JP2021194461A - Angle adjuster and article of furniture using the same - Google Patents

Angle adjuster and article of furniture using the same Download PDF

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JP2021194461A
JP2021194461A JP2020105274A JP2020105274A JP2021194461A JP 2021194461 A JP2021194461 A JP 2021194461A JP 2020105274 A JP2020105274 A JP 2020105274A JP 2020105274 A JP2020105274 A JP 2020105274A JP 2021194461 A JP2021194461 A JP 2021194461A
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Prior art keywords
winding
rotating shaft
outer peripheral
winding member
peripheral surface
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JP6830703B1 (en
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雅伸 山下
Masanobu Yamashita
健 山脇
Takeshi Yamawaki
章史 澤田
Akifumi Sawada
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Koyo Giken KK
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Koyo Giken KK
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Priority to JP2020105274A priority Critical patent/JP6830703B1/en
Application filed by Koyo Giken KK filed Critical Koyo Giken KK
Publication of JP6830703B1 publication Critical patent/JP6830703B1/en
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Priority to CN202110302381.9A priority patent/CN113812800A/en
Priority to CN202120583649.6U priority patent/CN215959129U/en
Priority to KR1020210059919A priority patent/KR102523663B1/en
Priority to PL21178713.0T priority patent/PL3925488T3/en
Priority to EP21178713.0A priority patent/EP3925488B1/en
Priority to ES21178713T priority patent/ES2968611T3/en
Publication of JP2021194461A publication Critical patent/JP2021194461A/en
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    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C1/00—Chairs adapted for special purposes
    • A47C1/02—Reclining or easy chairs
    • A47C1/022—Reclining or easy chairs having independently-adjustable supporting parts
    • A47C1/024—Reclining or easy chairs having independently-adjustable supporting parts the parts, being the back-rest, or the back-rest and seat unit, having adjustable and lockable inclination
    • A47C1/027—Reclining or easy chairs having independently-adjustable supporting parts the parts, being the back-rest, or the back-rest and seat unit, having adjustable and lockable inclination by means of clamps or friction locking members
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C20/00—Head -, foot -, or like rests for beds, sofas or the like
    • A47C20/04—Head -, foot -, or like rests for beds, sofas or the like with adjustable inclination
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C1/00—Chairs adapted for special purposes
    • A47C1/02—Reclining or easy chairs
    • A47C1/022—Reclining or easy chairs having independently-adjustable supporting parts
    • A47C1/03—Reclining or easy chairs having independently-adjustable supporting parts the parts being arm-rests
    • A47C1/0308—Reclining or easy chairs having independently-adjustable supporting parts the parts being arm-rests adjustable by rotation
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C17/00—Sofas; Couches; Beds
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C17/00—Sofas; Couches; Beds
    • A47C17/04—Seating furniture, e.g. sofas, couches, settees, or the like, with movable parts changeable to beds; Chair beds
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C31/00—Details or accessories for chairs, beds, or the like, not provided for in other groups of this subclass, e.g. upholstery fasteners, mattress protectors, stretching devices for mattress nets
    • A47C31/02—Upholstery attaching means
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47C—CHAIRS; SOFAS; BEDS
    • A47C7/00—Parts, details, or accessories of chairs or stools
    • A47C7/36—Support for the head or the back
    • A47C7/38—Support for the head or the back for the head
    • A—HUMAN NECESSITIES
    • A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
    • A47G—HOUSEHOLD OR TABLE EQUIPMENT
    • A47G9/00—Bed-covers; Counterpanes; Travelling rugs; Sleeping rugs; Sleeping bags; Pillows
    • A47G9/10—Pillows

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  • Health & Medical Sciences (AREA)
  • General Health & Medical Sciences (AREA)
  • Nursing (AREA)
  • Dentistry (AREA)
  • Otolaryngology (AREA)
  • Pulmonology (AREA)
  • Chairs For Special Purposes, Such As Reclining Chairs (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Chair Legs, Seat Parts, And Backrests (AREA)

Abstract

To provide an angle adjuster and an article of furniture using the same, the angle adjuster avoiding a component part being broken or damaged when an overload is applied and being capable of reused when the overload is removed.SOLUTION: An angle adjuster is composed of: a support body 20; a revolving shaft 40 non-rotatably supported to one end of the support body 20; a winding-up member 50 in pressured contact with an outer peripheral surface 46 of the revolving shaft 40; and a swinging body 30 having an attachment part 32 provided on one end side thereof, the attachment part coupled to the revolving shaft 40 through the winding-up member 50. When an overload is applied to the swinging body 30, increase in friction force of the winding-up member 50 against the outer peripheral surface 46 of the revolving shaft 40 is limited and, thereby, the overload causes the winding-up member 50 to slide and rotate on the outer peripheral surface 46 of the revolving shaft 40.SELECTED DRAWING: Figure 14

Description

本発明は家具類などに用いられる角度調整器、特に、家具類に過荷重が負荷された場合に、構成部品の破壊や破損を回避できる角度調整器に関する。 The present invention relates to an angle adjuster used for furniture and the like, and particularly to an angle adjuster capable of avoiding destruction or breakage of components when an overload is applied to furniture.

従来、家具類に使用される角度調整器としては、例えば、ソファのヘッドレストやアームレストの傾斜角度を、使用者好みの角度に調整できる構成の関節装置が知られている(特許文献１参照)。
すなわち、特許文献１の図２示すように、カム板３の咬合許容部３ａ内に爪片４が入り込んでいる。そして、第一金具１に所定の荷重が負荷された場合、その荷重を咬合阻止部３ｂと咬合阻止部３ｂとの境界段部３２において爪片４に受け止められる。 Conventionally, as an angle adjuster used for furniture, for example, a joint device having a configuration in which the inclination angle of a sofa headrest or an armrest can be adjusted to an angle preferred by the user is known (see Patent Document 1).
That is, as shown in FIG. 2 of Patent Document 1, the claw piece 4 has entered the occlusal allowable portion 3a of the cam plate 3. Then, when a predetermined load is applied to the first metal fitting 1, the load is received by the claw piece 4 at the boundary step portion 32 between the occlusal blocking portion 3b and the occlusal blocking portion 3b.

特許第４５１９５５５号公報Japanese Patent No. 4519555

しかしながら、前記関節装置では、第一金具１に極めて大きな過荷重が負荷された場合に、構成部品であるカム板３、爪片４等にも過荷重が負荷される。結果として、カム板３等が破断して破壊され、あるいは、カム板３等に塑性変形が生じて破損する。このような破壊や破損が、例えば、ソファに組み込まれた関節装置に生じると、ソファを分解して修理しなければならない。特に、修理に手間がかかり、修理代が高い場合には、ソファ全体を廃棄しなければならないという問題点がある。
本発明は、前記問題点に鑑み、過荷重が負荷された場合に、角度調整器の構成部品に破壊や破損が生じることを回避し、過荷重の除去後に再使用できる角度調整器およびこれを用いた家具を提供することを課題とする。 However, in the joint device, when an extremely large overload is applied to the first metal fitting 1, the overload is also applied to the cam plate 3, the claw piece 4, etc., which are constituent parts. As a result, the cam plate 3 or the like is broken and destroyed, or the cam plate 3 or the like is plastically deformed and damaged. If such destruction or breakage occurs, for example, in a joint device built into the sofa, the sofa must be disassembled and repaired. In particular, there is a problem that the entire sofa must be discarded when the repair is troublesome and the repair cost is high.
In view of the above problems, the present invention is an angle adjuster that can be reused after the overload is removed by avoiding breakage or breakage of the components of the angle adjuster when an overload is applied. The subject is to provide the used furniture.

本発明に係る角度調整器は、前記課題を解決すべく、
支持体と、
前記支持体の一端部に回動不能に支持された回転軸と、
前記回転軸の外周面に圧接する巻締め部材と、
一端側に設けた取り付け部を前記巻締め部材を介して前記回転軸に連結した揺動体と、からなり、
前記巻締め部材が、前記回転軸に圧接する巻締め部材本体と、前記巻締め部材本体から延在し、かつ、前記回転軸の外周面に圧接する略Ｊ字形状の巻締め部と、および、前記巻締め部の自由端から延在し、かつ、前記揺動体の取付け部に連結された支持部とを備え、
前記揺動体の正回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が減少し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が減少することにより、前記揺動体の正回転方向の回動が許容される一方、
前記揺動体の逆回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が増大し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が増大することにより、前記揺動体の逆回転方向の回動を阻止するとともに、
前記揺動体に過荷重が逆回転方向において負荷された場合に、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成とした。 The angle adjuster according to the present invention solves the above-mentioned problems.
With the support,
A rotating shaft that is non-rotatably supported by one end of the support,
A winding member that is in pressure contact with the outer peripheral surface of the rotating shaft,
It is composed of a swinging body in which a mounting portion provided on one end side is connected to the rotating shaft via the winding member.
A winding member main body in which the winding member is in pressure contact with the rotating shaft, a substantially J-shaped winding portion extending from the winding member main body and in pressure contact with the outer peripheral surface of the rotating shaft, and A support portion extending from the free end of the winding portion and connected to the mounting portion of the rocking body.
Due to the rotation of the rocking body in the forward rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft is reduced, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. While the force is reduced, the rocking body is allowed to rotate in the forward rotation direction, while it is allowed to rotate.
Due to the rotation of the rocking body in the reverse rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft increases, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. By increasing the force, the rocking body is prevented from rotating in the reverse rotation direction, and at the same time, it is prevented from rotating in the reverse rotation direction.
When an overload is applied to the rocking body in the reverse rotation direction, the outer peripheral surface of the rotating shaft is tightened by the overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft. Is configured to slide and rotate.

本発明によれば、構成部品に塑性変形が生じる前に巻締め部材が回動することにより、構成部品の破壊や破損を回避できるので、過荷重の除去後に再使用できる角度調整器が得られる。 According to the present invention, since the winding member rotates before the component is plastically deformed, the component can be prevented from being broken or damaged, so that an angle adjuster that can be reused after removing the overload can be obtained. ..

本発明の実施形態としては、一対の前記巻締め部材で、前記揺動体の取り付け部を挟持してもよい。
本実施形態によれば、一対の巻締め部材で揺動体を挟持するので、保持強度が増大する。 In the embodiment of the present invention, the attachment portion of the rocking body may be sandwiched between the pair of the winding members.
According to the present embodiment, since the rocking body is sandwiched between the pair of winding members, the holding strength is increased.

本発明の他の実施形態としては、前記回転軸の外周面に突設した環状鍔部を、一対の前記巻締め部材で挟持してもよい。
本実施形態によれば、一対の巻締め部材で回転軸の環状鍔部を挟持するので、保持強度が増大する。 In another embodiment of the present invention, the annular flange portion protruding from the outer peripheral surface of the rotating shaft may be sandwiched between the pair of winding members.
According to the present embodiment, since the annular flange portion of the rotating shaft is sandwiched between the pair of winding members, the holding strength is increased.

本発明の別の実施形態としては、前記巻締め部材本体に設けた位置規制突部に、前記揺動体の取り付け部に設けた巻締め規制軸を当接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成としてもよい。
本実施形態によれば、過荷重によって構成部品に破壊や破損が生じる前に回転軸の外周面を巻締め部材が滑って回動する。このため、構成部品の破壊や破損を回避でき、過荷重の除去後に再使用できる角度調整器が得られる。 In another embodiment of the present invention, the winding restricting shaft provided in the mounting portion of the rocking body is brought into contact with the position regulating protrusion provided in the winding member main body to regulate the rotation of the rocking body. By limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft, the winding member may slide and rotate on the outer peripheral surface of the rotating shaft due to an overload.
According to the present embodiment, the winding member slides and rotates on the outer peripheral surface of the rotating shaft before the components are broken or damaged due to the overload. Therefore, it is possible to avoid breakage or breakage of the components, and it is possible to obtain an angle adjuster that can be reused after removing the overload.

本発明の異なる実施形態としては、前記巻締め部材本体に設けた位置規制突部に、前記巻締め部を当接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増加を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成としてもよい。
本実施形態によれば、巻締め部材本体に設けた位置規制突部に、前記巻締め部を当接させて揺動体の回動を規制する。このため、部品点数,組立工数が少ない角度調整器が得られる。 In a different embodiment of the present invention, the winding portion is brought into contact with the position-regulating protrusion provided on the winding member main body to restrict the rotation of the rocking body, and the winding is tightened with respect to the outer peripheral surface of the rotating shaft. By limiting the increase in the frictional force of the member, the winding member may slide and rotate on the outer peripheral surface of the rotating shaft due to an overload.
According to the present embodiment, the winding portion is brought into contact with the position regulating protrusion provided on the winding member main body to regulate the rotation of the rocking body. Therefore, an angle adjuster with a small number of parts and assembling man-hours can be obtained.

本発明の他の実施形態としては、前記巻締め部材の支持部に設けた巻締め規制長孔の一端部に、前記揺動体の取り付け部に設けた巻締め規制軸を圧接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増加を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成としてもよい。
本実施形態によれば、過荷重に対する摩擦力を巻締め規制長孔の位置、形状、大きさ、個数を適宜、選択して調整できるので、設計,製造が容易な角度調整器が得られる。 In another embodiment of the present invention, the winding restricting shaft provided in the mounting portion of the rocking body is pressed against one end of the winding restricting elongated hole provided in the support portion of the winding member to form the rocking body. By restricting the rotation and limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft, the winding member may slide and rotate on the outer peripheral surface of the rotating shaft due to an overload.
According to this embodiment, the frictional force against overload can be adjusted by appropriately selecting and adjusting the position, shape, size, and number of winding regulation elongated holes, so that an angle adjuster that is easy to design and manufacture can be obtained.

本発明に係る家具としては、前述に記載の角度調整器を備えた構成としてある。 The furniture according to the present invention has a configuration provided with the angle adjuster described above.

本発明によれば、角度調整器の構成部品に破壊や破損が生じることを回避でき、過荷重の除去後に再使用できる家具が得られる。このため、過荷重による構成部品の破壊や破損を原因とする修理が不要になり、家具全体を廃棄することがないという効果がある。 According to the present invention, it is possible to prevent the components of the angle adjuster from being broken or damaged, and it is possible to obtain furniture that can be reused after removing the overload. Therefore, there is no need for repairs caused by destruction or breakage of components due to overload, and there is an effect that the entire furniture is not discarded.

本発明に係る角度調整器を、例えば、ソファに適用した場合の一例を説明するための斜視図である。It is a perspective view for demonstrating an example of the case where the angle adjuster which concerns on this invention is applied to a sofa, for example. 図１に示したソファの要部の拡大斜視図である。It is an enlarged perspective view of the main part of the sofa shown in FIG. 本発明に係る角度調整器の第１実施形態に係る初期位置を示す全体斜視図である。It is an overall perspective view which shows the initial position which concerns on 1st Embodiment of the angle adjuster which concerns on this invention. 図３に示した角度調整器の分解斜視図である。It is an exploded perspective view of the angle adjuster shown in FIG. 図４に示した分解斜視図を異なる角度から見た分解斜視図である。It is an exploded perspective view which looked at the exploded perspective view shown in FIG. 4 from a different angle. 図３に示した角度調整器からカバーおよび補強板を取り外した状態を示す部分正面図である。It is a partial front view which shows the state which the cover and the reinforcing plate were removed from the angle adjuster shown in FIG. 図６に示したVII-VII線断面図である。FIG. 6 is a sectional view taken along line VII-VII shown in FIG. 図６に示した角度調整器の要部拡大分解斜視図である。FIG. 6 is an enlarged exploded perspective view of a main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the angle adjuster which concerns on this invention. 図９に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図９の初期状態（第１状態）から変位した第２状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 2nd state displaced from the initial state (1st state) of FIG. 図１１に示した角度調整器の要部拡大図である。FIG. 11 is an enlarged view of a main part of the angle adjuster shown in FIG. 図１１の状態から過荷重の負荷で変位した第３状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 3rd state which was displaced by the load of an overload from the state of FIG. 図１３に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１１の状態から変位した第４状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 4th state displaced from the state of FIG. 図１５に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１５の状態から変位した第５状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 5th state displaced from the state of FIG. 図１７に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１７の状態から変位した第６状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 6th state displaced from the state of FIG. 図１９に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の第２実施形態の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the 2nd Embodiment of the angle adjuster which concerns on this invention. 図２１に示した角度調整器の要部拡大図である。FIG. 21 is an enlarged view of a main part of the angle adjuster shown in FIG. 図２１に示した角度調整器に過荷重を負荷した状態を示す正面図である。It is a front view which shows the state which the overload is applied to the angle adjuster shown in FIG. 図２３に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の第３実施形態の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the 3rd Embodiment of the angle adjuster which concerns on this invention. 図２５に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図２５に示した角度調整器に過荷重を負荷した状態を示す正面図である。FIG. 5 is a front view showing a state in which an overload is applied to the angle adjuster shown in FIG. 25. 図２７に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 27.

本発明に係る角度調整器の実施形態を図１ないし図２８の添付図面に従って説明する。
図１および図２に示すように、第１実施形態に係る角度調整器１０は、ソファ１のアームレスト２およびヘッドレスト３に適用した場合である。例えば、ヘッドレスト３は、並設した一対の角度調整器１０，１０の間に架け渡した芯材４に、クッション材(図示せず)を取り付け、皮革，布地等の張地５で被覆することにより、形成されている。 An embodiment of the angle adjuster according to the present invention will be described with reference to the accompanying drawings of FIGS. 1 to 28.
As shown in FIGS. 1 and 2, the angle adjuster 10 according to the first embodiment is applied to the armrest 2 and the headrest 3 of the sofa 1. For example, in the headrest 3, a cushion material (not shown) is attached to a core material 4 spanned between a pair of angle adjusters 10 and 10 arranged side by side, and the headrest 3 is covered with an upholstery 5 such as leather or cloth. Is formed by.

角度調整器１０は、図３ないし図５に示すように、大略、支持体２０と揺動体３０とで構成されている。
支持体２０は、図４に示すように、丸棒材を略Ｌ字形状に屈曲した形状を有する。そして、支持体２０は、その下端部に設けた雌ネジ部２１に、抜け止め座金２２と座金２３とを挿通し、両者の間に配置した基材(図示せず)を六角ナット２４で固定できる。
また、支持体２０は、その水平端部に設けた六角孔２５に挿通した鍔付き六角ナット２８に、座金２６を介し、ボルト２７を螺合することにより、揺動体３０を連結できる（図７）。 As shown in FIGS. 3 to 5, the angle adjuster 10 is roughly composed of a support 20 and a rocking body 30.
As shown in FIG. 4, the support 20 has a shape in which a round bar member is bent into a substantially L shape. Then, in the support 20, the retaining washer 22 and the washer 23 are inserted into the female screw portion 21 provided at the lower end thereof, and the base material (not shown) arranged between the two is fixed with the hexagon nut 24. can.
Further, the support 20 can be connected to the rocking body 30 by screwing a bolt 27 to a hexagon nut 28 with a flange inserted into a hexagonal hole 25 provided at its horizontal end via a washer 26 (FIG. 7). ).

揺動体３０は、その一端側に芯材４をネジ固定するためのリブ３１を曲げ起こしてある一方、その他端部に取り付け部３２を設けてある。取り付け部３２は、図８に示すように、その先端の中央に軸受け凹部３３を設けてある。また、取り付け部３２は、その先端の下方縁部に下方受け部３４を設けてあるとともに、その先端の上方縁部に上方突部３５を設けてある。さらに、取り付け部３２は、カシメ孔３６を設けてあるとともに、軸孔３７を設けてある。 The rocking body 30 is provided with a rib 31 for fixing the core material 4 with screws on one end side thereof, while a mounting portion 32 is provided on the other end portion. As shown in FIG. 8, the mounting portion 32 is provided with a bearing recess 33 in the center of the tip thereof. Further, the mounting portion 32 is provided with a lower receiving portion 34 at the lower edge portion of the tip thereof, and an upper protrusion 35 is provided at the upper edge portion of the tip thereof. Further, the mounting portion 32 is provided with a caulking hole 36 and a shaft hole 37.

そして、揺動体３０の取り付け部３２には、図４に示すように、回転軸４０の環状鍔部４２を挟持するように配置した巻締め部材５０，５０を、一対の補強板６２,６２を介して取り付けてある。このため、回転軸４０は、揺動体３０の延長線上に位置している。 Then, as shown in FIG. 4, the mounting portion 32 of the rocking body 30 is provided with winding members 50, 50 arranged so as to sandwich the annular flange portion 42 of the rotating shaft 40, and a pair of reinforcing plates 62, 62. It is attached via. Therefore, the rotating shaft 40 is located on the extension line of the rocking body 30.

回転軸４０は、図８に示すように、六角孔４１を有し、その外周面４６に突設した環状鍔部４２に第１、第２、第３爪部４３、４４、４５を所定のピッチで突設してある。 As shown in FIG. 8, the rotary shaft 40 has a hexagonal hole 41, and the first, second, and third claw portions 43, 44, and 45 are predetermined to the annular flange portion 42 projecting from the outer peripheral surface 46 thereof. It is projected on the pitch.

巻締め部材５０は、巻締め部材本体５１と、巻締め部材本体５１から延在し、かつ、前記回転軸４０の外周面４６に係合可能な形状を有する略Ｊ字形状の巻締め部５２と、巻締め部５２の自由端から延在する支持部５３と、で構成されている。このため、回転軸４０の外周面４６と巻締め部５２の内側面５４とが面接触可能となる（図７）。また、巻締め部材本体５１には、カシメ孔５５と、長孔５６とが設けられているとともに、位置規制突部５７が突設されている。また、支持部５３にはカシメ孔５８が設けられている。 The winding member 50 extends from the winding member main body 51 and the winding member main body 51, and has a substantially J-shaped winding portion 52 having a shape that can be engaged with the outer peripheral surface 46 of the rotary shaft 40. And a support portion 53 extending from the free end of the winding portion 52. Therefore, the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 can be in surface contact with each other (FIG. 7). Further, the winding member main body 51 is provided with a caulking hole 55 and an elongated hole 56, and a position restricting protrusion 57 is provided so as to project. Further, the support portion 53 is provided with a caulking hole 58.

次に、第１実施形態に係る角度調整器１０の組立方法について説明する。
回転軸４０の両側から巻締め部材５０，５０を組み付けた後、巻締め部材５０，５０の支持部５３，５３の間に、揺動体３０の取り付け部３２を挿入して位置決めする。
そして、取り付け部３２の軸孔３７に巻締め規制軸６０を嵌合するとともに、巻締め部材５０の長孔５６に解除軸６１を嵌合する。
さらに、巻締め部材５０，５０の外向面に補強板６２，６２をそれぞれ組み付け、補強板６２の嵌合孔６２ａを巻締め規制軸６０に嵌合する。ついで、第１リベット６３を、補強板６２のカシメ孔６２ｂ、巻締め部材５０のカシメ孔５８および揺動体３０のカシメ孔３６に挿通し、カシメ固定する。
同様に、第２リベット６４を、補強板６２のカシメ孔６２ｃ、巻締め部材５０のカシメ孔５５に挿通するとともに、揺動体３０の軸受け凹部３３に嵌合し、カシメ固定することにより、揺動体３０の組立が完了する。
したがって、第１，第２リベット６３，６４および巻締め規制軸６０のそれぞれの支点間距離は、一定である。また、解除軸６１は脱落することなく保持される。 Next, the method of assembling the angle adjuster 10 according to the first embodiment will be described.
After assembling the winding members 50 and 50 from both sides of the rotating shaft 40, the mounting portion 32 of the rocking body 30 is inserted between the support portions 53 and 53 of the winding members 50 and 50 for positioning.
Then, the winding restricting shaft 60 is fitted into the shaft hole 37 of the mounting portion 32, and the release shaft 61 is fitted into the elongated hole 56 of the winding member 50.
Further, the reinforcing plates 62 and 62 are assembled on the outward surfaces of the winding members 50 and 50, respectively, and the fitting hole 62a of the reinforcing plate 62 is fitted to the winding regulation shaft 60. Then, the first rivet 63 is inserted into the caulking hole 62b of the reinforcing plate 62, the caulking hole 58 of the winding member 50, and the caulking hole 36 of the rocking body 30, and is caulked and fixed.
Similarly, the second rivet 64 is inserted into the caulking hole 62c of the reinforcing plate 62 and the caulking hole 55 of the winding member 50, and is fitted into the bearing recess 33 of the rocking body 30 and crimped to fix the rocking body. The assembly of 30 is completed.
Therefore, the distances between the fulcrums of the first and second rivets 63 and 64 and the winding restricting shaft 60 are constant. Further, the release shaft 61 is held without falling off.

そして、巻締め部材５０全体を被覆可能な正面形状を有するカバー７０，７２を前後から組み合わせ、相互に着脱可能に係合一体化する。ついで、カバー７０の嵌合孔７１から鍔付き六角ナット２８を挿通し、回転軸４０の六角孔４１に挿通した後、カバー７２の嵌合孔７３から突出させる。さらに、嵌合孔７３から突出する鍔付き六角ナット２８の先端を支持体２０の六角孔２５に挿通し、座金２６を介してボルト２７を螺合する。この結果、支持体２０と揺動体３０とが連結一体化され、支持体２０に対して回転軸４０が回動不能に支持される。 Then, the covers 70 and 72 having a front shape capable of covering the entire winding member 50 are combined from the front and back, and are detachably engaged and integrated with each other. Then, the hexagon nut 28 with a flange is inserted through the fitting hole 71 of the cover 70, inserted into the hexagonal hole 41 of the rotating shaft 40, and then projected from the fitting hole 73 of the cover 72. Further, the tip of the flanged hexagon nut 28 protruding from the fitting hole 73 is inserted into the hexagonal hole 25 of the support 20, and the bolt 27 is screwed through the washer 26. As a result, the support 20 and the rocking body 30 are connected and integrated, and the rotating shaft 40 is non-rotatably supported with respect to the support 20.

次に、第１実施形態に係る角度調整器の操作工程を、図９ないし図２０に基づいて説明する。
初期位置である第１状態おいて、図９および図１０に示すように、回転軸４０の外周面４６にバネ弾性を有する巻締め部材５０が嵌合している。このため、回転軸４０の外周面４６に巻締め部材本体５１と略Ｊ字形状の巻締め部５２とが所定の圧力で面接触し、摩擦力が生じているので、揺動体３０にガタツキはない。このとき、巻締め部材本体５１と巻締め部５２との距離はｌ0である。 Next, the operation step of the angle adjuster according to the first embodiment will be described with reference to FIGS. 9 to 20.
In the first state, which is the initial position, as shown in FIGS. 9 and 10, a winding member 50 having spring elasticity is fitted to the outer peripheral surface 46 of the rotating shaft 40. For this reason, the winding member main body 51 and the substantially J-shaped winding portion 52 are in surface contact with the outer peripheral surface 46 of the rotating shaft 40 at a predetermined pressure, and a frictional force is generated, so that the rocking body 30 is not rattled. No. At this time, the distance between the winding member main body 51 and the winding portion 52 is l 0 .

第２状態は、図１１および図１２に示すように、第１状態における揺動体３０を矢印Ｐ方向（正回転方向）に引き起こして回動させると、第２リベット６４を支点として揺動体３０が回動する。このとき、第２リベット６４を介して巻締め部材本体５１は回転軸４０の外周面４６に押圧されて変位しないが、巻締め部５２が第１リベット６３を介して引き上げられる。このため、巻締め部材本体５１と巻締め部５２との間が距離ｌ１（＞ｌ0）に拡大し、回転軸４０に対する巻締め部材５０の巻締め力が減少する。よって、回転軸４０の外周面４６と巻締め部５２の内側面５４との間の摩擦力が減少し、揺動体３０を使用者好みの傾斜角度まで引き起こすことができる。 In the second state, as shown in FIGS. 11 and 12, when the rocking body 30 in the first state is triggered and rotated in the arrow P direction (forward rotation direction), the rocking body 30 is rotated with the second rivet 64 as a fulcrum. Rotate. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the winding portion 52 is pulled up via the first rivet 63. Therefore, the distance between the winding member main body 51 and the winding portion 52 is expanded to a distance l 1 (> l 0 ), and the winding force of the winding member 50 with respect to the rotating shaft 40 is reduced. Therefore, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 is reduced, and the rocking body 30 can be caused to an inclination angle preferred by the user.

そして、例えば、第２状態で使用者がヘッドレスト３に頭を乗せ、揺動体３０に所定の荷重を矢印Ｑ方向（逆回転方向）に負荷すると、揺動体３０は第２リベット６４を支点として回動する。このとき、第２リベット６４を介して巻締め部材本体５１は回転軸４０の外周面４６に押圧されて変位しないが、第１リベット６３を介して巻締め部５２が引き下げられる。このため、巻締め部材本体５１に巻締め部５２が接近し、両者の間が距離ｌ２（＜ｌ0）に縮まり、回転軸４０に対する巻締め部材５０の締め付け力が増大する。よって、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が増大し、揺動体３０は回動できず、ヘッドレスト３は使用者の好みの傾斜角度を保持する。アームレスト２に適用した場合も同様である。 Then, for example, when the user puts his head on the headrest 3 in the second state and applies a predetermined load to the rocking body 30 in the arrow Q direction (reverse rotation direction), the rocking body 30 rotates with the second rivet 64 as a fulcrum. Move. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the winding portion 52 is pulled down via the first rivet 63. Therefore, the winding portion 52 approaches the winding member main body 51, the distance between the two is reduced to l 2 (<l 0 ), and the tightening force of the winding member 50 with respect to the rotating shaft 40 increases. Therefore, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, the rocking body 30 cannot rotate, and the headrest 3 maintains the inclination angle preferred by the user. The same applies when applied to the armrest 2.

なお、第２状態において、極めて大きい過荷重がＱ方向（逆回転方向）に負荷された場合、図１３および図１４に示す第３状態となる。
すなわち、揺動体３０が第２リベット６４を支点として回動し、第２状態よりも巻締め部５２が更に引き下げられる。このため、巻締め部材本体５１と巻締め部５２との距離が距離ｌ３（＜ｌ２）に縮まるが、巻締め規制軸６０が巻締め部材本体５１の位置規制突部５７に当接し、揺動体３０の回動が阻止される。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が最大摩擦力となり、摩擦力はそれ以上増大しない。
したがって、揺動体３０に負荷される矢印Ｑ方向（逆回転方向）の過荷重が前述の最大摩擦力を超える場合には、巻締め部材５０は回転軸４０の外周面４６上を滑って回動する。このため、巻締め部材５０だけでなく、回転軸４０、揺動体３０などの構成部品に破壊や破損が生ぜず、角度調整器１０は破壊されず、破損しない。
要するに、本発明に係る角度調整器によれば、過荷重が負荷された場合には、巻締め部材５０等の構成部品に破壊や破損が生ぜず、角度調整器１０の破壊や破損を回避できるという利点がある。 In the second state, when an extremely large overload is applied in the Q direction (reverse rotation direction), the third state shown in FIGS. 13 and 14 is obtained.
That is, the rocking body 30 rotates around the second rivet 64 as a fulcrum, and the winding portion 52 is further pulled down from the second state. Therefore, the distance between the winding member main body 51 and the winding portion 52 is reduced to the distance l 3 (<l 2 ), but the winding restricting shaft 60 comes into contact with the position restricting protrusion 57 of the winding member main body 51. The rotation of the rocking body 30 is prevented. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 becomes the maximum frictional force, and the frictional force does not increase any more.
Therefore, when the overload in the arrow Q direction (reverse rotation direction) applied to the rocking body 30 exceeds the above-mentioned maximum frictional force, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40 and rotates. do. Therefore, not only the winding member 50 but also the components such as the rotating shaft 40 and the rocking body 30 are not destroyed or damaged, and the angle adjuster 10 is not destroyed or damaged.
In short, according to the angle adjuster according to the present invention, when an overload is applied, the components such as the winding member 50 are not destroyed or damaged, and the angle adjuster 10 can be avoided from being destroyed or damaged. There is an advantage.

次に、図１５および図１６に示す第４状態は、第２状態から揺動体３０を矢印Ｐ方向（正回転方向）に更に回動し、傾斜角度を調整できる最大範囲まで変位させた状態を示す。このとき、解除軸６１が回転軸４０の第２爪部４４に係止しているとともに、下方受け部３４に圧接している。また、巻締め部材本体５１と巻締め部５２との間は距離ｌ１である。
そして、揺動体３０に荷重を矢印Ｑ方向（逆回転方向）に負荷した場合には、揺動体３０は第２リベット６４を支点として回動する。このとき、第２リベット６４を介して巻締め部材本体５１が回転軸４０の外周面４６に押圧されて変位しないが、第１リベット６３を介して巻締め部５２が引っ張られる。このため、巻締め部材本体５１に巻締め部５２が接近して距離ｌ２（＜ｌ0）に縮まり、回転軸４０に対する巻締め部材５０の締め付け力が増大する。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が増大し、揺動体３０は回動できない。よって、ヘッドレスト３は使用者の好みの傾斜角度を保持する。 Next, the fourth state shown in FIGS. 15 and 16 is a state in which the rocking body 30 is further rotated in the arrow P direction (forward rotation direction) from the second state and displaced to the maximum range in which the tilt angle can be adjusted. show. At this time, the release shaft 61 is locked to the second claw portion 44 of the rotary shaft 40 and is in pressure contact with the lower receiving portion 34. Further, the distance l 1 is between the winding member main body 51 and the winding portion 52.
When a load is applied to the rocking body 30 in the arrow Q direction (reverse rotation direction), the rocking body 30 rotates with the second rivet 64 as a fulcrum. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the winding portion 52 is pulled through the first rivet 63. Therefore, the winding portion 52 approaches the winding member main body 51 and shrinks to a distance l 2 (<l 0 ), and the tightening force of the winding member 50 with respect to the rotating shaft 40 increases. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 cannot rotate. Therefore, the headrest 3 holds the user's favorite tilt angle.

第５状態は、図１７および図１８に示すように、第４状態から更にＰ方向（正回転方向）に揺動体３０を回動した場合である。
すなわち、揺動体３０を回動すると、第２爪部４４に係止する解除軸６１に下方受け部３４が乗り上げ、ロック状態となる。このため、解除軸６１が巻締め部材本体５１を介して回転軸４０に圧接し、巻締め部材本体５１の変位を規制する。同時に、上方突部３５が第３爪部４５に当接して位置規制される。この結果、巻締め部材本体５１と巻締め部５２との間は距離ｌ４（＞ｌ0）となり、回転軸４０に対する巻締め部材５０の巻締め力が減少する。よって、回転軸４０の外周面４６と巻締め部５２の内側面５４との間の摩擦力が減少した状態が保持され、揺動体３０を矢印Ｑ方向（逆回転方向）に回動できる。 The fifth state is a case where the rocking body 30 is further rotated in the P direction (forward rotation direction) from the fourth state, as shown in FIGS. 17 and 18.
That is, when the rocking body 30 is rotated, the lower receiving portion 34 rides on the release shaft 61 that is locked to the second claw portion 44, and is in a locked state. Therefore, the release shaft 61 is pressed against the rotating shaft 40 via the winding member main body 51 to regulate the displacement of the winding member main body 51. At the same time, the upper protrusion 35 abuts on the third claw portion 45 and the position is restricted. As a result, the distance between the winding member main body 51 and the winding portion 52 becomes l 4 (> l 0 ), and the winding force of the winding member 50 with respect to the rotating shaft 40 is reduced. Therefore, the state in which the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 is reduced is maintained, and the rocking body 30 can be rotated in the arrow Q direction (reverse rotation direction).

第６状態は、図１９および図２０に示すように、第５状態から揺動体３０を矢印Ｑ方向（逆回転方向）に回動させると、第２リベット６４を支点として巻締め部材本体５１が逆方向に回動する。そして、解除軸６１が第１爪部４３に係止して位置規制されるので、解除軸６１に乗り上げていた下方受け部３４が解除軸６１から外れる。さらに、揺動体３０を矢印Ｑ方向（逆回転方向）に回動することにより、初期状態である第１状態に復帰する。
以後、同様な操作を行うことにより、揺動体３０を操作できる。 In the sixth state, as shown in FIGS. 19 and 20, when the rocking body 30 is rotated in the arrow Q direction (reverse rotation direction) from the fifth state, the winding member main body 51 uses the second rivet 64 as a fulcrum. Rotate in the opposite direction. Then, since the release shaft 61 is locked to the first claw portion 43 and the position is restricted, the lower receiving portion 34 riding on the release shaft 61 is disengaged from the release shaft 61. Further, by rotating the rocking body 30 in the direction of arrow Q (reverse rotation direction), the first state, which is the initial state, is restored.
After that, the rocking body 30 can be operated by performing the same operation.

本発明に係る角度調整器の第２実施形態は、図２１ないし図２４に示すように、前述の第１実施形態とほぼ同様である。
すなわち、図２１および図２２に示す第１状態（初期状態）で、揺動体３０を矢印Ｐ方向（正回転方向）に回動させると、巻締め部材本体５１と巻締め部５２との間の距離ｌ０が距離ｌ１（図示せず）に広がる。このため、回転軸４０に対する巻締め部材本体５１と巻締め部５２とによる締め付け力が減少し、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が減少する。この結果、揺動体３０を所望の傾斜角度まで調整することができる。 As shown in FIGS. 21 to 24, the second embodiment of the angle adjuster according to the present invention is substantially the same as the first embodiment described above.
That is, when the rocking body 30 is rotated in the arrow P direction (forward rotation direction) in the first state (initial state) shown in FIGS. 21 and 22, between the winding member main body 51 and the winding portion 52. Distance l 0 extends to distance l 1 (not shown). Therefore, the tightening force between the winding member main body 51 and the winding portion 52 with respect to the rotating shaft 40 is reduced, and the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner side surface 54 of the winding portion 52 is reduced. As a result, the rocking body 30 can be adjusted to a desired tilt angle.

そして、揺動体３０に通常の荷重が矢印Ｑ方向（逆回転方向）に負荷された場合には、第２リベット６４を回動支点として揺動体３０が回動する。このとき、第２リベット６４を介して巻締め部材本体５１が回転軸４０の外周面４６に押圧されて変位しないが、第１リベット６３を介して巻締め部５２が引き下げられる。このため、巻締め部５２と巻締め部材本体５１との間の距離が縮まり、巻締め部材本体５１と巻締め部５２とによる締め付け力が増大する。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が増大し、揺動体３０は使用者好みの傾斜角度で保持される。 When a normal load is applied to the rocking body 30 in the arrow Q direction (reverse rotation direction), the rocking body 30 rotates with the second rivet 64 as a rotation fulcrum. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the winding portion 52 is pulled down via the first rivet 63. Therefore, the distance between the winding member main body 52 and the winding member main body 51 is shortened, and the tightening force between the winding member main body 51 and the winding member main body 52 is increased. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 is held at an inclination angle preferred by the user.

しかし、図２３および図２４に示すように、揺動体３０に極めて大きな過荷重が負荷された場合には、巻締め部５２が位置規制突部５７に直接、当接して位置規制され、揺動体３０の回動が阻止される。このため、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が最大摩擦力となり、それ以上に摩擦力は増大しない。この結果、最大摩擦力を超える過荷重が揺動体３０に負荷された場合には、巻締め部材５０が回転軸４０の外周面４６上を滑り、揺動体３０が回動する。よって、巻締め部材５０だけでなく、回転軸４０、揺動体３０などの構成部品が破壊されず、破損しないので、角度調整器１０の破壊や破損を防止できる。
他は前述の第１実施形態とほぼ同様であるので、同一部分には同一番号を附して説明を省略する。 However, as shown in FIGS. 23 and 24, when an extremely large overload is applied to the rocking body 30, the winding portion 52 directly abuts on the position restricting protrusion 57 to regulate the position, and the rocking body is regulated. The rotation of 30 is blocked. Therefore, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 becomes the maximum frictional force, and the frictional force does not increase any more. As a result, when an overload exceeding the maximum frictional force is applied to the rocking body 30, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40, and the rocking body 30 rotates. Therefore, not only the winding member 50 but also the components such as the rotating shaft 40 and the rocking body 30 are not destroyed and are not damaged, so that the angle adjuster 10 can be prevented from being destroyed or damaged.
Since the other parts are almost the same as those of the above-described first embodiment, the same parts are designated by the same numbers and the description thereof will be omitted.

本実施形態によれば、巻締め規制軸６０が不要になり、第１実施形態よりも部品点数、組立工数の少ない角度調整器が得られるという利点がある。 According to this embodiment, there is an advantage that the winding regulation shaft 60 becomes unnecessary, and an angle adjuster having a smaller number of parts and assembling man-hours can be obtained as compared with the first embodiment.

本発明に係る角度調整器の第３実施形態は、図２５ないし図２８に示すように、前述の第１実施形態とほぼ同様である。
異なる点は、巻締め部材５０の支持部５３に設けた巻締め規制長孔５９に、揺動体３０の取り付け部３２に設けた巻締め規制軸６５を、嵌合した点である。 As shown in FIGS. 25 to 28, the third embodiment of the angle adjuster according to the present invention is substantially the same as the first embodiment described above.
The difference is that the winding regulation shaft 65 provided in the mounting portion 32 of the rocking body 30 is fitted into the winding regulation elongated hole 59 provided in the support portion 53 of the winding member 50.

そして、図２５および図２６に示す第１状態（初期状態）で、揺動体３０を矢印Ｐ方向（正回転方向）に回動させると、巻締め部材本体５１と巻締め部５２との間は距離ｌ０から距離ｌ１（図示せず）に広がる。このため、回転軸４０に対する巻締め部材本体５１と巻締め部５２との締め付け力が減少し、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が減少する。この結果、揺動体３０を使用者好みの傾斜角度に調整できる。 Then, in the first state (initial state) shown in FIGS. 25 and 26, when the rocking body 30 is rotated in the arrow P direction (forward rotation direction), the space between the winding member main body 51 and the winding portion 52 is It extends from distance l 0 to distance l 1 (not shown). Therefore, the tightening force between the winding member main body 51 and the winding portion 52 with respect to the rotating shaft 40 is reduced, and the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner side surface 54 of the winding portion 52 is reduced. As a result, the rocking body 30 can be adjusted to the inclination angle preferred by the user.

一方、揺動体３０に通常の荷重が矢印Ｑ方向に負荷された場合には、第２リベット６４を回動支点として揺動体３０が回動する。このとき、巻締め部材本体５１は回転軸４０に圧接して変位しないが、第１リベット６３を介して巻締め部５２が引き下げられる。このため、巻締め部５２と巻締め部材本体５１との間の距離が縮まり、巻締め部材本体５１と巻締め部５２とによる締め付け力が増大する。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が増大し、揺動体３０は使用者好みの傾斜角度で保持される。 On the other hand, when a normal load is applied to the rocking body 30 in the direction of arrow Q, the rocking body 30 rotates with the second rivet 64 as a rotation fulcrum. At this time, the winding member main body 51 is pressed against the rotating shaft 40 and is not displaced, but the winding portion 52 is pulled down via the first rivet 63. Therefore, the distance between the winding member main body 52 and the winding member main body 51 is shortened, and the tightening force between the winding member main body 51 and the winding member main body 52 is increased. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 is held at an inclination angle preferred by the user.

しかし、図２７および図２８に示すように、揺動体３０に過荷重が矢印Ｑ方向（逆回転方向）に負荷された場合には、巻締め規制長孔５９の一端部に巻締め規制軸６５が圧接して位置規制される。このとき、巻締め部５２と巻締め部材本体５１とが接近し、距離ｌ３（＜ｌ０）となっても、それ以上に縮まることがない。このため、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が最大摩擦力となり、それ以上に摩擦力は増大しない。この結果、最大摩擦力を超える過荷重が揺動体３０に負荷された場合には、巻締め部材５０が回転軸４０の外周面４６上を滑り、揺動体３０が回動する。よって、巻締め部材５０だけでなく、回転軸４０、揺動体３０などを含む構成部品が破壊されず、破損しないので、角度調整器１０の破壊や破損を防止できる。
他は前述の第１実施形態とほぼ同様であるので、同一部分には同一番号を附して説明を省略する。 However, as shown in FIGS. 27 and 28, when an overload is applied to the rocking body 30 in the arrow Q direction (reverse rotation direction), the winding regulation shaft 65 is placed on one end of the winding regulation elongated hole 59. Is pressed and the position is regulated. At this time, even if the winding portion 52 and the winding member main body 51 come close to each other and the distance is l 3 (<l 0 ), the winding portion 52 does not shrink any further. Therefore, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 becomes the maximum frictional force, and the frictional force does not increase any more. As a result, when an overload exceeding the maximum frictional force is applied to the rocking body 30, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40, and the rocking body 30 rotates. Therefore, not only the winding member 50 but also the components including the rotating shaft 40, the rocking body 30, and the like are not destroyed and are not damaged, so that the angle adjuster 10 can be prevented from being destroyed or damaged.
Since the other parts are almost the same as those of the above-described first embodiment, the same parts are designated by the same numbers and the description thereof will be omitted.

第３実施形態によれば、最大摩擦力は、巻締め規制長孔５９および巻締め規制軸６５の形状および位置関係等を調整して設計できる。このため、安定動作する角度調整器の設計、製造が容易になるという利点がある。 According to the third embodiment, the maximum frictional force can be designed by adjusting the shape and positional relationship of the winding regulation elongated hole 59 and the winding regulation shaft 65. Therefore, there is an advantage that the design and manufacture of the angle adjuster that operates stably becomes easy.

本発明は、前述のソファのヘッドレスト、アームレストに限らず、例えば、折り畳み式のベッドなどの家具、車および飛行機などの座席にも適用可能である。 The present invention is not limited to the above-mentioned sofa headrests and armrests, but is also applicable to furniture such as foldable beds and seats such as cars and airplanes.

１ ソファ
２ アームレスト
３ ヘッドレスト
４ 芯材
５ 張地
１０ 角度調整器
２０ 支持体
２１ 雌ネジ部
２２ 抜け止め座金
２３ 座金
２４ 六角ナット
２５ 六角孔
２７ ボルト
２８ 鍔付き六角ナット
３０ 揺動体
３１ リブ
３２ 取り付け部
３３ 軸受け凹部
３４ 下方受け部
３５ 上方突部
３６ カシメ孔
３７ 軸孔
４０ 回転軸
４１ 六角孔
４２ 環状鍔部
４３ 第１爪部
４４ 第２爪部
４５ 第３爪部
４６ 外周面
５０ 巻締め部材
５１ 巻締め部材本体
５２ 巻締め部
５３ 支持部
５４ 内側面
５５ カシメ孔
５６ 長孔
５７ 位置規制突部
５８ カシメ孔
５９ 巻締め規制長孔
６０ 巻締め規制軸
６１ 解除軸
６２ 補強板
６２ａ 嵌合孔
６２ｂ カシメ孔
６２ｃ カシメ孔
６３ 第１リベット
６４ 第２リベット
６５ 巻締め規制軸
７０ カバー
７１ 嵌合孔
７２ カバー
７３ 嵌合孔
Ｐ方向 正回転方向
Ｑ方向 逆回転方向 1 Sofa 2 Armrest 3 Headrest 4 Core material 5 Upholstery 10 Angle adjuster 20 Support 21 Female thread part 22 Retaining seat washer 23 Washer 24 Hexagon nut 25 Hexagonal hole 27 Bolt 28 Hexagon nut with rivet 30 Rocking body 31 Rivet 32 Mounting part 33 Bearing recess 34 Lower receiving part 35 Upper protrusion 36 Caulking hole 37 Shaft hole 40 Rotating shaft 41 Hexagonal hole 42 Circular flange part 43 1st claw part 44 2nd claw part 45 3rd claw part 46 Outer peripheral surface 50 Winding member 51 Winding member Main body 52 Winding part 53 Support part 54 Inner side surface 55 Caulking hole 56 Long hole 57 Position restricting protrusion 58 Caulking hole 59 Winding restricting long hole 60 Winding restricting shaft 61 Release shaft 62 Reinforcing plate 62a Fitting hole 62b Caulking hole 62c Caulking hole 63 1st rivet 64 2nd rivet 65 Tightening control shaft 70 Cover
71 Fitting hole 72 Cover 73 Fitting hole P direction Forward rotation direction Q direction Reverse rotation direction

本発明は家具類などに用いられる角度調整器、特に、家具類に過荷重が負荷された場合
に、構成部品の破壊や破損を回避できる角度調整器に関する。 The present invention relates to an angle adjuster used for furniture and the like, and particularly to an angle adjuster capable of avoiding destruction or breakage of components when an overload is applied to furniture.

従来、家具類に使用される角度調整器としては、例えば、ソファのヘッドレストやアー
ムレストの傾斜角度を、使用者好みの角度に調整できる構成の関節装置が知られている(
特許文献１参照)。
すなわち、特許文献１の図２示すように、カム板３の咬合許容部３ａ内に爪片４が入り
込んでいる。そして、第一金具１に所定の荷重が負荷された場合、その荷重を咬合阻止部
３ｂと咬合阻止部３ｂとの境界段部３２において爪片４に受け止められる。 Conventionally, as an angle adjuster used for furniture, for example, a joint device having a configuration in which the inclination angle of a sofa headrest or an armrest can be adjusted to an angle preferred by the user is known (
See Patent Document 1).
That is, as shown in FIG. 2 of Patent Document 1, the claw piece 4 has entered the occlusal allowable portion 3a of the cam plate 3. Then, when a predetermined load is applied to the first metal fitting 1, the load is received by the claw piece 4 at the boundary step portion 32 between the occlusal blocking portion 3b and the occlusal blocking portion 3b.

特許第４５１９５５５号公報Japanese Patent No. 4519555

しかしながら、前記関節装置では、第一金具１に極めて大きな過荷重が負荷された場合
に、構成部品であるカム板３、爪片４等にも過荷重が負荷される。結果として、カム板３
等が破断して破壊され、あるいは、カム板３等に塑性変形が生じて破損する。このような
破壊や破損が、例えば、ソファに組み込まれた関節装置に生じると、ソファを分解して修
理しなければならない。特に、修理に手間がかかり、修理代が高い場合には、ソファ全体
を廃棄しなければならないという問題点がある。
本発明は、前記問題点に鑑み、過荷重が負荷された場合に、角度調整器の構成部品に破
壊や破損が生じることを回避し、過荷重の除去後に再使用できる角度調整器およびこれを
用いた家具を提供することを課題とする。 However, in the joint device, when an extremely large overload is applied to the first metal fitting 1, the overload is also applied to the cam plate 3, the claw piece 4, etc., which are constituent parts. As a result, the cam plate 3
Etc. are broken and destroyed, or the cam plate 3 and the like are plastically deformed and damaged. If such destruction or breakage occurs, for example, in a joint device built into the sofa, the sofa must be disassembled and repaired. In particular, there is a problem that the entire sofa must be discarded when the repair is troublesome and the repair cost is high.
In view of the above problems, the present invention is an angle adjuster that can be reused after the overload is removed by avoiding breakage or breakage of the components of the angle adjuster when an overload is applied. The subject is to provide the used furniture.

本発明に係る角度調整器は、前記課題を解決すべく、
支持体と、
前記支持体の一端部に回動不能に支持された回転軸と、
前記回転軸の外周面に圧接する巻締め部材と、
一端側に設けた取り付け部を前記巻締め部材を介して前記回転軸に連結した揺動体と、からなり、
前記巻締め部材が、前記回転軸に圧接する巻締め部材本体と、前記巻締め部材本体から延在し、かつ、前記回転軸の外周面に圧接する略Ｊ字形状の巻締め部と、および、前記巻締め部の自由端から延在し、かつ、前記揺動体の取付け部に連結された支持部とを備え、
前記揺動体の正回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が減少し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が減少することにより、前記揺動体の正回転方向の回動が許容される一方、
前記揺動体の逆回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が増大し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が増大することにより、前記揺動体の逆回転方向の回動を阻止するとともに、
前記巻締め部材本体に設けた位置規制突部に、前記揺動体の取り付け部に設けた巻締め規制軸を当接させて揺動体の回動を規制し、
前記揺動体に過荷重が逆回転方向において負荷された場合に、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成とした。 The angle adjuster according to the present invention solves the above-mentioned problems.
With the support,
A rotating shaft that is non-rotatably supported by one end of the support,
A winding member that is in pressure contact with the outer peripheral surface of the rotating shaft,
It is composed of a swinging body in which a mounting portion provided on one end side is connected to the rotating shaft via the winding member.
A winding member main body in which the winding member is in pressure contact with the rotating shaft, a substantially J-shaped winding portion extending from the winding member main body and in pressure contact with the outer peripheral surface of the rotating shaft, and A support portion extending from the free end of the winding portion and connected to the mounting portion of the rocking body.
Due to the rotation of the rocking body in the forward rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft is reduced, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. While the force is reduced, the rocking body is allowed to rotate in the forward rotation direction, while it is allowed to rotate.
Due to the rotation of the rocking body in the reverse rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft increases, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. By increasing the force, the rocking body is prevented from rotating in the reverse rotation direction, and at the same time, it is prevented from rotating in the reverse rotation direction.
The winding restricting shaft provided on the mounting portion of the rocking body is brought into contact with the position regulating protrusion provided on the winding member main body to regulate the rotation of the rocking body.
When an overload is applied to the rocking body in the reverse rotation direction, the outer peripheral surface of the rotating shaft is tightened by the overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft. Is configured to slide and rotate.

本発明によれば、過荷重によって構成部品に塑性変形が生じる前に回転軸の外周面を巻締め部材が滑って回動する。このため、構成部品の破壊や破損を回避できるので、過荷重の除去後に再使用できる角度調整器が得られる。 According to the present invention, the winding member slides and rotates on the outer peripheral surface of the rotating shaft before plastic deformation occurs in the component due to the overload. Therefore, it is possible to avoid destruction or damage of the components, the angle regulator can be re-used after removal of the overload is obtained.

本発明に係る他の角度調整器は、前記課題を解決すべく、The other angle adjuster according to the present invention is used to solve the above-mentioned problems.
支持体と、With the support,
前記支持体の一端部に回動不能に支持された回転軸と、A rotating shaft that is non-rotatably supported by one end of the support,
前記回転軸の外周面に圧接する巻締め部材と、A winding member that is in pressure contact with the outer peripheral surface of the rotating shaft,
一端側に設けた取り付け部を前記巻締め部材を介して前記回転軸に連結した揺動体と、からなり、It is composed of a swinging body in which a mounting portion provided on one end side is connected to the rotating shaft via the winding member.
前記巻締め部材が、前記回転軸に圧接する巻締め部材本体と、前記巻締め部材本体から延在し、かつ、前記回転軸の外周面に圧接する略Ｊ字形状の巻締め部と、および、前記巻締め部の自由端から延在し、かつ、前記揺動体の取付け部に連結された支持部とを備え、A winding member main body in which the winding member is in pressure contact with the rotating shaft, a substantially J-shaped winding portion extending from the winding member main body and in pressure contact with the outer peripheral surface of the rotating shaft, and A support portion extending from the free end of the winding portion and connected to the mounting portion of the rocking body.
前記揺動体の正回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が減少し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が減少することにより、前記揺動体の正回転方向の回動が許容される一方、Due to the rotation of the rocking body in the forward rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft is reduced, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. While the force is reduced, the rocking body is allowed to rotate in the forward rotation direction, while it is allowed to rotate.
前記揺動体の逆回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が増大し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が増大することにより、前記揺動体の逆回転方向の回動を阻止するとともに、Due to the rotation of the rocking body in the reverse rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft increases, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. By increasing the force, the rocking body is prevented from rotating in the reverse rotation direction, and at the same time, it is prevented from rotating in the reverse rotation direction.
前記巻締め部材本体に設けた位置規制突部に、前記巻締め部を当接させて揺動体の回動を規制し、The winding portion is brought into contact with the position-regulating protrusion provided on the winding member main body to regulate the rotation of the rocking body.
前記揺動体に過荷重が逆回転方向において負荷された場合に、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成としてもよい。When an overload is applied to the rocking body in the reverse rotation direction, the outer peripheral surface of the rotating shaft is wound by the overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft. May be configured to slide and rotate.

本発明によれば、前述の効果に加え、巻締め部材本体に設けた位置規制突部に、前記巻締め部を当接させて揺動体の回動を規制する。このため、部品点数,組立工数が少ない角度調整器が得られる。According to the present invention, in addition to the above-mentioned effects, the winding portion is brought into contact with the position-regulating protrusion provided on the winding member main body to regulate the rotation of the rocking body. Therefore, an angle adjuster with a small number of parts and assembling man-hours can be obtained.

本発明に係る別の角度調整器は、前記課題を解決すべく、Another angle adjuster according to the present invention is to solve the above-mentioned problems.
支持体と、With the support,
前記支持体の一端部に回動不能に支持された回転軸と、A rotating shaft that is non-rotatably supported by one end of the support,
前記回転軸の外周面に圧接する巻締め部材と、A winding member that is in pressure contact with the outer peripheral surface of the rotating shaft,
一端側に設けた取り付け部を前記巻締め部材を介して前記回転軸に連結した揺動体と、からなり、It is composed of a swinging body in which a mounting portion provided on one end side is connected to the rotating shaft via the winding member.
前記巻締め部材が、前記回転軸に圧接する巻締め部材本体と、前記巻締め部材本体から延在し、かつ、前記回転軸の外周面に圧接する略Ｊ字形状の巻締め部と、および、前記巻締め部の自由端から延在し、かつ、前記揺動体の取付け部に連結された支持部とを備え、A winding member main body in which the winding member is in pressure contact with the rotating shaft, a substantially J-shaped winding portion extending from the winding member main body and in pressure contact with the outer peripheral surface of the rotating shaft, and A support portion extending from the free end of the winding portion and connected to the mounting portion of the rocking body.
前記揺動体の正回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が減少し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が減少することにより、前記揺動体の正回転方向の回動が許容される一方、Due to the rotation of the rocking body in the forward rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft is reduced, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. While the force is reduced, the rocking body is allowed to rotate in the forward rotation direction, while it is allowed to rotate.
前記揺動体の逆回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が増大し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が増大することにより、前記揺動体の逆回転方向の回動を阻止するとともに、Due to the rotation of the rocking body in the reverse rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft increases, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. By increasing the force, the rocking body is prevented from rotating in the reverse rotation direction, and at the same time, it is prevented from rotating in the reverse rotation direction.
前記巻締め部材の支持部に設けた巻締め規制長孔の一端部に、前記揺動体の取り付け部に設けた巻締め規制軸を圧接させて揺動体の回動を規制し、The winding restricting shaft provided in the mounting portion of the rocking body is pressed against one end of the winding restricting elongated hole provided in the support portion of the winding member to regulate the rotation of the rocking body.
前記揺動体に過荷重が逆回転方向において負荷された場合に、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動する構成としてもよい。When an overload is applied to the rocking body in the reverse rotation direction, the outer peripheral surface of the rotating shaft is wound by the overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft. May be configured to slide and rotate.
本発明によれば、前述の効果に加え、過荷重に対する摩擦力を巻締め規制長孔の位置、形状、大きさ、個数を適宜、選択して調整できるので、設計,製造が容易な角度調整器が得られる。According to the present invention, in addition to the above-mentioned effects, the frictional force against overload can be adjusted by appropriately selecting and adjusting the position, shape, size, and number of winding regulation elongated holes, so that the angle adjustment is easy to design and manufacture. A vessel is obtained.

本発明の実施形態としては、一対の前記巻締め部材で、前記揺動体の取り付け部を挟持
してもよい。
本実施形態によれば、一対の巻締め部材で揺動体を挟持するので、保持強度が増大する
。 In the embodiment of the present invention, the attachment portion of the rocking body may be sandwiched between the pair of the winding members.
According to the present embodiment, since the rocking body is sandwiched between the pair of winding members, the holding strength is increased.

本発明の他の実施形態としては、前記回転軸の外周面に突設した環状鍔部を、一対の前
記巻締め部材で挟持してもよい。
本実施形態によれば、一対の巻締め部材で回転軸の環状鍔部を挟持するので、保持強度
が増大する。 In another embodiment of the present invention, the annular flange portion protruding from the outer peripheral surface of the rotating shaft may be sandwiched between the pair of winding members.
According to the present embodiment, since the annular flange portion of the rotating shaft is sandwiched between the pair of winding members, the holding strength is increased.

本発明に係る家具としては、前述に記載の角度調整器を備えた構成としてある。 The furniture according to the present invention has a configuration provided with the angle adjuster described above.

本発明によれば、角度調整器の構成部品に破壊や破損が生じることを回避でき、過荷重
の除去後に再使用できる家具が得られる。このため、過荷重による構成部品の破壊や破損
を原因とする修理が不要になり、家具全体を廃棄することがないという効果がある。 According to the present invention, it is possible to prevent the components of the angle adjuster from being broken or damaged, and it is possible to obtain furniture that can be reused after removing the overload. Therefore, there is no need for repairs caused by destruction or breakage of components due to overload, and there is an effect that the entire furniture is not discarded.

本発明に係る角度調整器を、例えば、ソファに適用した場合の一例を説明するための斜視図である。It is a perspective view for demonstrating an example of the case where the angle adjuster which concerns on this invention is applied to a sofa, for example. 図１に示したソファの要部の拡大斜視図である。It is an enlarged perspective view of the main part of the sofa shown in FIG. 本発明に係る角度調整器の第１実施形態に係る初期位置を示す全体斜視図である。It is an overall perspective view which shows the initial position which concerns on 1st Embodiment of the angle adjuster which concerns on this invention. 図３に示した角度調整器の分解斜視図である。It is an exploded perspective view of the angle adjuster shown in FIG. 図４に示した分解斜視図を異なる角度から見た分解斜視図である。It is an exploded perspective view which looked at the exploded perspective view shown in FIG. 4 from a different angle. 図３に示した角度調整器からカバーおよび補強板を取り外した状態を示す部分正面図である。It is a partial front view which shows the state which the cover and the reinforcing plate were removed from the angle adjuster shown in FIG. 図６に示したVII-VII線断面図である。FIG. 6 is a sectional view taken along line VII-VII shown in FIG. 図６に示した角度調整器の要部拡大分解斜視図である。FIG. 6 is an enlarged exploded perspective view of a main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the angle adjuster which concerns on this invention. 図９に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図９の初期状態（第１状態）から変位した第２状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 2nd state displaced from the initial state (1st state) of FIG. 図１１に示した角度調整器の要部拡大図である。FIG. 11 is an enlarged view of a main part of the angle adjuster shown in FIG. 図１１の状態から過荷重の負荷で変位した第３状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 3rd state which was displaced by the load of an overload from the state of FIG. 図１３に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１１の状態から変位した第４状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 4th state displaced from the state of FIG. 図１５に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１５の状態から変位した第５状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 5th state displaced from the state of FIG. 図１７に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図１７の状態から変位した第６状態の位置関係を示す正面図である。It is a front view which shows the positional relationship of the 6th state displaced from the state of FIG. 図１９に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の第２実施形態の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the 2nd Embodiment of the angle adjuster which concerns on this invention. 図２１に示した角度調整器の要部拡大図である。FIG. 21 is an enlarged view of a main part of the angle adjuster shown in FIG. 図２１に示した角度調整器に過荷重を負荷した状態を示す正面図である。It is a front view which shows the state which the overload is applied to the angle adjuster shown in FIG. 図２３に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 本発明に係る角度調整器の第３実施形態の初期状態（第１状態）の位置関係を示す正面図である。It is a front view which shows the positional relationship of the initial state (first state) of the 3rd Embodiment of the angle adjuster which concerns on this invention. 図２５に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 図２５に示した角度調整器に過荷重を負荷した状態を示す正面図である。FIG. 5 is a front view showing a state in which an overload is applied to the angle adjuster shown in FIG. 25. 図２７に示した角度調整器の要部拡大図である。It is an enlarged view of the main part of the angle adjuster shown in FIG. 27.

本発明に係る角度調整器の実施形態を図１ないし図２８の添付図面に従って説明する。
図１および図２に示すように、第１実施形態に係る角度調整器１０は、ソファ１のアー
ムレスト２およびヘッドレスト３に適用した場合である。例えば、ヘッドレスト３は、並
設した一対の角度調整器１０，１０の間に架け渡した芯材４に、クッション材(図示せず)
を取り付け、皮革，布地等の張地５で被覆することにより、形成されている。 An embodiment of the angle adjuster according to the present invention will be described with reference to the accompanying drawings of FIGS. 1 to 28.
As shown in FIGS. 1 and 2, the angle adjuster 10 according to the first embodiment is applied to the armrest 2 and the headrest 3 of the sofa 1. For example, the headrest 3 has a cushioning material (not shown) on a core material 4 spanning between a pair of angle adjusters 10 and 10 arranged side by side.
Is attached and covered with upholstery 5 such as leather and cloth.

角度調整器１０は、図３ないし図５に示すように、大略、支持体２０と揺動体３０とで
構成されている。
支持体２０は、図４に示すように、丸棒材を略Ｌ字形状に屈曲した形状を有する。そし
て、支持体２０は、その下端部に設けた雌ネジ部２１に、抜け止め座金２２と座金２３と
を挿通し、両者の間に配置した基材(図示せず)を六角ナット２４で固定できる。
また、支持体２０は、その水平端部に設けた六角孔２５に挿通した鍔付き六角ナット２
８に、座金２６を介し、ボルト２７を螺合することにより、揺動体３０を連結できる（図
７）。 As shown in FIGS. 3 to 5, the angle adjuster 10 is roughly composed of a support 20 and a rocking body 30.
As shown in FIG. 4, the support 20 has a shape in which a round bar member is bent into a substantially L shape. Then, in the support 20, the retaining washer 22 and the washer 23 are inserted into the female screw portion 21 provided at the lower end thereof, and the base material (not shown) arranged between the two is fixed with the hexagon nut 24. can.
Further, the support 20 is a hexagon nut 2 with a flange inserted into a hexagonal hole 25 provided at its horizontal end.
The rocking body 30 can be connected to 8 by screwing the bolt 27 via the washer 26 (FIG. 7).

揺動体３０は、その一端側に芯材４をネジ固定するためのリブ３１を曲げ起こしてある
一方、その他端部に取り付け部３２を設けてある。取り付け部３２は、図８に示すように
、その先端の中央に軸受け凹部３３を設けてある。また、取り付け部３２は、その先端の
下方縁部に下方受け部３４を設けてあるとともに、その先端の上方縁部に上方突部３５を
設けてある。さらに、取り付け部３２は、カシメ孔３６を設けてあるとともに、軸孔３７
を設けてある。 The rocking body 30 is provided with a rib 31 for fixing the core material 4 with screws on one end side thereof, while a mounting portion 32 is provided on the other end portion. As shown in FIG. 8, the mounting portion 32 is provided with a bearing recess 33 in the center of the tip thereof. Further, the mounting portion 32 is provided with a lower receiving portion 34 at the lower edge portion of the tip thereof, and an upper protrusion 35 is provided at the upper edge portion of the tip thereof. Further, the mounting portion 32 is provided with a caulking hole 36, and the shaft hole 37 is provided.
Is provided.

そして、揺動体３０の取り付け部３２には、図４に示すように、回転軸４０の環状鍔部
４２を挟持するように配置した巻締め部材５０，５０を、一対の補強板６２,６２を介し
て取り付けてある。このため、回転軸４０は、揺動体３０の延長線上に位置している。 Then, as shown in FIG. 4, the mounting portion 32 of the rocking body 30 is provided with winding members 50, 50 arranged so as to sandwich the annular flange portion 42 of the rotating shaft 40, and a pair of reinforcing plates 62, 62. It is attached via. Therefore, the rotating shaft 40 is located on the extension line of the rocking body 30.

回転軸４０は、図８に示すように、六角孔４１を有し、その外周面４６に突設した環状
鍔部４２に第１、第２、第３爪部４３、４４、４５を所定のピッチで突設してある。 As shown in FIG. 8, the rotary shaft 40 has a hexagonal hole 41, and the first, second, and third claw portions 43, 44, and 45 are predetermined to the annular flange portion 42 projecting from the outer peripheral surface 46 thereof. It is projected on the pitch.

巻締め部材５０は、巻締め部材本体５１と、巻締め部材本体５１から延在し、かつ、前
記回転軸４０の外周面４６に係合可能な形状を有する略Ｊ字形状の巻締め部５２と、巻締
め部５２の自由端から延在する支持部５３と、で構成されている。このため、回転軸４０
の外周面４６と巻締め部５２の内側面５４とが面接触可能となる（図７）。また、巻締め
部材本体５１には、カシメ孔５５と、長孔５６とが設けられているとともに、位置規制突
部５７が突設されている。また、支持部５３にはカシメ孔５８が設けられている。 The winding member 50 extends from the winding member main body 51 and the winding member main body 51, and has a substantially J-shaped winding portion 52 having a shape that can be engaged with the outer peripheral surface 46 of the rotary shaft 40. And a support portion 53 extending from the free end of the winding portion 52. Therefore, the rotating shaft 40
The outer peripheral surface 46 and the inner surface 54 of the winding portion 52 can be in surface contact with each other (FIG. 7). Further, the winding member main body 51 is provided with a caulking hole 55 and an elongated hole 56, and a position restricting protrusion 57 is provided so as to project. Further, the support portion 53 is provided with a caulking hole 58.

次に、第１実施形態に係る角度調整器１０の組立方法について説明する。
回転軸４０の両側から巻締め部材５０，５０を組み付けた後、巻締め部材５０，５０の
支持部５３，５３の間に、揺動体３０の取り付け部３２を挿入して位置決めする。
そして、取り付け部３２の軸孔３７に巻締め規制軸６０を嵌合するとともに、巻締め部
材５０の長孔５６に解除軸６１を嵌合する。
さらに、巻締め部材５０，５０の外向面に補強板６２，６２をそれぞれ組み付け、補強
板６２の嵌合孔６２ａを巻締め規制軸６０に嵌合する。ついで、第１リベット６３を、補
強板６２のカシメ孔６２ｂ、巻締め部材５０のカシメ孔５８および揺動体３０のカシメ孔
３６に挿通し、カシメ固定する。
同様に、第２リベット６４を、補強板６２のカシメ孔６２ｃ、巻締め部材５０のカシメ
孔５５に挿通するとともに、揺動体３０の軸受け凹部３３に嵌合し、カシメ固定すること
により、揺動体３０の組立が完了する。
したがって、第１，第２リベット６３，６４および巻締め規制軸６０のそれぞれの支点
間距離は、一定である。また、解除軸６１は脱落することなく保持される。 Next, the method of assembling the angle adjuster 10 according to the first embodiment will be described.
After assembling the winding members 50 and 50 from both sides of the rotating shaft 40, the mounting portion 32 of the rocking body 30 is inserted between the support portions 53 and 53 of the winding members 50 and 50 for positioning.
Then, the winding restricting shaft 60 is fitted into the shaft hole 37 of the mounting portion 32, and the release shaft 61 is fitted into the elongated hole 56 of the winding member 50.
Further, the reinforcing plates 62 and 62 are assembled on the outward surfaces of the winding members 50 and 50, respectively, and the fitting hole 62a of the reinforcing plate 62 is fitted to the winding regulation shaft 60. Then, the first rivet 63 is inserted into the caulking hole 62b of the reinforcing plate 62, the caulking hole 58 of the winding member 50, and the caulking hole 36 of the rocking body 30, and is caulked and fixed.
Similarly, the second rivet 64 is inserted into the caulking hole 62c of the reinforcing plate 62 and the caulking hole 55 of the winding member 50, and is fitted into the bearing recess 33 of the rocking body 30 and crimped to fix the rocking body. The assembly of 30 is completed.
Therefore, the distances between the fulcrums of the first and second rivets 63 and 64 and the winding restricting shaft 60 are constant. Further, the release shaft 61 is held without falling off.

そして、巻締め部材５０全体を被覆可能な正面形状を有するカバー７０，７２を前後か
ら組み合わせ、相互に着脱可能に係合一体化する。ついで、カバー７０の嵌合孔７１から
鍔付き六角ナット２８を挿通し、回転軸４０の六角孔４１に挿通した後、カバー７２の嵌
合孔７３から突出させる。さらに、嵌合孔７３から突出する鍔付き六角ナット２８の先端
を支持体２０の六角孔２５に挿通し、座金２６を介してボルト２７を螺合する。この結果
、支持体２０と揺動体３０とが連結一体化され、支持体２０に対して回転軸４０が回動不
能に支持される。 Then, the covers 70 and 72 having a front shape capable of covering the entire winding member 50 are combined from the front and back, and are detachably engaged and integrated with each other. Then, the hexagon nut 28 with a flange is inserted through the fitting hole 71 of the cover 70, inserted into the hexagonal hole 41 of the rotating shaft 40, and then projected from the fitting hole 73 of the cover 72. Further, the tip of the flanged hexagon nut 28 protruding from the fitting hole 73 is inserted into the hexagonal hole 25 of the support 20, and the bolt 27 is screwed through the washer 26. As a result, the support 20 and the rocking body 30 are connected and integrated, and the rotating shaft 40 is non-rotatably supported with respect to the support 20.

次に、第１実施形態に係る角度調整器の操作工程を、図９ないし図２０に基づいて説明
する。
初期位置である第１状態おいて、図９および図１０に示すように、回転軸４０の外周面
４６にバネ弾性を有する巻締め部材５０が嵌合している。このため、回転軸４０の外周面
４６に巻締め部材本体５１と略Ｊ字形状の巻締め部５２とが所定の圧力で面接触し、摩擦
力が生じているので、揺動体３０にガタツキはない。このとき、巻締め部材本体５１と巻
締め部５２との距離はｌ0である。 Next, the operation step of the angle adjuster according to the first embodiment will be described with reference to FIGS. 9 to 20.
In the first state, which is the initial position, as shown in FIGS. 9 and 10, a winding member 50 having spring elasticity is fitted to the outer peripheral surface 46 of the rotating shaft 40. For this reason, the winding member main body 51 and the substantially J-shaped winding portion 52 are in surface contact with the outer peripheral surface 46 of the rotating shaft 40 at a predetermined pressure, and a frictional force is generated, so that the rocking body 30 is not rattled. No. At this time, the distance between the winding member main body 51 and the winding portion 52 is l0.

第２状態は、図１１および図１２に示すように、第１状態における揺動体３０を矢印Ｐ
方向（正回転方向）に引き起こして回動させると、第２リベット６４を支点として揺動体
３０が回動する。このとき、第２リベット６４を介して巻締め部材本体５１は回転軸４０
の外周面４６に押圧されて変位しないが、巻締め部５２が第１リベット６３を介して引き
上げられる。このため、巻締め部材本体５１と巻締め部５２との間が距離ｌ１（＞ｌ0）
に拡大し、回転軸４０に対する巻締め部材５０の巻締め力が減少する。よって、回転軸４
０の外周面４６と巻締め部５２の内側面５４との間の摩擦力が減少し、揺動体３０を使用
者好みの傾斜角度まで引き起こすことができる。 In the second state, as shown in FIGS. 11 and 12, the rocking body 30 in the first state is indicated by the arrow P.
When it is triggered and rotated in the direction (forward rotation direction), the rocking body 30 rotates with the second rivet 64 as a fulcrum. At this time, the winding member main body 51 is connected to the rotating shaft 40 via the second rivet 64.
Although it is pressed against the outer peripheral surface 46 and does not displace, the winding portion 52 is pulled up via the first rivet 63. Therefore, the distance between the winding member main body 51 and the winding portion 52 is l1 (> l0).
The winding force of the winding member 50 with respect to the rotating shaft 40 is reduced. Therefore, the rotation axis 4
The frictional force between the outer peripheral surface 46 of 0 and the inner surface 54 of the winding portion 52 is reduced, and the rocking body 30 can be caused to an inclination angle preferred by the user.

そして、例えば、第２状態で使用者がヘッドレスト３に頭を乗せ、揺動体３０に所定の
荷重を矢印Ｑ方向（逆回転方向）に負荷すると、揺動体３０は第２リベット６４を支点と
して回動する。このとき、第２リベット６４を介して巻締め部材本体５１は回転軸４０の
外周面４６に押圧されて変位しないが、第１リベット６３を介して巻締め部５２が引き下
げられる。このため、巻締め部材本体５１に巻締め部５２が接近し、両者の間が距離ｌ２
（＜ｌ0）に縮まり、回転軸４０に対する巻締め部材５０の締め付け力が増大する。よっ
て、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力が増大し、揺動体３
０は回動できず、ヘッドレスト３は使用者の好みの傾斜角度を保持する。アームレスト２
に適用した場合も同様である。 Then, for example, when the user puts his head on the headrest 3 in the second state and applies a predetermined load to the rocking body 30 in the arrow Q direction (reverse rotation direction), the rocking body 30 rotates with the second rivet 64 as a fulcrum. Move. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the winding portion 52 is pulled down via the first rivet 63. Therefore, the winding portion 52 approaches the winding member main body 51, and the distance between the two is l2.
It shrinks to (<l0), and the tightening force of the winding member 50 with respect to the rotating shaft 40 increases. Therefore, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 3
0 cannot rotate, and the headrest 3 holds the user's favorite tilt angle. Armrest 2
The same applies when applied to.

なお、第２状態において、極めて大きい過荷重がＱ方向（逆回転方向）に負荷された場
合、図１３および図１４に示す第３状態となる。
すなわち、揺動体３０が第２リベット６４を支点として回動し、第２状態よりも巻締め
部５２が更に引き下げられる。このため、巻締め部材本体５１と巻締め部５２との距離が
距離ｌ３（＜ｌ２）に縮まるが、巻締め規制軸６０が巻締め部材本体５１の位置規制突部
５７に当接し、揺動体３０の回動が阻止される。この結果、回転軸４０の外周面４６と巻
締め部５２の内側面５４との摩擦力が最大摩擦力となり、摩擦力はそれ以上増大しない。
したがって、揺動体３０に負荷される矢印Ｑ方向（逆回転方向）の過荷重が前述の最大
摩擦力を超える場合には、巻締め部材５０は回転軸４０の外周面４６上を滑って回動する
。このため、巻締め部材５０だけでなく、回転軸４０、揺動体３０などの構成部品に破壊
や破損が生ぜず、角度調整器１０は破壊されず、破損しない。
要するに、本発明に係る角度調整器によれば、過荷重が負荷された場合には、巻締め部
材５０等の構成部品に破壊や破損が生ぜず、角度調整器１０の破壊や破損を回避できると
いう利点がある。 In the second state, when an extremely large overload is applied in the Q direction (reverse rotation direction), the third state shown in FIGS. 13 and 14 is obtained.
That is, the rocking body 30 rotates around the second rivet 64 as a fulcrum, and the winding portion 52 is further pulled down from the second state. Therefore, the distance between the winding member main body 51 and the winding portion 52 is reduced to the distance l3 (<l2), but the winding restricting shaft 60 comes into contact with the position restricting protrusion 57 of the winding member main body 51, and the rocking body The rotation of 30 is blocked. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 becomes the maximum frictional force, and the frictional force does not increase any more.
Therefore, when the overload in the arrow Q direction (reverse rotation direction) applied to the rocking body 30 exceeds the above-mentioned maximum frictional force, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40 and rotates. do. Therefore, not only the winding member 50 but also the components such as the rotating shaft 40 and the rocking body 30 are not destroyed or damaged, and the angle adjuster 10 is not destroyed or damaged.
In short, according to the angle adjuster according to the present invention, when an overload is applied, the components such as the winding member 50 are not destroyed or damaged, and the angle adjuster 10 can be avoided from being destroyed or damaged. There is an advantage.

次に、図１５および図１６に示す第４状態は、第２状態から揺動体３０を矢印Ｐ方向（
正回転方向）に更に回動し、傾斜角度を調整できる最大範囲まで変位させた状態を示す。
このとき、解除軸６１が回転軸４０の第２爪部４４に係止しているとともに、下方受け部
３４に圧接している。また、巻締め部材本体５１と巻締め部５２との間は距離ｌ１である
。
そして、揺動体３０に荷重を矢印Ｑ方向（逆回転方向）に負荷した場合には、揺動体３
０は第２リベット６４を支点として回動する。このとき、第２リベット６４を介して巻締
め部材本体５１が回転軸４０の外周面４６に押圧されて変位しないが、第１リベット６３
を介して巻締め部５２が引っ張られる。このため、巻締め部材本体５１に巻締め部５２が
接近して距離ｌ２（＜ｌ0）に縮まり、回転軸４０に対する巻締め部材５０の締め付け力
が増大する。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩擦力
が増大し、揺動体３０は回動できない。よって、ヘッドレスト３は使用者の好みの傾斜角
度を保持する。 Next, in the fourth state shown in FIGS. 15 and 16, the rocking body 30 is moved in the arrow P direction (from the second state).
It shows a state in which the tilt angle is further rotated in the forward rotation direction) and displaced to the maximum range in which the tilt angle can be adjusted.
At this time, the release shaft 61 is locked to the second claw portion 44 of the rotary shaft 40 and is in pressure contact with the lower receiving portion 34. Further, there is a distance l1 between the winding member main body 51 and the winding portion 52.
Then, when a load is applied to the rocking body 30 in the arrow Q direction (reverse rotation direction), the rocking body 3 is used.
0 rotates around the second rivet 64 as a fulcrum. At this time, the winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 via the second rivet 64 and is not displaced, but the first rivet 63.
The winding tightening portion 52 is pulled through. Therefore, the winding portion 52 approaches the winding member main body 51 and shrinks to a distance l2 (<l0), and the tightening force of the winding member 50 with respect to the rotating shaft 40 increases. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 cannot rotate. Therefore, the headrest 3 holds the user's favorite tilt angle.

第５状態は、図１７および図１８に示すように、第４状態から更にＰ方向（正回転方向
）に揺動体３０を回動した場合である。
すなわち、揺動体３０を回動すると、第２爪部４４に係止する解除軸６１に下方受け部
３４が乗り上げ、ロック状態となる。このため、解除軸６１が巻締め部材本体５１を介し
て回転軸４０に圧接し、巻締め部材本体５１の変位を規制する。同時に、上方突部３５が
第３爪部４５に当接して位置規制される。この結果、巻締め部材本体５１と巻締め部５２
との間は距離ｌ４（＞ｌ0）となり、回転軸４０に対する巻締め部材５０の巻締め力が減
少する。よって、回転軸４０の外周面４６と巻締め部５２の内側面５４との間の摩擦力が
減少した状態が保持され、揺動体３０を矢印Ｑ方向（逆回転方向）に回動できる。 The fifth state is a case where the rocking body 30 is further rotated in the P direction (forward rotation direction) from the fourth state, as shown in FIGS. 17 and 18.
That is, when the rocking body 30 is rotated, the lower receiving portion 34 rides on the release shaft 61 that is locked to the second claw portion 44, and is in a locked state. Therefore, the release shaft 61 is pressed against the rotating shaft 40 via the winding member main body 51 to regulate the displacement of the winding member main body 51. At the same time, the upper protrusion 35 abuts on the third claw portion 45 and the position is restricted. As a result, the winding member main body 51 and the winding portion 52
The distance between them is l4 (> l0), and the tightening force of the winding member 50 with respect to the rotating shaft 40 is reduced. Therefore, the state in which the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 is reduced is maintained, and the rocking body 30 can be rotated in the arrow Q direction (reverse rotation direction).

第６状態は、図１９および図２０に示すように、第５状態から揺動体３０を矢印Ｑ方向
（逆回転方向）に回動させると、第２リベット６４を支点として巻締め部材本体５１が逆
方向に回動する。そして、解除軸６１が第１爪部４３に係止して位置規制されるので、解
除軸６１に乗り上げていた下方受け部３４が解除軸６１から外れる。さらに、揺動体３０
を矢印Ｑ方向（逆回転方向）に回動することにより、初期状態である第１状態に復帰する
。
以後、同様な操作を行うことにより、揺動体３０を操作できる。 In the sixth state, as shown in FIGS. 19 and 20, when the rocking body 30 is rotated in the arrow Q direction (reverse rotation direction) from the fifth state, the winding member main body 51 uses the second rivet 64 as a fulcrum. Rotate in the opposite direction. Then, since the release shaft 61 is locked to the first claw portion 43 and the position is restricted, the lower receiving portion 34 riding on the release shaft 61 is disengaged from the release shaft 61. Further, the rocking body 30
Is rotated in the direction of arrow Q (reverse rotation direction) to return to the first state, which is the initial state.
After that, the rocking body 30 can be operated by performing the same operation.

本発明に係る角度調整器の第２実施形態は、図２１ないし図２４に示すように、前述の
第１実施形態とほぼ同様である。
すなわち、図２１および図２２に示す第１状態（初期状態）で、揺動体３０を矢印Ｐ方
向（正回転方向）に回動させると、巻締め部材本体５１と巻締め部５２との間の距離ｌ０
が距離ｌ１（図示せず）に広がる。このため、回転軸４０に対する巻締め部材本体５１と
巻締め部５２とによる締め付け力が減少し、回転軸４０の外周面４６と巻締め部５２の内
側面５４との摩擦力が減少する。この結果、揺動体３０を所望の傾斜角度まで調整するこ
とができる。 As shown in FIGS. 21 to 24, the second embodiment of the angle adjuster according to the present invention is substantially the same as the first embodiment described above.
That is, when the rocking body 30 is rotated in the arrow P direction (forward rotation direction) in the first state (initial state) shown in FIGS. 21 and 22, between the winding member main body 51 and the winding portion 52. Distance l0
Spreads over a distance l1 (not shown). Therefore, the tightening force between the winding member main body 51 and the winding portion 52 with respect to the rotating shaft 40 is reduced, and the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner side surface 54 of the winding portion 52 is reduced. As a result, the rocking body 30 can be adjusted to a desired tilt angle.

そして、揺動体３０に通常の荷重が矢印Ｑ方向（逆回転方向）に負荷された場合には、
第２リベット６４を回動支点として揺動体３０が回動する。このとき、第２リベット６４
を介して巻締め部材本体５１が回転軸４０の外周面４６に押圧されて変位しないが、第１
リベット６３を介して巻締め部５２が引き下げられる。このため、巻締め部５２と巻締め
部材本体５１との間の距離が縮まり、巻締め部材本体５１と巻締め部５２とによる締め付
け力が増大する。この結果、回転軸４０の外周面４６と巻締め部５２の内側面５４との摩
擦力が増大し、揺動体３０は使用者好みの傾斜角度で保持される。 Then, when a normal load is applied to the rocking body 30 in the direction of arrow Q (reverse rotation direction),
The rocking body 30 rotates with the second rivet 64 as a rotation fulcrum. At this time, the second rivet 64
The winding member main body 51 is pressed against the outer peripheral surface 46 of the rotating shaft 40 and is not displaced, but the first
The winding portion 52 is pulled down via the rivet 63. Therefore, the distance between the winding member main body 52 and the winding member main body 51 is shortened, and the tightening force between the winding member main body 51 and the winding member main body 52 is increased. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 is held at an inclination angle preferred by the user.

しかし、図２３および図２４に示すように、揺動体３０に極めて大きな過荷重が負荷さ
れた場合には、巻締め部５２が位置規制突部５７に直接、当接して位置規制され、揺動体
３０の回動が阻止される。このため、回転軸４０の外周面４６と巻締め部５２の内側面５
４との摩擦力が最大摩擦力となり、それ以上に摩擦力は増大しない。この結果、最大摩擦
力を超える過荷重が揺動体３０に負荷された場合には、巻締め部材５０が回転軸４０の外
周面４６上を滑り、揺動体３０が回動する。よって、巻締め部材５０だけでなく、回転軸
４０、揺動体３０などの構成部品が破壊されず、破損しないので、角度調整器１０の破壊
や破損を防止できる。
他は前述の第１実施形態とほぼ同様であるので、同一部分には同一番号を附して説明を
省略する。 However, as shown in FIGS. 23 and 24, when an extremely large overload is applied to the rocking body 30, the winding portion 52 directly abuts on the position restricting protrusion 57 to regulate the position, and the rocking body is regulated. The rotation of 30 is blocked. Therefore, the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 5 of the winding portion 52
The frictional force with 4 becomes the maximum frictional force, and the frictional force does not increase any more. As a result, when an overload exceeding the maximum frictional force is applied to the rocking body 30, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40, and the rocking body 30 rotates. Therefore, not only the winding member 50 but also the components such as the rotating shaft 40 and the rocking body 30 are not destroyed and are not damaged, so that the angle adjuster 10 can be prevented from being destroyed or damaged.
Since the other parts are almost the same as those of the above-described first embodiment, the same parts are designated by the same numbers and the description thereof will be omitted.

本実施形態によれば、巻締め規制軸６０が不要になり、第１実施形態よりも部品点数、
組立工数の少ない角度調整器が得られるという利点がある。 According to this embodiment, the winding regulation shaft 60 is not required, and the number of parts is larger than that of the first embodiment.
There is an advantage that an angle adjuster with a small number of assembly steps can be obtained.

本発明に係る角度調整器の第３実施形態は、図２５ないし図２８に示すように、前述の
第１実施形態とほぼ同様である。
異なる点は、巻締め部材５０の支持部５３に設けた巻締め規制長孔５９に、揺動体３０
の取り付け部３２に設けた巻締め規制軸６５を、嵌合した点である。 As shown in FIGS. 25 to 28, the third embodiment of the angle adjuster according to the present invention is substantially the same as the first embodiment described above.
The difference is that the rocking body 30 is provided in the winding regulation elongated hole 59 provided in the support portion 53 of the winding member 50.
It is a point where the winding restricting shaft 65 provided in the mounting portion 32 of the above is fitted.

そして、図２５および図２６に示す第１状態（初期状態）で、揺動体３０を矢印Ｐ方向
（正回転方向）に回動させると、巻締め部材本体５１と巻締め部５２との間は距離ｌ０か
ら距離ｌ１（図示せず）に広がる。このため、回転軸４０に対する巻締め部材本体５１と
巻締め部５２との締め付け力が減少し、回転軸４０の外周面４６と巻締め部５２の内側面
５４との摩擦力が減少する。この結果、揺動体３０を使用者好みの傾斜角度に調整できる
。 Then, in the first state (initial state) shown in FIGS. 25 and 26, when the rocking body 30 is rotated in the arrow P direction (forward rotation direction), the space between the winding member main body 51 and the winding portion 52 is It extends from distance l0 to distance l1 (not shown). Therefore, the tightening force between the winding member main body 51 and the winding portion 52 with respect to the rotating shaft 40 is reduced, and the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner side surface 54 of the winding portion 52 is reduced. As a result, the rocking body 30 can be adjusted to the inclination angle preferred by the user.

一方、揺動体３０に通常の荷重が矢印Ｑ方向に負荷された場合には、第２リベット６４
を回動支点として揺動体３０が回動する。このとき、巻締め部材本体５１は回転軸４０に
圧接して変位しないが、第１リベット６３を介して巻締め部５２が引き下げられる。この
ため、巻締め部５２と巻締め部材本体５１との間の距離が縮まり、巻締め部材本体５１と
巻締め部５２とによる締め付け力が増大する。この結果、回転軸４０の外周面４６と巻締
め部５２の内側面５４との摩擦力が増大し、揺動体３０は使用者好みの傾斜角度で保持さ
れる。 On the other hand, when a normal load is applied to the rocking body 30 in the direction of arrow Q, the second rivet 64
The rocking body 30 rotates around the rotation fulcrum. At this time, the winding member main body 51 is pressed against the rotating shaft 40 and is not displaced, but the winding portion 52 is pulled down via the first rivet 63. Therefore, the distance between the winding member main body 52 and the winding member main body 51 is shortened, and the tightening force between the winding member main body 51 and the winding member main body 52 is increased. As a result, the frictional force between the outer peripheral surface 46 of the rotating shaft 40 and the inner surface 54 of the winding portion 52 increases, and the rocking body 30 is held at an inclination angle preferred by the user.

しかし、図２７および図２８に示すように、揺動体３０に過荷重が矢印Ｑ方向（逆回転
方向）に負荷された場合には、巻締め規制長孔５９の一端部に巻締め規制軸６５が圧接し
て位置規制される。このとき、巻締め部５２と巻締め部材本体５１とが接近し、距離ｌ３
（＜ｌ０）となっても、それ以上に縮まることがない。このため、回転軸４０の外周面４
６と巻締め部５２の内側面５４との摩擦力が最大摩擦力となり、それ以上に摩擦力は増大
しない。この結果、最大摩擦力を超える過荷重が揺動体３０に負荷された場合には、巻締
め部材５０が回転軸４０の外周面４６上を滑り、揺動体３０が回動する。よって、巻締め
部材５０だけでなく、回転軸４０、揺動体３０などを含む構成部品が破壊されず、破損し
ないので、角度調整器１０の破壊や破損を防止できる。
他は前述の第１実施形態とほぼ同様であるので、同一部分には同一番号を附して説明を
省略する。 However, as shown in FIGS. 27 and 28, when an overload is applied to the rocking body 30 in the arrow Q direction (reverse rotation direction), the winding regulation shaft 65 is placed on one end of the winding regulation elongated hole 59. Is pressed and the position is regulated. At this time, the winding portion 52 and the winding member main body 51 are close to each other, and the distance is l3.
Even if it becomes (<l0), it does not shrink any more. Therefore, the outer peripheral surface 4 of the rotating shaft 40
The frictional force between 6 and the inner side surface 54 of the winding portion 52 becomes the maximum frictional force, and the frictional force does not increase any more. As a result, when an overload exceeding the maximum frictional force is applied to the rocking body 30, the winding member 50 slides on the outer peripheral surface 46 of the rotating shaft 40, and the rocking body 30 rotates. Therefore, not only the winding member 50 but also the components including the rotating shaft 40, the rocking body 30, and the like are not destroyed and are not damaged, so that the angle adjuster 10 can be prevented from being destroyed or damaged.
Since the other parts are almost the same as those of the above-described first embodiment, the same parts are designated by the same numbers and the description thereof will be omitted.

第３実施形態によれば、最大摩擦力は、巻締め規制長孔５９および巻締め規制軸６５の
形状および位置関係等を調整して設計できる。このため、安定動作する角度調整器の設計
、製造が容易になるという利点がある。 According to the third embodiment, the maximum frictional force can be designed by adjusting the shape and positional relationship of the winding regulation elongated hole 59 and the winding regulation shaft 65. Therefore, there is an advantage that the design and manufacture of the angle adjuster that operates stably becomes easy.

本発明は、前述のソファのヘッドレスト、アームレストに限らず、例えば、折り畳み式の
ベッドなどの家具、車および飛行機などの座席にも適用可能である。 The present invention is not limited to the above-mentioned sofa headrests and armrests, but is also applicable to furniture such as foldable beds and seats such as cars and airplanes.

１ ソファ
２ アームレスト
３ ヘッドレスト
４ 芯材
５ 張地
１０ 角度調整器
２０ 支持体
２１ 雌ネジ部
２２ 抜け止め座金
２３ 座金
２４ 六角ナット
２５ 六角孔
２７ ボルト
２８ 鍔付き六角ナット
３０ 揺動体
３１ リブ
３２ 取り付け部
３３ 軸受け凹部
３４ 下方受け部
３５ 上方突部
３６ カシメ孔
３７ 軸孔
４０ 回転軸
４１ 六角孔
４２ 環状鍔部
４３ 第１爪部
４４ 第２爪部
４５ 第３爪部
４６ 外周面
５０ 巻締め部材
５１ 巻締め部材本体
５２ 巻締め部
５３ 支持部
５４ 内側面
５５ カシメ孔
５６ 長孔
５７ 位置規制突部
５８ カシメ孔
５９ 巻締め規制長孔
６０ 巻締め規制軸
６１ 解除軸
６２ 補強板
６２ａ 嵌合孔
６２ｂ カシメ孔
６２ｃ カシメ孔
６３ 第１リベット
６４ 第２リベット
６５ 巻締め規制軸
７０ カバー
７１ 嵌合孔
７２ カバー
７３ 嵌合孔
Ｐ方向 正回転方向
Ｑ方向 逆回転方向 1 Sofa 2 Armrest 3 Headrest 4 Core material 5 Upholstery 10 Angle adjuster 20 Support 21 Female thread part 22 Retaining seat washer 23 Washer 24 Hexagon nut 25 Hexagonal hole 27 Bolt 28 Hexagon nut with rivet 30 Rocking body 31 Rivet 32 Mounting part 33 Bearing recess 34 Lower receiving part 35 Upper protrusion 36 Caulking hole 37 Shaft hole 40 Rotating shaft 41 Hexagonal hole 42 Circular flange part 43 1st claw part 44 2nd claw part 45 3rd claw part 46 Outer peripheral surface 50 Winding member 51 Winding member Main body 52 Winding part 53 Support part 54 Inner side surface 55 Caulking hole 56 Long hole 57 Position restricting protrusion 58 Caulking hole 59 Winding restricting long hole 60 Winding restricting shaft 61 Release shaft 62 Reinforcing plate 62a Fitting hole 62b Caulking hole 62c Caulking hole 63 1st rivet 64 2nd rivet 65 Tightening control shaft 70 Cover
71 Fitting hole 72 Cover 73 Fitting hole P direction Forward rotation direction Q direction Reverse rotation direction

Claims (7)

支持体と、
前記支持体の一端部に回動不能に支持された回転軸と、
前記回転軸の外周面に圧接する巻締め部材と、
一端側に設けた取り付け部を前記巻締め部材を介して前記回転軸に連結した揺動体と、からなり、
前記巻締め部材が、前記回転軸に圧接する巻締め部材本体と、前記巻締め部材本体から延在し、かつ、前記回転軸の外周面に圧接する略Ｊ字形状の巻締め部と、および、前記巻締め部の自由端から延在し、かつ、前記揺動体の取付け部に連結された支持部とを備え、
前記揺動体の正回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が減少し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が減少することにより、前記揺動体の正回転方向の回動が許容される一方、
前記揺動体の逆回転方向の回動により、前記回転軸の外周面に対する巻締め部材の締め付け力が増大し、回転軸の外周面と巻締め部材の巻締め部の内側面との接触による摩擦力が増大することにより、前記揺動体の逆回転方向の回動を阻止するとともに、
前記揺動体に過荷重が逆回転方向において負荷された場合に、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動することを特徴とする角度調整器。 With the support,
A rotating shaft that is non-rotatably supported by one end of the support,
A winding member that is in pressure contact with the outer peripheral surface of the rotating shaft,
It is composed of a swinging body in which a mounting portion provided on one end side is connected to the rotating shaft via the winding member.
A winding member main body in which the winding member is in pressure contact with the rotating shaft, a substantially J-shaped winding portion extending from the winding member main body and in pressure contact with the outer peripheral surface of the rotating shaft, and A support portion extending from the free end of the winding portion and connected to the mounting portion of the rocking body.
Due to the rotation of the rocking body in the forward rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft is reduced, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. While the force is reduced, the rocking body is allowed to rotate in the forward rotation direction, while it is allowed to rotate.
Due to the rotation of the rocking body in the reverse rotation direction, the tightening force of the winding member with respect to the outer peripheral surface of the rotating shaft increases, and friction due to contact between the outer peripheral surface of the rotating shaft and the inner surface of the winding portion of the winding member. By increasing the force, the rocking body is prevented from rotating in the reverse rotation direction, and at the same time, it is prevented from rotating in the reverse rotation direction.
When an overload is applied to the rocking body in the reverse rotation direction, the outer peripheral surface of the rotating shaft is tightened by the overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft. An angle adjuster characterized by sliding and rotating. 一対の前記巻締め部材で、前記揺動体の取り付け部を挟持したことを特徴とする請求項１に記載の角度調整器。 The angle adjuster according to claim 1, wherein the attachment portion of the rocking body is sandwiched between the pair of the winding members. 前記回転軸の外周面に突設した環状鍔部を、一対の前記巻締め部材で挟持したことを特徴とする請求項１または２に記載の角度調整器。 The angle adjuster according to claim 1 or 2, wherein an annular flange portion projecting from the outer peripheral surface of the rotating shaft is sandwiched between the pair of winding members. 前記巻締め部材本体に設けた位置規制突部に、前記揺動体の取り付け部に設けた巻締め規制軸を当接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増大を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動することを特徴とする請求項１ないし３のいずれか１項に記載の角度調整器。 The winding restricting shaft provided on the mounting portion of the rocking body is brought into contact with the position restricting protrusion provided on the winding member main body to regulate the rotation of the rocking body, and the winding is tightened with respect to the outer peripheral surface of the rotating shaft. The angle adjustment according to any one of claims 1 to 3, wherein the winding member slides and rotates on the outer peripheral surface of the rotating shaft by limiting the increase in the frictional force of the member. vessel. 前記巻締め部材本体に設けた位置規制突部に、前記巻締め部を当接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増加を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動することを特徴とする請求項１ないし３のいずれか１項に記載の角度調整器。 The winding portion is brought into contact with the position-regulating protrusion provided on the winding member main body to restrict the rotation of the rocking body, and the increase in the frictional force of the winding member with respect to the outer peripheral surface of the rotating shaft is limited. The angle adjuster according to any one of claims 1 to 3, wherein the winding member slides and rotates on the outer peripheral surface of the rotating shaft due to an overload. 前記巻締め部材の支持部に設けた巻締め規制長孔の一端部に、前記揺動体の取り付け部に設けた巻締め規制軸を圧接させて揺動体の回動を規制し、前記回転軸の外周面に対する巻締め部材の摩擦力の増加を制限することにより、過荷重によって回転軸の外周面を巻締め部材が滑って回動することを特徴とする請求項１ないし３のいずれか１項に記載の角度調整器。 The winding restricting shaft provided in the mounting portion of the rocking body is pressed against one end of the winding restricting elongated hole provided in the support portion of the winding member to regulate the rotation of the rocking body, and the rotation of the rotating shaft is restricted. One of claims 1 to 3, wherein the winding member slides and rotates on the outer peripheral surface of the rotating shaft due to an overload by limiting the increase in the frictional force of the winding member with respect to the outer peripheral surface. The angle adjuster described in. 請求項１ないし６のいずれか１項に記載の角度調整器を備えたことを特徴とする家具。 A piece of furniture comprising the angle adjuster according to any one of claims 1 to 6.
JP2020105274A 2020-06-18 2020-06-18 Angle adjuster and furniture using it Active JP6830703B1 (en)

Priority Applications (7)

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JP2020105274A JP6830703B1 (en) 2020-06-18 2020-06-18 Angle adjuster and furniture using it
CN202110302381.9A CN113812800A (en) 2020-06-18 2021-03-22 Angle adjuster and furniture using same
CN202120583649.6U CN215959129U (en) 2020-06-18 2021-03-22 Angle adjuster and furniture using same
KR1020210059919A KR102523663B1 (en) 2020-06-18 2021-05-10 Angle adjuster and furniture item using the same
PL21178713.0T PL3925488T3 (en) 2020-06-18 2021-06-10 Angle adjuster and furniture item using the same
EP21178713.0A EP3925488B1 (en) 2020-06-18 2021-06-10 Angle adjuster and furniture item using the same
ES21178713T ES2968611T3 (en) 2020-06-18 2021-06-10 Angle regulator and furniture that uses the same

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JP4519555B2 (en) 2004-07-28 2010-08-04 株式会社ヒカリ Joint device
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PL228113B1 (en) * 2014-07-18 2018-02-28 Stalmot & Wolmet Społka Akcyjna Stepless joint, preferably for the upholstered furniture
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CN215959129U (en) 2022-03-08
PL3925488T3 (en) 2024-05-13
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ES2968611T3 (en) 2024-05-13
KR102523663B1 (en) 2023-04-20

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