expansion than a threaded component are formed in the screw. A screw component fastening structure for connecting the members by connecting them with each other, wherein the sleeve has a thermal expansion coefficient equivalent to that of the screw component between the hole and the screw component of the member positioned outside in the fastening direction. A large-diameter portion having a larger diameter than the inner end of the sleeve in the fastening direction is provided at the outer end in the fastening direction of the sleeve, while the outer peripheral portion of the peripheral surface of the hole of the member is provided in the circumferential direction. A gap is provided along the gap.
【０００６】上記ねじ部品締結構造においては、前記ス
リーブの前記大径部が前記ねじ部品の座面の大きさ以上
の大きさを有することを特徴とする。In the above screw part fastening structure, the large diameter portion of the sleeve has a size larger than a size of a seating surface of the screw part.
【０００７】上記ねじ部品締結構造においては、前記ス
リーブの前記大径部がフランジであることを特徴とす
る。In the above screw part fastening structure, the large diameter portion of the sleeve is a flange.
【０００８】上記ねじ部品締結構造においては、前記隙
間の前記穴の径方向の大きさが前記スリーブの前記大径
部の径方向の大きさ以上の大きさを有すると共に、当該
隙間の上記穴の軸心方向の大きさが前記部材の熱膨張率
と上記スリーブの熱膨張率との差に基づいて設定された
大きさであることを特徴とする。In the above screw part fastening structure, the radial size of the hole of the gap is equal to or greater than the radial size of the large diameter portion of the sleeve, and The size in the axial direction is a size set based on the difference between the coefficient of thermal expansion of the member and the coefficient of thermal expansion of the sleeve.
【０００９】上記ねじ部品締結構造においては、前記隙
間が前記部材同士の当接面に形成されていてもよい。In the above screw part fastening structure, the gap may be formed on a contact surface between the members.
【００１０】上記ねじ部品締結構造においては、前記隙
間が前記部材間にシムを介在させることにより形成され
ていてもよい。[0010] In the threaded fasteners fastening structure may be formed by the gap to interpose a shim between said members.
【００１１】[0011]
【発明の実施の形態】本発明によるねじ部品締結構造の
実施の形態を図１を用いて説明する。なお、図１は、そ
の概略構造を表す断面図である。DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of a screw component fastening structure according to the present invention will be described with reference to FIG. FIG. 1 is a sectional view showing the schematic structure.
【００１２】図１（ａ）に示すように、互いに締結させ
られるアルミニウム製の部材１１，１２には、穴１１
ａ，１２ａが連通するようにして形成されている。部材
１１の上記穴１１ａには、貫通穴１３ａを有する円筒型
をなすスチール製のスリーブ１３が嵌合している。一
方、部材１２の上記穴１２ａには、内周面にねじ山１４
ａを形成した円筒型をなすスチール製のスリーブ１４が
嵌合している。これらスリーブ１３，１４の部材１１，
１２の外側面側の端部には、当該スリーブ１３，１４の
部材１１，１２の内側面側の端部よりも大径をなす大径
部であるフランジ１３ｂ，１４ｂがそれぞれ形成されて
おり、これらスリーブ１３，１４の当該フランジ１３
ｂ，１４ｂは、互いに等しい大きさを有すると共に、部
材１１，１２の前記穴１１ａ，１２ａの外側面側に形成
された収納溝１１ｂ，１２ｂにそれぞれ嵌め込まれてい
る。As shown in FIG. 1A, holes 11 are formed in aluminum members 11 and 12 which are fastened to each other.
a and 12a are formed so as to communicate with each other. A cylindrical steel sleeve 13 having a through hole 13a is fitted into the hole 11a of the member 11. On the other hand, the hole 12a of the member 12 has a thread 14
A steel sleeve 14 having a cylindrical shape and forming a is fitted therein. The members 11 of these sleeves 13 and 14,
Flanges 13b and 14b, which are larger diameter portions than the inner surface ends of the members 11 and 12 of the sleeves 13 and 14, respectively, are formed at ends of the outer surfaces of the sleeves 12 and 14, respectively. The flange 13 of these sleeves 13 and 14
b and 14b have the same size as each other, and are fitted respectively into housing grooves 11b and 12b formed on the outer surface side of the holes 11a and 12a of the members 11 and 12, respectively.
【００１３】前記スリーブ１３の前記貫通穴１３ａに
は、ボルト１５が差し込まれ、当該ボルト１５は、前記
スリーブ１４のねじ山１４ａに螺合している。つまり、
ボルト１５は、上記スリーブ１３，１４を連結して前記
部材１１，１２を締結しているのである。ボルト１５の
フランジ１５ａの座面は、上記スリーブ１３の前記フラ
ンジ１３ｂにのみ荷重を加えるようになっている、言い
換えれば、スリーブ１３のフランジ１３ｂは、ボルト１
５のフランジ１５ａの座面の大きさ以上の大きさを有し
ているのである。A bolt 15 is inserted into the through hole 13 a of the sleeve 13, and the bolt 15 is screwed to a thread 14 a of the sleeve 14. That is,
The bolt 15 connects the sleeves 13 and 14 to fasten the members 11 and 12. The bearing surface of the flange 15 a of the bolt 15 applies a load only to the flange 13 b of the sleeve 13. In other words, the flange 13 b of the sleeve 13
5 has a size larger than the size of the bearing surface of the flange 15a.
【００１４】一方、前記部材１１，１２同士の当接面に
は、前記穴１１ａ，１２ａの周面の周方向に沿って隙間
となる緩衝溝１１ｃ，１２ｃがそれぞれ形成されてい
る。これら部材１１，１２の上記緩衝溝１１ｃ，１２ｃ
は、その穴１１ａ，１２ａの径方向の大きさが前記スリ
ーブ１３，１４のフランジ１３ｂ，１４ｂの径方向の大
きさ以上の大きさをなすと共に、その穴１１ａ，１２ａ
の軸心方向の大きさが部材１１，１２の熱膨張率とスリ
ーブ１３，１４の熱膨張率との差に基づいて設定された
大きさ、即ち、温度上昇に伴う部材１１，１２の上記軸
心方向への負荷を緩衝できる大きさとなっている。具体
的には、次のようにして設定する。On the other hand, buffer grooves 11c and 12c are formed in the contact surfaces of the members 11 and 12 along the circumferential direction of the peripheral surfaces of the holes 11a and 12a. The buffer grooves 11c, 12c of these members 11, 12
The size of the holes 11a and 12a in the radial direction is larger than the size of the flanges 13b and 14b of the sleeves 13 and 14 in the radial direction, and the holes 11a and 12a
Is set based on the difference between the thermal expansion coefficients of the members 11 and 12 and the thermal expansion coefficients of the sleeves 13 and 14, that is, the shafts of the members 11 and 12 associated with the temperature rise. It is large enough to buffer the load in the direction of the center. Specifically, it is set as follows.
【００１５】温度上昇に伴って膨張する長さΔＬは、下
記の式（１）から求めることができる。The length ΔL that expands with an increase in temperature can be obtained from the following equation (1).
【数１】ΔＬ＝β・ΔＴ・Ｌ …式（１） 但し、 β ：線熱膨張係数 ΔＴ：上昇温度 Ｌ ：当初の長さ また、鉄は、β＝１１．８×１０-6／ｄｅｇであり、ア
ルミニウムは、β＝２３．０×１０-6／ｄｅｇである。ΔL = β · ΔT · L Equation (1) where β: linear thermal expansion coefficient ΔT: rising temperature L: initial length Further, iron is β = 11.8 × 10 −6 / deg. And aluminum has β = 23.0 × 10 −6 / deg.
【００１６】よって、部材１１，１２の厚さ及びスリー
ブ１３，１４の軸心方向の長さをそれぞれ１０ｍｍと
し、ボルト１５の軸部の長さを２０ｍｍとし、２０℃か
ら９０℃まで温度上昇するとすれば、部材１１，１２の
厚さ方向の合計膨張長さは、３．２２×１０-2ｍｍとな
り、スリーブ１３，１４の軸心方向の合計膨張長さ及び
ボルト１５の軸部の膨張長さは、１．６５２×１０-2ｍ
ｍとなり、その膨張長さの差は、０．０１５６８ｍｍと
なる。従って、部材１１，１２の前記緩衝溝１１ｃ，１
２ｃの前記穴１１ａ，１２ａの軸心方向のサイズは、そ
の加工性及び検査性などの点を考慮して、それぞれ０．
５ｍｍ程度に設定すれば十分である。Therefore, when the thickness of the members 11 and 12 and the length of the sleeves 13 and 14 in the axial direction are each 10 mm, the length of the shaft of the bolt 15 is 20 mm, and the temperature rises from 20 ° C. to 90 ° C. Then, the total expansion length of the members 11 and 12 in the thickness direction becomes 3.22 × 10 −2 mm, and the total expansion length of the sleeves 13 and 14 in the axial direction and the expansion length of the shaft portion of the bolt 15. The height is 1.652 × 10 -2 m
m, and the difference between the expanded lengths is 0.01568 mm. Therefore, the buffer grooves 11c, 1 of the members 11, 12
The size of the holes 11a and 12a in the axial center direction is set to 0.
It is sufficient to set it to about 5 mm.
【００１７】このようなねじ部品締結構造では、温度上
昇に伴って、部材１１，１２、スリーブ１３，１４、ボ
ルト１５が当該ボルト１５の軸心方向へ熱膨張すると、
部材１１，１２とスリーブ１３，１４との熱膨張率の差
から、部材１１，１２の前記収納溝１１ｂ，１２ｂに上
記軸心方向内側への応力が加わるものの、部材１１，１
２の前記緩衝溝１１ｃ，１２ｃにより、部材１１，１２
が塑性変形せずに弾性変形するようになるので、部材１
１，１２に加わる上記軸心方向への負荷を緩衝すること
ができる。In such a screw component fastening structure, when the members 11 and 12, the sleeves 13 and 14, and the bolt 15 thermally expand in the axial direction of the bolt 15 as the temperature rises,
Due to the difference in the coefficient of thermal expansion between the members 11 and 12 and the sleeves 13 and 14, stress is applied to the storage grooves 11b and 12b of the members 11 and 12 inward in the axial direction.
The members 11 and 12 are formed by the two buffer grooves 11c and 12c.
Is elastically deformed without plastic deformation.
The axial load applied to the first and second shafts 12 can be buffered.
【００１８】従って、上述したような温度上昇が繰り返
されても、ボルト１５による締結力が低下することはな
い。Therefore, even if the above-described temperature rise is repeated, the fastening force by the bolt 15 does not decrease.
【００１９】なお、本実施の形態では、スリーブ１４の
内周面にねじ山１４ａを形成して、当該スリーブ１４に
ボルト１５を螺合することにより、部材１１，１２を締
結するようにしたが、これに限らず、例えば、図１
（ｂ）に示すように、スリーブ２３，２４の貫通穴２３
ａ，２４ａにボルト２５を挿通し、当該ボルト２５にス
チール製のワッシャ２６を介してスチール製のナット２
７を螺合することで部材１１，１２を締結するようにし
てもよい。In this embodiment, the members 11 and 12 are fastened by forming the thread 14a on the inner peripheral surface of the sleeve 14 and screwing the bolt 15 to the sleeve 14. , Not limited to this, for example, FIG.
As shown in (b), the through holes 23 of the sleeves 23, 24
a and 24a, and a steel nut 2 is inserted through the bolt 25 through a steel washer 26.
The members 11 and 12 may be fastened by screwing the 7.
【００２０】また、本実施の形態では、部材１１，１２
同士の当接面に穴１１ａ，１２ａの周面の周方向に沿っ
て緩衝溝１１ｃ，１２ｃをそれぞれ形成したが、これに
限らず、例えば、図２（ａ）に示すように、部材１１，
１２の間にシム３８（材質は特に限定されないが、部材
１１，１２以下の熱膨張率を有する材料であると好まし
い）を介在させることで隙間３８ａを形成するようにし
てもよいし、図２（ｂ）に示すように、部材１１，１２
の穴１１ａ，１２ａの内部部分に上記緩衝溝１１ｃ，１
２ｃと同様な隙間となる緩衝溝１１ｄ，１２ｄを形成す
るようにしてもよい。In this embodiment, the members 11 and 12 are used.
The buffer grooves 11c and 12c are formed on the contact surfaces of the respective members along the circumferential direction of the peripheral surfaces of the holes 11a and 12a. However, the present invention is not limited to this. For example, as shown in FIG.
A gap 38a may be formed by interposing a shim 38 (material is not particularly limited, but is preferably a material having a thermal expansion coefficient equal to or less than that of the members 11 and 12) between the members 12 and 12. As shown in FIG.
The inside of the holes 11a, 12a is provided with the buffer grooves 11c, 1
The buffer grooves 11d and 12d having the same gap as that of 2c may be formed.
【００２１】本実施の形態では、アルミニウム製の部材
をスチール製のボルトなどで締結する場合について説明
したが、これに限らず、ねじ部品よりも大きい熱膨張率
を有する複数の部材にそれぞれ形成された穴同士を上記
ねじ部品で連結して当該部材同士を締結するねじ部品締
結構造であれば、上述した場合と同様にして適用するこ
とができる。In this embodiment, the case in which the aluminum member is fastened with a steel bolt or the like has been described. However, the present invention is not limited to this, and each member is formed of a plurality of members having a larger coefficient of thermal expansion than the screw part. Any screw component fastening structure in which the holes are connected to each other with the screw components and the members are fastened can be applied in the same manner as in the above-described case.
【００２２】[0022]
【発明の効果】本発明によるねじ部品締結構造では、温
度上昇に伴って、部材にねじ部品の軸心方向への応力が
加わっても、部材が塑性変形せずに弾性変形するように
なるので、部材の上記軸心方向への負荷を緩衝すること
ができる。このため、温度変化が頻繁に生じる環境下で
用いても、ねじ部品による締結力の低下を抑えることが
できる。In the screw component fastening structure according to the present invention, even if a stress is applied to the member in the axial direction of the screw component as the temperature rises, the member is elastically deformed without plastic deformation. , The load on the member in the axial direction can be buffered. For this reason, even when used in an environment in which temperature changes frequently occur, it is possible to suppress a decrease in the fastening force due to the screw component.
【図１】本発明によるねじ部品締結構造の実施の形態の
概略構造を表す断面図である。FIG. 1 is a cross-sectional view illustrating a schematic structure of a screw component fastening structure according to an embodiment of the present invention.
【図２】本発明によるねじ部品締結構造の他の実施の形
態の概略構造を表す断面図である。FIG. 2 is a sectional view showing a schematic structure of another embodiment of the screw component fastening structure according to the present invention.
【図３】従来のねじ部品締結構造の一例の概略構造を表
す断面図である。FIG. 3 is a cross-sectional view illustrating a schematic structure of an example of a conventional screw component fastening structure.
１１，１２ 部材 １１ａ，１２ａ 穴 １１ｂ，１２ｂ 収納溝 １１ｃ，１２ｃ，１１ｄ，１２ｄ 緩衝溝 １３，１４，２３，２４ スリーブ １３ａ 貫通穴 １４ａ ねじ山 １３ｂ，１４ｂ，２３ｂ，２４ｂ フランジ １５，２５ ボルト ２６ ワッシャ ２７ ナット ３８ シム ３８ａ 隙間 11, 12 member 11a, 12a hole 11b, 12b storage groove 11c, 12c, 11d, 12d buffer groove 13, 14, 23, 24 sleeve 13a through hole 14a thread 13b, 14b, 23b, 24b flange 15, 25 bolt 26 washer 27 Nut 38 Shim 38a Clearance
フロントページの続き (58)調査した分野(Int.Cl.7，ＤＢ名) F16B 39/01 F16B 31/04 Continuation of the front page (58) Field surveyed (Int.Cl. 7 , DB name) F16B 39/01 F16B 31/04
Claims (4)
複数の部品にそれぞれ形成された穴同士を上記ねじ部品
で連結して当該部材同士を締結するねじ部品締結構造で
あって、締結方向外側に位置する前記部材の前記穴と前
記ねじ部品との間に当該ねじ部品と同等の熱膨張率を有
するスリーブを介装すると共に、当該スリーブの締結方
向外側の端部に当該スリーブの締結方向内側の端部より
も大径をなす大径部を設ける一方、前記部材の前記穴の
周面の周方向に沿って隙間を設けたことを特徴とするね
じ部品締結構造。1. A screw part fastening structure in which holes formed in a plurality of parts having a larger coefficient of thermal expansion than a screw part are connected to each other by the screw part, and the members are fastened to each other. A sleeve having a coefficient of thermal expansion equivalent to that of the threaded component is interposed between the hole of the member and the threaded component located at the end of the sleeve in the direction of fastening of the sleeve. A screw part fastening structure, wherein a large-diameter portion having a diameter larger than that of the end portion is provided, and a gap is provided along a circumferential direction of a peripheral surface of the hole of the member.
品の座面の大きさ以上の大きさを有することを特徴とす
る請求項１に記載のねじ部品締結構造。2. The screw component fastening structure according to claim 1, wherein the large diameter portion of the sleeve has a size equal to or larger than a size of a seating surface of the screw component.
あることを特徴とする請求項１または２に記載のねじ部
品締結構造。3. The screw component fastening structure according to claim 1, wherein the large-diameter portion of the sleeve is a flange.
記スリーブの前記大径部の径方向の大きさ以上の大きさ
を有すると共に、当該隙間の上記穴の軸心方向の大きさ
が前記部材の熱膨張率と上記スリーブの熱膨張率との差
に基づいて設定された大きさであることを特徴とする請
求項１から３のいずれかに記載のねじ部品締結構造。4. The size of the gap in the radial direction of the hole is equal to or greater than the size of the large diameter portion of the sleeve in the radial direction, and the size of the gap in the axial direction of the hole. The screw component fastening structure according to any one of claims 1 to 3, wherein the size is set based on a difference between a coefficient of thermal expansion of the member and a coefficient of thermal expansion of the sleeve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7317682A JP3055446B2 (en) | 1995-12-06 | 1995-12-06 | Screw part fastening structure |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP7317682A JP3055446B2 (en) | 1995-12-06 | 1995-12-06 | Screw part fastening structure |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH09158936A JPH09158936A (en) | 1997-06-17 |
| JP3055446B2 true JP3055446B2 (en) | 2000-06-26 |
Family
ID=18090852
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP7317682A Expired - Fee Related JP3055446B2 (en) | 1995-12-06 | 1995-12-06 | Screw part fastening structure |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3055446B2 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| USD977278S1 (en) | 2017-01-20 | 2023-02-07 | The Gillette Company Llc | Shaving razor stand |
| US11648693B2 (en) | 2017-01-20 | 2023-05-16 | The Gillette Company Llc | Personal care product docking system |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7484610B2 (en) * | 2004-03-10 | 2009-02-03 | Heidelberger Druckmaschinen | Apparatus for the actuation of clamping elements that can be controlled remotely |
| KR100922155B1 (en) * | 2008-02-15 | 2009-10-21 | 한국단자공업 주식회사 | Bracket of box |
| JP6087721B2 (en) * | 2013-05-09 | 2017-03-01 | 株式会社ティラド | Mounting structure of support material for heat exchanger |
| CA2907101C (en) * | 2013-05-21 | 2018-07-31 | Halliburton Energy Services, Inc. | Thermal securing set screws |
-
1995
- 1995-12-06 JP JP7317682A patent/JP3055446B2/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| USD977278S1 (en) | 2017-01-20 | 2023-02-07 | The Gillette Company Llc | Shaving razor stand |
| US11648693B2 (en) | 2017-01-20 | 2023-05-16 | The Gillette Company Llc | Personal care product docking system |
| US11648692B2 (en) | 2017-01-20 | 2023-05-16 | The Gillette Company, LLC | Personal care product docking system |
Also Published As
| Publication number | Publication date |
|---|---|
| JPH09158936A (en) | 1997-06-17 |
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