JP2016065375A

JP2016065375A - Hinge device with damper

Info

Publication number: JP2016065375A
Application number: JP2014193563A
Authority: JP
Inventors: 新村　健; Takeshi Niimura; 健新村
Original assignee: Sugatsune Kogyo Co Ltd
Current assignee: Sugatsune Kogyo Co Ltd
Priority date: 2014-09-24
Filing date: 2014-09-24
Publication date: 2016-04-28
Anticipated expiration: 2034-09-24
Also published as: JP6170025B2

Abstract

PROBLEM TO BE SOLVED: To provide a hinge device with a damper which can prevent a rotor of the damper from causing a positional deviation even if the engagement of teeth of a link and teeth of the rotor of the damper is released.SOLUTION: The hinge device with a damper comprises: a hinge having a main body side member 4, a door side member 7, and at least one link 5 which is rotatably connected to at least either of the main body side member 4 and the door side member 7; a damper 11 which has a damper main body 9 and a rotor 10 capable of relatively rotating with respect to the damper main body 9, and brakes the relative rotation of the rotor 10 with respect to the damper main body 9; and an intermittent mechanism 14 which intermittently rotates the rotor 10 by the rotation of the link 5. The intermittent mechanism 14 constrains the rotation of the rotor 10 when the rotation of the rotor 10 is stopped.SELECTED DRAWING: Figure 1

Description

本発明は、家具、建築物等に用いられ、本体の開口部に対して扉を開閉可能にするヒンジ装置に関し、特に扉の閉じ動作及び／又は開き動作を制動するダンパが組み込まれるダンパ付きヒンジ装置に関する。 The present invention relates to a hinge device that is used in furniture, buildings, and the like and that can open and close a door with respect to an opening of a main body, and more particularly, a hinge with a damper in which a damper that brakes a closing operation and / or an opening operation of the door is incorporated. Relates to the device.

この種のダンパ付きヒンジ装置として、図１６に示すように、本体側部材９１と、扉側部材９２と、本体側部材９１及び扉側部材９２に回転可能に連結される第一のリンク９３と、本体側部材９１及び扉側部材９２に回転可能に連結される第二のリンク９４と、を備えるものが知られている（特許文献１参照）。ヒンジを構成する本体側部材９１、扉側部材９２、第一のリンク９３及び第二のリンク９４は、四節回転連鎖をなす。本体側部材９１を本体９６に固定すると、本体９６に対して扉９７は一定の運動だけが可能になり、本体９６の開口部が開閉可能になる。図１６（ａ）は扉９７の閉じ位置を示し、図１６（ｂ）は扉９７の中間位置を示し、図１６（ｃ）は扉９７の開き位置を示す。 As shown in FIG. 16, as this type of hinge device with a damper, a main body side member 91, a door side member 92, a first link 93 rotatably connected to the main body side member 91 and the door side member 92, And a second link 94 rotatably connected to the main body side member 91 and the door side member 92 are known (see Patent Document 1). The main body side member 91, the door side member 92, the first link 93, and the second link 94 that constitute the hinge form a four-node rotation chain. When the main body side member 91 is fixed to the main body 96, the door 97 can only move with respect to the main body 96, and the opening of the main body 96 can be opened and closed. 16A shows the closed position of the door 97, FIG. 16B shows the intermediate position of the door 97, and FIG. 16C shows the open position of the door 97.

このダンパ付きヒンジ装置には、扉９７を閉じるとき及び／又は扉を開くとき、扉９７がゆっくり動くようにするダンパ１００が組み込まれる。扉９７の動きに高級感を与えるためである。図１６（ｂ）に示すように、ダンパ１００は、ダンパ本体９９と、ダンパ本体９９に対して回転可能なロータ９８と、を備える。ダンパ本体９９とロータ９８との間には例えばオイルが充填され、オイルの粘性抵抗でロータ９８に制動力を働かせる。ロータ９８には歯車が結合される。第一のリンク９３には、ロータ９８の歯車に噛み合う歯車１０１が取り付けられる。図１６（ｂ）及び図１６（ｃ）に示すように、扉９７が開くとき、第一のリンク９３の歯車１０１とロータ９８の歯車が噛み合い、ロータ９８が回転する。このため、第一のリンク９３に制動力が働き、扉９７がゆっくり開く。 This damper-equipped hinge device incorporates a damper 100 that allows the door 97 to move slowly when the door 97 is closed and / or when the door is opened. This is to give a high-class feeling to the movement of the door 97. As shown in FIG. 16B, the damper 100 includes a damper main body 99 and a rotor 98 that can rotate with respect to the damper main body 99. For example, oil is filled between the damper main body 99 and the rotor 98, and a braking force is applied to the rotor 98 by the viscous resistance of the oil. A gear is coupled to the rotor 98. A gear 101 that meshes with the gear of the rotor 98 is attached to the first link 93. As shown in FIGS. 16B and 16C, when the door 97 is opened, the gear 101 of the first link 93 and the gear of the rotor 98 are engaged with each other, and the rotor 98 rotates. For this reason, a braking force acts on the first link 93 and the door 97 is slowly opened.

ところで、扉９７の閉じ位置から開き位置まで常に第一のリンク９３の歯車１０１とロータ９８の歯車が噛み合うと、常に扉９７にダンパ１００の制動力が働く。ダンパ１００の制動力は、人手による扉９７の開閉を重くする。このため、特許文献１に記載のダンパ付きヒンジ装置においては、図１６（ａ）に示す扉９７の閉じ位置から図１６（ｂ）に示す扉９７の中間位置まで、第一のリンク９３の歯車１０１とロータ９８の歯車との噛み合いを外し、人手による扉９７の開閉を容易にしている。 By the way, when the gear 101 of the first link 93 and the gear of the rotor 98 are always meshed from the closed position to the open position of the door 97, the braking force of the damper 100 is always applied to the door 97. The braking force of the damper 100 makes opening and closing of the door 97 heavy manually. For this reason, in the hinge device with a damper described in Patent Document 1, the gear of the first link 93 from the closed position of the door 97 shown in FIG. 16A to the intermediate position of the door 97 shown in FIG. 101 and the gears of the rotor 98 are disengaged so that the door 97 can be easily opened and closed manually.

独国特許出願公開第１０１５９１４０号明細書German Patent Application No. 10159140

しかし、特許文献１に記載のダンパ付きヒンジにあっては、第一のリンク９３の歯車１０１とロータ９８の歯車との噛み合いが外れたとき、ロータ９８が位置ずれを起こす（言い換えれば回転する）という問題がある。ロータ９８が位置ずれを起こすと、再び第一のリンク９３の歯車１０１とロータ９８の歯車とが噛み合うとき、これらの歯が正規の位置で噛み合うことができなくなる。このため、これらの歯に衝撃が発生したり、又は過大な荷重が発生したりする。ロータ９８の替わりにダンパ本体９９に歯車を設け、ダンパ本体９９を回転させるようにしたダンパ付きヒンジ装置にも同様な問題がある。 However, in the hinge with a damper described in Patent Document 1, when the gear 101 of the first link 93 and the gear of the rotor 98 are disengaged, the rotor 98 is displaced (in other words, rotated). There is a problem. When the rotor 98 is displaced, when the gear 101 of the first link 93 and the gear of the rotor 98 are engaged again, these teeth cannot be engaged at the normal positions. For this reason, an impact is generated on these teeth, or an excessive load is generated. There is a similar problem in the hinge device with a damper in which a gear is provided in the damper main body 99 instead of the rotor 98 and the damper main body 99 is rotated.

そこで本発明は、上記の課題を解決できるダンパ付きヒンジ装置を提供することを目的とする。 Then, an object of this invention is to provide the hinge apparatus with a damper which can solve said subject.

以下、本発明を説明する。なお、本発明の理解を容易にするために、添付図面の参照番号を括弧書きにて付記するが、それにより本発明が図示の形態に限定されるものではない。 The present invention will be described below. In addition, in order to make an understanding of this invention easy, the reference number of an accompanying drawing is attached in parenthesis, However, This invention is not limited to the form of illustration by it.

上記課題を解決するために、本発明は、本体側部材（４）、扉側部材（７）、並びに前記本体側部材（４）及び前記扉側部材（７）の少なくとも一方に回転可能に連結される少なくとも一つのリンク（５又は６）を有するヒンジ（８）と、ダンパ本体（９）及び前記ダンパ本体（９）に対して相対的に回転可能なロータ（１０）を有し、前記ダンパ本体（９）に対する前記ロータ（１０）の相対的な回転を制動するダンパ（１１）と、前記リンク（５又は６）の回転によって前記ロータ（１０）及び前記ダンパ本体（９）の一方を間欠的に回転させる間欠機構（１４，４４，６３）と、を備え、前記間欠機構（１４，４４，６３）は、前記ロータ（１０）及び前記ダンパ本体（９）の一方の回転が停止するとき、前記ロータ（１０）及び前記ダンパ本体（９）の一方の回転を拘束するダンパ付きヒンジ装置である。 In order to solve the above problems, the present invention is rotatably connected to at least one of a main body side member (4), a door side member (7), and the main body side member (4) and the door side member (7). A hinge (8) having at least one link (5 or 6), a damper body (9) and a rotor (10) rotatable relative to the damper body (9), the damper A damper (11) that brakes relative rotation of the rotor (10) with respect to the main body (9) and one of the rotor (10) and the damper main body (9) are intermittently rotated by the rotation of the link (5 or 6). Intermittent mechanism (14, 44, 63) that rotates automatically, and when the rotation of one of the rotor (10) and the damper body (9) stops, the intermittent mechanism (14, 44, 63) The rotor (10) and the rotor Lymph, which is one with a damper hinge device for restraining rotation of the body (9).

本発明によれば、ロータ及びダンパ本体の一方の回転が停止するとき、間欠機構がロータ及びダンパ本体の一方の回転を拘束する。このため、ロータ及びダンパ本体の一方の位置を保持することができ、ロータ及びダンパ本体の一方が位置ずれを起こすのを防止できる。 According to the present invention, when one rotation of the rotor and the damper main body is stopped, the intermittent mechanism restrains one rotation of the rotor and the damper main body. For this reason, one position of a rotor and a damper main body can be hold | maintained, and it can prevent that one of a rotor and a damper main body raise | generates position shift.

本発明の好ましい第一の態様は、前記間欠機構（１４）は、前記ロータ（１０）及び前記ダンパ本体（９）の一方に設けられる従動歯車（１３）と、前記リンク（５又は６）と一緒に回転し、前記従動歯車（１３）に噛み合う原動歯車（１２，４６）と、を備え、前記原動歯車（１２，４６）は、前記原動歯車（１２，４６）の回転中心と同心の円弧形に形成される円弧部（１２ｂ，４６ｂ）を有し、前記ロータ（１０）及び前記ダンパ本体（９）の一方の回転が停止するとき、前記原動歯車（１２，４６）の前記円弧部（１２ｂ，４６ｂ）が前記従動歯車（１３）の隣り合う一対の歯（１３ａ，１３ｂ）に向かい合い、前記一対の歯（１３ａ，１３ｂ）を利用して前記従動歯車（１３）の回転を拘束することを特徴とする。 In a preferred first aspect of the present invention, the intermittent mechanism (14) includes a driven gear (13) provided on one of the rotor (10) and the damper main body (9), and the link (5 or 6). A driving gear (12, 46) that rotates together and meshes with the driven gear (13), and the driving gear (12, 46) is concentric with the center of rotation of the driving gear (12, 46). An arc portion (12b, 46b) formed in an arc shape, and when the rotation of one of the rotor (10) and the damper main body (9) stops, the arc portion of the driving gear (12, 46) (12b, 46b) face a pair of adjacent teeth (13a, 13b) of the driven gear (13) and restrain the rotation of the driven gear (13) using the pair of teeth (13a, 13b). It is characterized by that.

本発明の好ましい第一の態様によれば、従動歯車を特殊な形状に形成しなくても、従動歯車の隣り合う一対の歯を利用して、従動歯車の回転を拘束することができる。 According to the first preferred embodiment of the present invention, the rotation of the driven gear can be constrained using a pair of adjacent teeth of the driven gear without forming the driven gear in a special shape.

本発明の好ましい第二の態様は、前記間欠機構（４４）は、前記ロータ（１０）及び前記ダンパ本体（９）の一方に設けられる従動歯車（４７，５２）と、前記リンク（５又は６）と一緒に回転し、前記従動歯車（４７，５２）に噛み合う原動歯車（１２，５５）と、を備え、前記原動歯車（１２，５５）は、前記原動歯車（１２，５５）の回転中心と同心の円弧形に形成される円弧部（１２ｂ，５５ｂ）を有し、前記従動歯車（４７，５２）は、前記原動歯車（１２，５５）の回転中心と同心の円弧形に形成される円弧部（４８，５３）を有し、前記ロータ（１０）及び前記ダンパ本体（９）の一方の回転が停止するとき、前記原動歯車（１２，５５）の円弧部（１２ｂ，５５ｂ）が前記従動歯車（４７，５２）の円弧部（４８，５３）に向かい合うことを特徴とする。 In a preferred second aspect of the present invention, the intermittent mechanism (44) includes a driven gear (47, 52) provided on one of the rotor (10) and the damper main body (9), and the link (5 or 6). ) And a driven gear (12, 55) meshing with the driven gear (47, 52), and the driving gear (12, 55) is the center of rotation of the driving gear (12, 55). And the driven gears (47, 52) are formed in an arc shape concentric with the rotation center of the driving gear (12, 55). And when the rotation of one of the rotor (10) and the damper main body (9) stops, the arc portion (12b, 55b) of the driving gear (12, 55). On the arcuate part (48, 53) of the driven gear (47, 52). Characterized in that each other to buy.

本発明の好ましい第二の態様によれば、原動歯車の円弧部が従動歯車の円弧部に向かい合うので、従動歯車の回転を確実に拘束することができる。 According to the second preferred embodiment of the present invention, since the arc portion of the driving gear faces the arc portion of the driven gear, the rotation of the driven gear can be reliably restrained.

本発明の好ましい第三の態様は、前記間欠機構（６３）は、前記ロータ（１０）及び前記ダンパ本体（９）の一方に設けられる従動部材（６２，７２）と、前記リンク（５又は６）と一緒に回転し、前記従動部材（６２，７２）に係合する原動部材（６１，７１）と、を備え、前記従動部材（６２，７２）及び前記原動部材（６１，７１）のいずれか一方は、前記原動部材（６１，７１）の回転中心と同心の円弧溝（６５，７４）と、前記円弧溝（６５，７４）に対して傾斜する傾斜溝（６６，７６）と、を有し、前記従動部材（６２，７２）及び前記原動部材（６１，７１）の他方は、軸部（６４，７３）を有し、前記ロータ（１０）及び前記ダンパ本体（９）の一方の回転が停止するとき、前記軸部（６４，７３）が前記円弧溝（６５，７４）に嵌まり、前記リンク（５又は６）の回転によって前記ロータ（１０）及び前記ダンパ本体（９）の一方が回転するとき、前記軸部（６４，７３）が前記傾斜溝（６６，７６）に嵌まることを特徴とする。 In a preferred third aspect of the present invention, the intermittent mechanism (63) includes a driven member (62, 72) provided on one of the rotor (10) and the damper main body (9), and the link (5 or 6). ) And a driving member (61, 71) that engages with the driven member (62, 72), and includes either the driven member (62, 72) or the driving member (61, 71). On the other hand, an arc groove (65, 74) concentric with the rotation center of the driving member (61, 71) and an inclined groove (66, 76) inclined with respect to the arc groove (65, 74) are provided. The other of the driven member (62, 72) and the driving member (61, 71) has a shaft portion (64, 73), and one of the rotor (10) and the damper main body (9). When the rotation stops, the shaft portion (64, 73) is moved into the circular groove (65, 4) and when one of the rotor (10) and the damper main body (9) is rotated by the rotation of the link (5 or 6), the shaft portion (64, 73) is formed in the inclined groove (66, 76).

本発明の好ましい第三の態様によれば、軸部及び円弧溝を利用して、従動部材の回転を拘束することができる。このため、間欠機構の形状をシンプルにすることができる。 According to the third preferred embodiment of the present invention, the rotation of the driven member can be restrained using the shaft portion and the arc groove. For this reason, the shape of the intermittent mechanism can be simplified.

本発明の第一の実施形態のヒンジ装置の側面図（本体及び扉の水平断面図）である。It is a side view (horizontal sectional view of a main part and a door) of a hinge device of a first embodiment of the present invention. 本発明の第一の実施形態のヒンジ装置の斜視図である。It is a perspective view of the hinge apparatus of 1st embodiment of this invention. 本発明の第一の実施形態のヒンジ装置の分解斜視図である。It is a disassembled perspective view of the hinge apparatus of 1st embodiment of this invention. 本発明の第一の実施形態のヒンジ装置の側面図である（図４（ａ）は扉の開き位置を示し、図４（ｂ）は扉の中間位置を示し、図４（ｃ）は扉の閉じ位置を示す）。It is a side view of the hinge apparatus of 1st embodiment of this invention (FIG.4 (a) shows the open position of a door, FIG.4 (b) shows the intermediate position of a door, FIG.4 (c) is a door. Indicates the closed position). 図５（ａ）は図４（ａ）のＡ部拡大図であり、図５（ｂ）は図４（ｂ）のＢ部拡大図であり、図５（ｃ）は図４（ｃ）のＣ部拡大図である。5A is an enlarged view of a portion A of FIG. 4A, FIG. 5B is an enlarged view of a portion B of FIG. 4B, and FIG. 5C is a view of FIG. It is a C section enlarged view. 本発明の第一の実施形態のヒンジ装置の他の例の側面図である（図６（ａ）は扉の開き位置を示し、図６（ｂ）は扉の中間位置を示し、図６（ｃ）は扉の閉じ位置を示す）。It is a side view of the other example of the hinge apparatus of 1st embodiment of this invention (FIG. 6 (a) shows the open position of a door, FIG.6 (b) shows the intermediate position of a door, FIG. c) shows the closed position of the door). 本発明の第二の実施形態のヒンジ装置の側面図である（図７（ａ）は扉の開き位置を示し、図７（ｂ）は扉の中間位置を示し、図７（ｃ）は扉の閉じ位置を示す）。It is a side view of the hinge apparatus of 2nd embodiment of this invention (FIG.7 (a) shows the opening position of a door, FIG.7 (b) shows the intermediate position of a door, FIG.7 (c) is a door. Indicates the closed position). 図８（ａ）は図７（ａ）のＡ部拡大図であり、図８（ｂ）は図７（ｂ）のＢ部拡大図であり、図８（ｃ）は図７（ｃ）のＣ部拡大図である。8A is an enlarged view of a portion A in FIG. 7A, FIG. 8B is an enlarged view of a portion B in FIG. 7B, and FIG. 8C is a view in FIG. 7C. It is a C section enlarged view. 本発明の第二の実施形態のヒンジ装置の他の例の側面図である（図９（ａ）は扉の開き位置を示し、図９（ｂ）は扉の中間位置を示し、図９（ｃ）は扉の閉じ位置を示す）。It is a side view of the other example of the hinge apparatus of 2nd embodiment of this invention (FIG. 9 (a) shows the open position of a door, FIG.9 (b) shows the intermediate position of a door, FIG. c) shows the closed position of the door). 図１０（ａ）は図９（ａ）のＡ部拡大図であり、図１０（ｂ）は図１０（ｂ）のＢ部拡大図であり、図１０（ｃ）は図１０（ｃ）のＣ部拡大図である。10A is an enlarged view of a portion A in FIG. 9A, FIG. 10B is an enlarged view of a portion B in FIG. 10B, and FIG. 10C is a view in FIG. It is a C section enlarged view. 本発明の第三の実施形態のヒンジ装置の側面図である（図１１（ａ）は扉の開き位置を示し、図１１（ｂ）は扉の中間位置を示し、図１１（ｃ）は扉の閉じ位置を示す）。It is a side view of the hinge apparatus of 3rd embodiment of this invention (FIG.11 (a) shows the open position of a door, FIG.11 (b) shows the intermediate position of a door, FIG.11 (c) is a door. Indicates the closed position). 図１２（ａ）は図１１（ａ）のＡ部拡大図であり、図１２（ｂ）は図１１（ｂ）のＢ部拡大図であり、図１２（ｃ）は図１１（ｃ）のＣ部拡大図である。12A is an enlarged view of a portion A in FIG. 11A, FIG. 12B is an enlarged view of a portion B in FIG. 11B, and FIG. 12C is a view in FIG. It is a C section enlarged view. 本発明の第三の実施形態のヒンジ装置の他の例の側面図である（図１３（ａ）は扉の開き位置を示し、図１３（ｂ）は扉の中間位置を示し、図１３（ｃ）は扉の閉じ位置を示す）。It is a side view of the other example of the hinge apparatus of 3rd embodiment of this invention (FIG. 13 (a) shows the open position of a door, FIG.13 (b) shows the intermediate position of a door, FIG. c) shows the closed position of the door). 図１４（ａ）は図１３（ａ）のＡ部拡大図であり、図１４（ｂ）は図１３（ｂ）のＢ部拡大図であり、図１４（ｃ）は図１３（ｃ）のＣ部拡大図である。14A is an enlarged view of part A of FIG. 13A, FIG. 14B is an enlarged view of part B of FIG. 13B, and FIG. 14C is a view of FIG. 13C. It is a C section enlarged view. 本発明のヒンジ装置のヒンジの他の例を示す図である（図１５（ａ）は扉の中間位置を示し、図１５（ｂ）は扉の閉じ位置を示す）。It is a figure which shows the other example of the hinge of the hinge apparatus of this invention (FIG. 15 (a) shows the intermediate position of a door, FIG.15 (b) shows the closed position of a door). 従来のヒンジ装置の側面図である（図１６（ａ）は扉の閉じ位置を示し、図１６（ｂ）は扉の中間位置を示し、図１６（ｃ）は扉の開き位置を示す）。It is a side view of the conventional hinge apparatus (FIG. 16 (a) shows the closed position of a door, FIG.16 (b) shows the intermediate position of a door, FIG.16 (c) shows the open position of a door).

以下添付図面に基づいて、本発明のダンパ付きヒンジ装置（以下、単にヒンジ装置という）の実施形態を詳細に説明する。図１ないし図５は、本発明の第一の実施形態のヒンジ装置を示す。図１は、ヒンジ装置の側面図（ヒンジ装置が取り付けられた本体１及び扉２の水平断面図）を示す。図１に示すように、ヒンジ装置は、ヒンジ８、ダンパ１１、及び間欠機構１４を備える。なお、以下においては、説明の便宜上、本体１を正面から見たときの方向、すなわち図１及び図３に示す前後方向、左右方向、及び上下方向を用いてヒンジ装置の構成を説明する。もちろん、ヒンジ装置の配置は、このような前後、左右、及び上下に限定されるものではない。 Embodiments of a hinge device with a damper (hereinafter simply referred to as a hinge device) according to the present invention will be described below in detail with reference to the accompanying drawings. 1 to 5 show a hinge device according to a first embodiment of the present invention. FIG. 1 is a side view of the hinge device (horizontal sectional view of the main body 1 and the door 2 to which the hinge device is attached). As shown in FIG. 1, the hinge device includes a hinge 8, a damper 11, and an intermittent mechanism 14. In the following, for convenience of explanation, the configuration of the hinge device will be described using directions when the main body 1 is viewed from the front, that is, the front-rear direction, the left-right direction, and the up-down direction shown in FIGS. Of course, the arrangement of the hinge device is not limited to such front and rear, left and right, and top and bottom.

図１に示すように、ヒンジ８は、本体側部材４、扉側部材７、並びに本体側部材４及び扉側部材７に両端部が回転可能に連結される第一のリンク５及び第二のリンク６を備える。以下では、第一のリンク５を内側リンク５と呼び、第二のリンク６を外側リンク６と呼ぶ。本体側部材４は、本体１の側板の内面に取り付けられる。扉側部材７は、扉２の背面に取り付けられる。本体側部材４、扉側部材７、内側リンク５及び外側リンク６は、すべて回り対偶によって連鎖をなす四節回転連鎖である。本体側部材４を固定すると、扉２は一定の運動（水平方向への回転）だけが可能になり、扉２は本体１の前面の開口部を開閉する。なお、ヒンジ８の構成は、少なくとも一つのリンクを有するものであれば、四つのリンクがすべて回り対偶によって連鎖をなすものに限られることはなく、例えば図１５に示すヒンジ（詳しくは後述する）を用いることもできる。 As shown in FIG. 1, the hinge 8 includes a main body side member 4, a door side member 7, a first link 5 and a second link whose both ends are rotatably connected to the main body side member 4 and the door side member 7. A link 6 is provided. Hereinafter, the first link 5 is referred to as the inner link 5, and the second link 6 is referred to as the outer link 6. The main body side member 4 is attached to the inner surface of the side plate of the main body 1. The door side member 7 is attached to the back surface of the door 2. The main body side member 4, the door side member 7, the inner link 5 and the outer link 6 are all a four-node rotating chain that forms a chain by turning pairs. When the main body side member 4 is fixed, the door 2 can only perform a certain movement (rotation in the horizontal direction), and the door 2 opens and closes the opening on the front surface of the main body 1. Note that the configuration of the hinge 8 is not limited to a configuration in which all four links are chained by turning pairs as long as it has at least one link. For example, the hinge shown in FIG. 15 (details will be described later) Can also be used.

図１に示すように、ダンパ１１は、ダンパ本体９と、ダンパ本体９に対して相対的に回転可能なロータ１０と、を備える。ダンパ本体９とロータ１０との間にはオイルが充填される。ダンパ本体９に対してロータ１０が相対的に回転するとき、オイルの粘性抵抗でロータ１０に制動力が働く。なお、図１には、ダンパ本体９が固定され、ロータ１０がダンパ本体９に対して回転可能な例が示されているが、ロータ１０を固定し、ダンパ本体９を回転可能にすることも可能である。また、図１に示すダンパ１１は本体側部材４に取り付けられているが、本体側部材４に限られることはなく、ヒンジ８を構成する四つのリンク（本体側部材４、扉側部材７、第一のリンク５、第二のリンク６）のいずれにもダンパ１１を取り付けることができる。 As shown in FIG. 1, the damper 11 includes a damper body 9 and a rotor 10 that can rotate relative to the damper body 9. Oil is filled between the damper main body 9 and the rotor 10. When the rotor 10 rotates relative to the damper main body 9, a braking force acts on the rotor 10 due to the viscous resistance of oil. 1 shows an example in which the damper main body 9 is fixed and the rotor 10 is rotatable with respect to the damper main body 9. However, the rotor 10 may be fixed and the damper main body 9 may be rotatable. Is possible. 1 is attached to the main body side member 4, but is not limited to the main body side member 4, and the four links (the main body side member 4, the door side member 7, The damper 11 can be attached to either the first link 5 or the second link 6).

間欠機構１４は、内側リンク５の回転によってロータ１０を間欠的に回転させる。すなわち、間欠機構１４は、内側リンク５が連続回転するとき、内側リンク５の回転によってロータ１０を一定期間回転させ、内側リンク５が回転してもロータ１０の回転を一定期間停止させる。この実施形態では、間欠機構１４は、扉２の開き位置（図４（ａ）の位置）から閉じ位置の直前（図４（ｂ）の位置）までは、内側リンク５が回転してもロータ１０の回転を停止させる。そして、間欠機構１４は、扉２の閉じ位置の直前（図４（ｂ）の位置）から閉じ位置（図４（ｃ）の位置）まで内側リンク５の回転によってロータ１０を回転させる。間欠機構１４は、ロータ１０の回転が停止するとき、ロータ１０の回転を拘束する。 The intermittent mechanism 14 rotates the rotor 10 intermittently by the rotation of the inner link 5. That is, the intermittent mechanism 14 rotates the rotor 10 for a certain period by the rotation of the inner link 5 when the inner link 5 rotates continuously, and stops the rotation of the rotor 10 for a certain period even if the inner link 5 rotates. In this embodiment, the intermittent mechanism 14 is a rotor from the opening position of the door 2 (position in FIG. 4A) to immediately before the closing position (position in FIG. 4B) even if the inner link 5 rotates. The rotation of 10 is stopped. Then, the intermittent mechanism 14 rotates the rotor 10 by the rotation of the inner link 5 from immediately before the closing position of the door 2 (position in FIG. 4B) to the closing position (position in FIG. 4C). The intermittent mechanism 14 restrains the rotation of the rotor 10 when the rotation of the rotor 10 stops.

以下に、ヒンジ８、ダンパ１１、間欠機構１４の詳細な構造を順番に説明する。 Below, the detailed structure of the hinge 8, the damper 11, and the intermittent mechanism 14 is demonstrated in order.

図１に示すように、ヒンジ８は、扉側部材７、本体側部材４、内側リンク５及び外側リンク６を備える。本体側部材４は、本体１の側板に取り付けられる取付けプレート１６と、取付けプレート１６に着脱可能に取り付けられるヒンジ本体１７と、を備える。取付けプレート１６は、前後調節ねじ、上下調節ねじ、及び左右調節ねじを備える。各調節ねじを手回しドライバで調整することによって、ヒンジ本体１７を前後方向、上下方向及び左右方向に位置調整可能である。 As shown in FIG. 1, the hinge 8 includes a door side member 7, a main body side member 4, an inner link 5 and an outer link 6. The main body side member 4 includes a mounting plate 16 attached to the side plate of the main body 1 and a hinge main body 17 detachably attached to the mounting plate 16. The mounting plate 16 includes a front / rear adjustment screw, a vertical adjustment screw, and a left / right adjustment screw. The hinge body 17 can be adjusted in position in the front-rear direction, the up-down direction, and the left-right direction by manually turning each adjustment screw and adjusting it with a screwdriver.

図３は、ヒンジ装置の分解斜視図を示す。図３に示すように、ヒンジ本体１７は、対向する一対の側板部１７ａ、及び一対の側板部１７ａを連結する連結板部１７ｂを有して、断面Ｕ字形に形成される。一対の側板部１７ａは、その長手方向を前後方向に向けていて、上下方向に対向して配置される。連結板部１７ｂは、一対の側板部１７ａの長辺部に一体に形成される。ヒンジ本体１７は、その開放部を取付けプレート１６（図１参照）に向けて配置される。ヒンジ本体１７の一対の側板部１７ａの前端部には、長手方向を上下方向に向けた第一及び第二の軸２１，２２が固定される。第一の軸２１には、外側リンク６の一端部が回転可能に連結される。第二の軸２２には、内側リンク５の一端部が回転可能に連結される。 FIG. 3 shows an exploded perspective view of the hinge device. As shown in FIG. 3, the hinge main body 17 has a pair of side plate portions 17a facing each other and a connecting plate portion 17b for connecting the pair of side plate portions 17a, and is formed in a U-shaped cross section. The pair of side plate portions 17a are disposed so as to face each other in the vertical direction with the longitudinal direction thereof directed in the front-rear direction. The connecting plate portion 17b is formed integrally with the long side portion of the pair of side plate portions 17a. The hinge main body 17 is arranged with its open part facing the mounting plate 16 (see FIG. 1). First and second shafts 21 and 22 having a longitudinal direction directed in the vertical direction are fixed to front end portions of the pair of side plate portions 17a of the hinge body 17. One end of the outer link 6 is rotatably connected to the first shaft 21. One end of the inner link 5 is rotatably connected to the second shaft 22.

外側リンク６は、上下方向に対向する一対の側板部６ａと、一対の側板部６ａの長辺部を連結する連結板部６ｂを有して、断面Ｕ字形に形成される。外側リンク６の一対の側板部６ａは、ヒンジ本体１７の一対の側板部１７ａの内側に配置される。外側リンク６の側板部６ａの長手方向の一端部には、第一の軸２１が貫通する貫通孔６ｃが空けられる。外側リンク６の側板部６ａの長手方向の他端部には、第三の軸２３が貫通する貫通孔６ｄが空けられる。 The outer link 6 includes a pair of side plate portions 6a facing each other in the vertical direction and a connecting plate portion 6b that connects the long sides of the pair of side plate portions 6a, and is formed in a U-shaped cross section. The pair of side plate portions 6 a of the outer link 6 is disposed inside the pair of side plate portions 17 a of the hinge body 17. A through hole 6c through which the first shaft 21 passes is formed at one end of the side plate portion 6a of the outer link 6 in the longitudinal direction. A through hole 6d through which the third shaft 23 passes is formed at the other end portion of the side plate portion 6a of the outer link 6 in the longitudinal direction.

内側リンク５は、湾曲した細長い板状に形成される。内側リンク５の長手方向の一端部には、上下方向に対向する一対の側板部５ａが一体に形成される。内側リンク５の一対の側板部５ａは、ヒンジ本体１７の一対の側板部１７ａの内側に配置される。内側リンク５の側板部５ａには、第二の軸２２が貫通する貫通孔５ｃが形成される。内側リンク５の長手方向の他端部には、カール加工等により第四の軸２４が挿入される筒部５ｄが形成される。 The inner link 5 is formed in a curved elongated plate shape. A pair of side plate portions 5 a that are opposed to each other in the vertical direction are integrally formed at one end portion in the longitudinal direction of the inner link 5. The pair of side plate portions 5 a of the inner link 5 is disposed inside the pair of side plate portions 17 a of the hinge body 17. A through hole 5 c through which the second shaft 22 passes is formed in the side plate portion 5 a of the inner link 5. A cylindrical portion 5d into which the fourth shaft 24 is inserted is formed by curling or the like at the other end portion in the longitudinal direction of the inner link 5.

内側リンク５の側板部５ａには、間欠機構を構成する扇形の原動歯車１２が一体に形成される。原動歯車１２は、ロータ１０の従動歯車１３との噛み合いを間欠的にするために、歯車部１２ａと、円弧部１２ｂと、を円周方向に隣接して有する（図５（ａ）も参照）。歯車部１２ａには、円周方向に複数の歯が形成される。歯の形は、インボリュート歯形、サイクロイド歯形等のいずれでもよい。円弧部１２ｂには、歯は形成されていない。円弧部１２ｂはその外縁が、第二の軸２２の中心（すなわち原動歯車１２の回転中心）と同心の円弧形に形成される。この円弧部１２ｂの半径は、歯車部１２ａの歯底円の半径よりも大きく歯先円の半径よりも小さい。 The side plate portion 5a of the inner link 5 is integrally formed with a fan-shaped driving gear 12 that constitutes an intermittent mechanism. The driving gear 12 has a gear portion 12a and an arc portion 12b adjacent to each other in the circumferential direction in order to intermittently engage the driven gear 13 of the rotor 10 (see also FIG. 5 (a)). . A plurality of teeth are formed in the circumferential direction on the gear portion 12a. The tooth shape may be any of an involute tooth shape, a cycloid tooth shape, and the like. No teeth are formed on the arc portion 12b. The outer edge of the arc portion 12b is formed in an arc shape concentric with the center of the second shaft 22 (that is, the rotation center of the driving gear 12). The radius of the arc portion 12b is larger than the radius of the root circle of the gear portion 12a and smaller than the radius of the tip circle.

図１に示すように、扉側部材７（以下カップ部材７という）は、扉２の背面に取り付けられる。図３に示すように、カップ部材７は、扉２の背面の穴に嵌められるカップ本体７ａと、扉２の背面に取り付けられる一対の突出片７ｂと、を備える。突出片７ｂには、ねじの通し孔７ｃが形成される。カップ本体７ａには、凹部７ａ１が形成される。カップ本体７ａには、平行な一対の第三及び第四の軸２３，２４を有するＵ字形の連結部材２５が固定される。第三及び第四の軸２３，２４は上下方向に向くように配置されていて、互いに平行である。第三の軸２３には、外側リンク６の長手方向の他端部が回転可能に連結される。第四の軸２４には、内側リンク５の長手方向の他端部が回転可能に連結される。外側リンク６及び内側リンク５の長手方向の他端部は、カップ本体７ａの凹部７ａ１内に入る。 As shown in FIG. 1, the door side member 7 (hereinafter referred to as cup member 7) is attached to the back surface of the door 2. As shown in FIG. 3, the cup member 7 includes a cup body 7 a that is fitted into a hole on the back surface of the door 2, and a pair of protruding pieces 7 b that are attached to the back surface of the door 2. A threaded hole 7c is formed in the protruding piece 7b. A recess 7a1 is formed in the cup body 7a. A U-shaped connecting member 25 having a pair of parallel third and fourth shafts 23 and 24 is fixed to the cup body 7a. The 3rd and 4th axis | shafts 23 and 24 are arrange | positioned so that it may face an up-down direction, and are mutually parallel. The other end portion in the longitudinal direction of the outer link 6 is rotatably connected to the third shaft 23. The other end portion in the longitudinal direction of the inner link 5 is rotatably connected to the fourth shaft 24. The other ends in the longitudinal direction of the outer link 6 and the inner link 5 enter the recess 7a1 of the cup body 7a.

図１に示すように、ヒンジ本体１７と内側リンク５との間には、付勢手段としてのねじりコイルばね３１が配置される。図３に示すように、ねじりコイルばね３１は、中心線が一致する第一及び第二のコイル部３２，３３と、第一のコイル部３２から引き出された第一のアーム３２ａと、第二のコイル部３３から引き出された第二のアーム３３ａと、第一のコイル部３２と第二のコイル部３３とを連結するＵ字形アーム３４と、を備える。ねじりコイルばね３１の第一及び第二のコイル部３２，３３は、第一の軸２１に嵌められる。ねじりコイルばね３１の第一及び第二のアーム３２ａ，３３ａは、ヒンジ本体１７の連結板部１７ｂに当接する。ねじりコイルばね３１のＵ字形アーム３４は、内側リンク５の起立片５ｅ（図１、図５参照）に当接する。 As shown in FIG. 1, a torsion coil spring 31 as an urging means is disposed between the hinge body 17 and the inner link 5. As shown in FIG. 3, the torsion coil spring 31 includes first and second coil portions 32 and 33 whose center lines coincide with each other, a first arm 32 a drawn out from the first coil portion 32, and a second A second arm 33 a drawn out from the coil portion 33, and a U-shaped arm 34 that connects the first coil portion 32 and the second coil portion 33. The first and second coil portions 32 and 33 of the torsion coil spring 31 are fitted on the first shaft 21. The first and second arms 32 a and 33 a of the torsion coil spring 31 abut on the connecting plate portion 17 b of the hinge body 17. The U-shaped arm 34 of the torsion coil spring 31 abuts on the upright piece 5 e (see FIGS. 1 and 5) of the inner link 5.

図４（ａ）は扉２の開き位置を示し、図４（ｂ）は扉２の中間位置を示し、図４（ｃ）は扉２の閉じ位置を示す。内側リンク５の起立片５ｅは、図４（ｂ）に示す扉２の中間位置でねじりコイルばね３１のねじり量が最も大きく、図４（ｃ）に示す扉２の閉じ位置及び図４（ａ）に示す開き位置で中間位置よりもねじりコイルばね３１のねじり量が小さくなるように形成される。このため、ねじりコイルばね３１は、図４（ｂ）に示す中間位置から図４（ａ）に示す開き位置まで、扉２に開き方向の付勢力を与え、図４（ｂ）に示す中間位置から図４（ｃ）に示す閉じ位置まで扉２に閉じ方向の付勢力を与える。なお、ねじりコイルばね３１が、扉２に開き方向及び閉じ方向のいずれか一方の付勢力を与えるように内側リンク５の起立片５ｅを形成することもできる。また、ねじりコイルばね３１をヒンジ本体１７と外側リンク６との間に配置することもできるし、カップ部材７と内側リンク５又は外側リンク６との間に配置することもできるし、内側リンク５と外側リンク６との間に配置することもできる。さらに、上開きの扉にヒンジを使用する場合等、ねじりコイルばね３１を省略することもできる。 4A shows the opening position of the door 2, FIG. 4B shows the intermediate position of the door 2, and FIG. 4C shows the closing position of the door 2. The standing piece 5e of the inner link 5 has the largest torsional amount of the torsion coil spring 31 at the intermediate position of the door 2 shown in FIG. 4B, and the closed position of the door 2 shown in FIG. The torsion amount of the torsion coil spring 31 is smaller at the opening position shown in FIG. For this reason, the torsion coil spring 31 applies an urging force in the opening direction to the door 2 from the intermediate position shown in FIG. 4B to the open position shown in FIG. 4A, and the intermediate position shown in FIG. To the closing position shown in FIG. 4C is applied to the door 2 in the closing direction. In addition, the standing piece 5e of the inner link 5 can also be formed so that the torsion coil spring 31 applies either one of the urging force in the opening direction or the closing direction to the door 2. Further, the torsion coil spring 31 can be disposed between the hinge body 17 and the outer link 6, or can be disposed between the cup member 7 and the inner link 5 or the outer link 6, or the inner link 5. It can also be arranged between the outer link 6 and the outer link 6. Furthermore, the torsion coil spring 31 can be omitted when a hinge is used for the upper door.

図３に示すように、ダンパ１１は、ダンパ本体９と、ダンパ本体９に対して相対的に回転可能なロータ１０と、を備える。ダンパ本体９は、一端が開口し、他端が底部によって閉じられた有底円筒形に形成されており、内部がロータ１０を収容する収容部１１ａ（図５（ｂ）参照）とされている。ダンパ本体９の開口部はロータ１０で塞がれる。図５（ｂ）に示すように、ダンパ本体９の収容部１１ａの内壁面には、収容部１１ａを二つに区画する一対の凸部１１ｂが円周方向に１８０度の間隔を空けて形成される。 As shown in FIG. 3, the damper 11 includes a damper main body 9 and a rotor 10 that can rotate relative to the damper main body 9. The damper main body 9 is formed in a bottomed cylindrical shape having one end opened and the other end closed by a bottom portion, and the inside is a housing portion 11a for housing the rotor 10 (see FIG. 5B). . The opening of the damper main body 9 is closed by the rotor 10. As shown in FIG. 5 (b), a pair of convex portions 11b that divide the accommodating portion 11a into two are formed on the inner wall surface of the accommodating portion 11a of the damper main body 9 with an interval of 180 degrees in the circumferential direction. Is done.

ロータ１０は、ダンパ本体９に回転可能に支持されるロータ軸４１と、ロータ軸４１に結合されるロータ本体４２と、ロータ軸４１に結合される従動歯車１３と、を備える。ロータ本体４２は、ダンパ本体９の収容部１１ａ内に配置されており、円周方向に１８０度の間隔を空けて半径方向に突出する一対の羽根４３を備える。羽根４３の先端部には、羽根４３と収容部１１ａの内壁面との間の隙間を開閉する弁が設けられる。ダンパ本体９の収容部１１ａとロータ本体４２との間にはオイルが充填される。 The rotor 10 includes a rotor shaft 41 that is rotatably supported by the damper main body 9, a rotor main body 42 that is coupled to the rotor shaft 41, and a driven gear 13 that is coupled to the rotor shaft 41. The rotor main body 42 is disposed in the accommodating portion 11a of the damper main body 9, and includes a pair of blades 43 protruding in the radial direction with an interval of 180 degrees in the circumferential direction. A valve that opens and closes a gap between the blade 43 and the inner wall surface of the housing portion 11 a is provided at the tip of the blade 43. Oil is filled between the accommodating portion 11 a of the damper main body 9 and the rotor main body 42.

例えばロータ１０が図５（ｂ）の時計方向に回転するとき、弁は、羽根４３と収容部１１ａの内壁面との間の隙間を塞ぎ、収容部１１ａの区画Ｓ１を高圧室Ｓ１−１と低圧室Ｓ１−２に区画する。同様に、弁は、収容部１１ａの区画Ｓ２を高圧室Ｓ２−１と低圧室Ｓ２−２に区画する。区画Ｓ１の高圧室Ｓ１−１内のオイルは、弁によって低圧室Ｓ１−２に流れにくくなり、同様に区画Ｓ２の高圧室Ｓ２−１内のオイルは、弁によって低圧室Ｓ２−２に流れにくくなっている。このため、ロータ１０の回転に制動力が働く。一方、ロータ１０が反時計方向に回転するとき、弁は、羽根４３と収容部１１ａの内壁面との間にオイルが流れる隙間を発生させる。このため、ロータ１０に制動力が働きにくくなる。ダンパ１１には、制動力を調整できるように、ダンパ本体９とロータ１０との間の隙間を調整する隙間調整機構を設けることもできる。 For example, when the rotor 10 rotates in the clockwise direction of FIG. 5B, the valve closes the gap between the blade 43 and the inner wall surface of the accommodating portion 11a, and the compartment S1 of the accommodating portion 11a is separated from the high pressure chamber S1-1. Comparting into a low pressure chamber S1-2. Similarly, the valve partitions the compartment S2 of the accommodating portion 11a into a high pressure chamber S2-1 and a low pressure chamber S2-2. The oil in the high pressure chamber S1-1 in the compartment S1 is less likely to flow into the low pressure chamber S1-2 by the valve, and similarly, the oil in the high pressure chamber S2-1 in the compartment S2 is less likely to flow into the low pressure chamber S2-2 by the valve. It has become. For this reason, a braking force acts on the rotation of the rotor 10. On the other hand, when the rotor 10 rotates counterclockwise, the valve generates a gap through which oil flows between the blades 43 and the inner wall surface of the accommodating portion 11a. For this reason, the braking force is less likely to act on the rotor 10. The damper 11 may be provided with a gap adjusting mechanism for adjusting the gap between the damper main body 9 and the rotor 10 so that the braking force can be adjusted.

ダンパ本体９に対してロータ１０が所定角度以上回転すると、ロータ１０の羽根４３とダンパ本体９の凸部１１ｂが当接する。このため、ロータ１０の回転が制限される。この実施形態のダンパ１１は、所定角度以上のロータ１０の回転が制限される有限ダンパである。なお、ダンパ１１には、ロータ１０が無限回転可能な無限ダンパを用いることもできる。また、ダンパ１１には、ロータ１０が時計方向及び反時計方向のいずれに回転したときにも制動力が発生する両方向ダンパを用いることもできる。 When the rotor 10 rotates with respect to the damper main body 9 by a predetermined angle or more, the blades 43 of the rotor 10 and the convex portion 11b of the damper main body 9 come into contact with each other. For this reason, rotation of the rotor 10 is restricted. The damper 11 of this embodiment is a finite damper that limits the rotation of the rotor 10 beyond a predetermined angle. The damper 11 may be an infinite damper that allows the rotor 10 to rotate infinitely. Further, the damper 11 may be a bi-directional damper that generates a braking force when the rotor 10 rotates clockwise or counterclockwise.

図５（ａ）に示すように、間欠機構１４は、内側リンク５に一体に形成される原動歯車１２と、ロータ軸４１に結合される従動歯車１３と、を備える。従動歯車１３は通常の円形の歯車であり、従動歯車１３の周囲には、一定のピッチで複数の歯が形成される。歯の形は、インボリュート歯形、サイクロイド歯形等のいずれでもよい。上記のように、原動歯車１２は、円弧部１２ｂと、歯車部１２ａと、を備える。ロータ１０の回転を停止させるとき、原動歯車１２の円弧部１２ｂが従動歯車１３に向かい合う。原動歯車１２の円弧部１２ｂは、従動歯車１３の隣り合う一対の歯１３ａ，１３ｂに接触するように形成される。ロータ１０を回転させるとき、原動歯車１２の歯車部１２ａが従動歯車１３に噛み合う。なお、従動歯車１３の隣り合う一対の歯１３ａ，１３ｂを利用して、従動歯車１３の回転を拘束することができれば、原動歯車１２の円弧部１２ｂと従動歯車１３の隣り合う一対の歯１３ａ，１３ｂとの間には、僅かな隙間があってもよい。 As shown in FIG. 5A, the intermittent mechanism 14 includes a driving gear 12 that is integrally formed with the inner link 5, and a driven gear 13 that is coupled to the rotor shaft 41. The driven gear 13 is an ordinary circular gear, and a plurality of teeth are formed around the driven gear 13 at a constant pitch. The tooth shape may be any of an involute tooth shape, a cycloid tooth shape, and the like. As described above, the driving gear 12 includes the arc portion 12b and the gear portion 12a. When stopping the rotation of the rotor 10, the arcuate portion 12 b of the driving gear 12 faces the driven gear 13. The arcuate portion 12 b of the driving gear 12 is formed so as to contact a pair of adjacent teeth 13 a and 13 b of the driven gear 13. When the rotor 10 is rotated, the gear portion 12 a of the driving gear 12 meshes with the driven gear 13. If the rotation of the driven gear 13 can be constrained using a pair of adjacent teeth 13a, 13b of the driven gear 13, a pair of adjacent teeth 13a, 13 There may be a slight gap between 13b.

本発明の第一の実施形態のヒンジ装置の動作を図４及び図５を参照して説明する。図４（ａ）は扉２の開き位置を示し、図４（ｂ）は扉２の中間位置（ダンパ作動開始位置）を示し、図４（ｃ）は扉２の閉じ位置を示す。図５（ａ）（ｂ）（ｃ）は、図４（ａ）（ｂ）（ｃ）のＡ部、Ｂ部、Ｃ部の拡大図を示す。図５（ｂ）の右側の図は、ダンパ１１の断面図を示す。 The operation of the hinge device according to the first embodiment of the present invention will be described with reference to FIGS. 4A shows the opening position of the door 2, FIG. 4B shows the intermediate position (damper operation start position) of the door 2, and FIG. 4C shows the closing position of the door 2. FIGS. 5A, 5B, and 5C are enlarged views of portions A, B, and C of FIGS. 4A, 4B, and 4C. The right side of FIG. 5B shows a cross-sectional view of the damper 11.

図４（ａ）に示す扉２の開き位置では、図５（ａ）の拡大図に示すように、原動歯車１２の円弧部１２ｂが従動歯車１３の隣り合う一対の歯１３ａ，１３ｂに向かい合う。このため、原動歯車１２が反時計方向に図５（ｂ）に示す中間位置まで回転しても、従動歯車１３の回転は拘束され（言い換えれば回転不可能であり）、従動歯車１３は一定の位置に保持される。従動歯車１３に結合されるロータ１０も回転することはなく、ダンパ１１の制動力も発生しない。 In the open position of the door 2 shown in FIG. 4A, the arcuate portion 12b of the driving gear 12 faces a pair of adjacent teeth 13a, 13b of the driven gear 13, as shown in the enlarged view of FIG. Therefore, even if the driving gear 12 rotates counterclockwise to the intermediate position shown in FIG. 5B, the rotation of the driven gear 13 is constrained (in other words, cannot be rotated), and the driven gear 13 is fixed. Held in position. The rotor 10 coupled to the driven gear 13 also does not rotate, and the braking force of the damper 11 is not generated.

図５（ｂ）に示す中間位置を過ぎて原動歯車１２が反時計方向に回転すると、原動歯車１２の歯車部１２ａが従動歯車１３に噛み合い始める。このため、原動歯車１２の反時計方向の回転によってダンパ１１のロータ１０が時計方向に回転し、制動力が発生する。原動歯車１２の歯車部１２ａと従動歯車１３との噛み合いは、図５（ｃ）に示す扉２の閉じ位置まで継続する。 When the driving gear 12 rotates counterclockwise past the intermediate position shown in FIG. 5 (b), the gear portion 12 a of the driving gear 12 starts to mesh with the driven gear 13. For this reason, the rotor 10 of the damper 11 rotates in the clockwise direction by the counterclockwise rotation of the driving gear 12, and a braking force is generated. The meshing between the gear portion 12a of the driving gear 12 and the driven gear 13 continues until the door 2 is closed as shown in FIG.

逆に、扉２が図５（ｃ）に示す閉じ位置から図５（ｂ）に示す中間位置まで開くとき、原動歯車１２の時計方向の回転によってダンパ１１のロータ１０が反時計方向に回転する。ダンパ１１には一方向ダンパを用いているので、このときダンパ１１には制動力は働かない。扉２が図５（ｂ）に示す中間位置から図５（ａ）に示す開き位置まで開くとき、原動歯車１２が時計方向に回転しても、ロータ１０は回転することなく、一定の位置を保持する。 Conversely, when the door 2 is opened from the closed position shown in FIG. 5C to the intermediate position shown in FIG. 5B, the rotor 10 of the damper 11 rotates counterclockwise by the clockwise rotation of the driving gear 12. . Since a one-way damper is used as the damper 11, no braking force is applied to the damper 11 at this time. When the door 2 opens from the intermediate position shown in FIG. 5 (b) to the open position shown in FIG. 5 (a), even if the driving gear 12 rotates in the clockwise direction, the rotor 10 does not rotate and remains at a certain position. Hold.

本発明の第一の実施形態のヒンジ装置によれば、以下の効果を奏する。ロータ１０の回転が停止するとき、間欠機構１４がロータ１０の回転を拘束するので、ロータ１０の位置を保持することができる。このため、再び内側リンク５の原動歯車１２の歯車部１２ａとロータ１０の従動歯車１３が噛み合うとき、これらが正規の位置で噛み合う。また、従動歯車１３を特殊な形状に形成しなくても、従動歯車１３の隣り合う一対の歯１３ａ，１３ｂを利用して、従動歯車１３の回転を拘束することができる。さらに、原動歯車１２が内側リンク５に一体に形成されるので、部品点数を削減することができる。さらに、間欠機構１４がロータ１０の位置ずれを防止するので、ロータ１０の回転が制限される有限ダンパを使用することが可能になる。 The hinge device according to the first embodiment of the present invention has the following effects. When the rotation of the rotor 10 stops, the intermittent mechanism 14 restrains the rotation of the rotor 10, so that the position of the rotor 10 can be maintained. For this reason, when the gear portion 12a of the driving gear 12 of the inner link 5 and the driven gear 13 of the rotor 10 are meshed again, they mesh at a regular position. Further, even if the driven gear 13 is not formed in a special shape, the rotation of the driven gear 13 can be constrained using a pair of adjacent teeth 13a and 13b of the driven gear 13. Furthermore, since the driving gear 12 is integrally formed with the inner link 5, the number of parts can be reduced. Furthermore, since the intermittent mechanism 14 prevents the displacement of the rotor 10, it becomes possible to use a finite damper in which the rotation of the rotor 10 is limited.

図６（ａ）は、本発明の第一の実施形態のヒンジ装置の他の例を示す。この例のヒンジ装置も、ヒンジ８、ダンパ１１、及び間欠機構１４を備える。ヒンジ８、ダンパ１１の構成は、第一の実施形態のヒンジ装置と略同一なので、同一の符号を附してその説明を省略する。 Fig.6 (a) shows the other example of the hinge apparatus of 1st embodiment of this invention. The hinge device of this example also includes a hinge 8, a damper 11, and an intermittent mechanism 14. Since the structure of the hinge 8 and the damper 11 is substantially the same as that of the hinge device of the first embodiment, the same reference numerals are given and description thereof is omitted.

この例のヒンジ装置では、間欠機構１４の原動歯車４６が内側リンク５ではなく、外側リンク６に一体に設けられている点が、第一の実施形態のヒンジ装置と異なる。原動歯車４６は、外側リンク６の側板部６ａに一体に形成される。原動歯車４６は、ロータ１０の従動歯車１３との噛み合いを間欠的にするために、歯車部４６ａと、円弧部４６ｂと、を円周方向に隣接して有する（図６（ｂ）参照）。 The hinge device of this example is different from the hinge device of the first embodiment in that the driving gear 46 of the intermittent mechanism 14 is provided integrally with the outer link 6 instead of the inner link 5. The driving gear 46 is formed integrally with the side plate portion 6 a of the outer link 6. The driving gear 46 has a gear portion 46a and an arc portion 46b adjacent to each other in the circumferential direction in order to intermittently engage the driven gear 13 of the rotor 10 (see FIG. 6B).

図６（ａ）に示す開き位置にある扉２を閉じるとき、外側リンク６は図６（ｂ）に示す中間位置までは時計方向に回転し、図６（ｂ）に示す中間位置を過ぎると、逆に反時計方向に回転する。図６（ａ）に示す開き位置から図６（ｂ）に示す中間位置までは、原動歯車４６の円弧部４６ｂが従動歯車１３の隣り合う一対の歯１３ａ，１３ｂに向かい合う。このため、原動歯車４６が時計方向に回転しても、従動歯車１３の回転は拘束される。図６（ｂ）に示す中間位置を過ぎて原動歯車４６が反時計方向に回転すると、図６（ｃ）に示すように原動歯車４６の歯車部４６ａが従動歯車１３に噛み合い始める。このため、原動歯車４６の反時計方向の回転によってダンパ１１のロータ１０が時計方向に回転し、制動力が発生する。原動歯車４６の歯車部４６ａと従動歯車１３との噛み合いは、図６（ｃ）に示す扉２の閉じ位置まで継続する。 When closing the door 2 in the open position shown in FIG. 6 (a), the outer link 6 rotates clockwise to the intermediate position shown in FIG. 6 (b) and passes the intermediate position shown in FIG. 6 (b). Conversely, it rotates counterclockwise. From the open position shown in FIG. 6A to the intermediate position shown in FIG. 6B, the arc portion 46 b of the driving gear 46 faces a pair of adjacent teeth 13 a and 13 b of the driven gear 13. For this reason, even if the driving gear 46 rotates clockwise, the rotation of the driven gear 13 is restrained. When the driving gear 46 rotates counterclockwise past the intermediate position shown in FIG. 6B, the gear portion 46a of the driving gear 46 begins to mesh with the driven gear 13 as shown in FIG. 6C. For this reason, the rotor 10 of the damper 11 rotates in the clockwise direction by the counterclockwise rotation of the driving gear 46, and a braking force is generated. The meshing between the gear portion 46a of the driving gear 46 and the driven gear 13 continues until the door 2 is closed as shown in FIG.

図７及び図８は、本発明の第二の実施形態のヒンジ装置を示す。図７（ａ）に示すように、この例のヒンジ装置も、ヒンジ８、ダンパ１１、及び間欠機構４４を備える。ヒンジ８、ダンパ１１の構成は、第一の実施形態のヒンジ装置と略同一なので、同一の符号を附してその説明を省略する。 7 and 8 show a hinge device according to a second embodiment of the present invention. As shown in FIG. 7A, the hinge device of this example also includes a hinge 8, a damper 11, and an intermittent mechanism 44. Since the structure of the hinge 8 and the damper 11 is substantially the same as that of the hinge device of the first embodiment, the same reference numerals are given and description thereof is omitted.

この例のヒンジ装置では、間欠機構４４の原動歯車１２が内側リンク５に一体に形成される。原動歯車１２は、ロータ１０の従動歯車４７との噛み合いを間欠的にするために、歯車部１２ａと、円弧部１２ｂと、を円周方向に隣接して有する（図８（ｂ）参照）。図８（ｂ）に示すように、歯車部１２ａには、円周方向に複数の歯が形成される。歯の形は、インボリュート歯形、サイクロイド歯形等のいずれでもよい。円弧部１２ｂには、原動歯車１２の歯は形成されていない。円弧部１２ｂはその外縁が、第二の軸２２の中心（すなわち原動歯車１２の回転中心）と同心の円弧形に形成される。この円弧部１２ｂの半径は、歯車部１２ａの歯底円の半径よりも大きく、歯先円の半径よりも小さい。円弧部１２ｂの半径は、例えば歯車部１２ａのピッチ円と等しい。 In the hinge device of this example, the driving gear 12 of the intermittent mechanism 44 is formed integrally with the inner link 5. The driving gear 12 has a gear portion 12a and an arc portion 12b adjacent to each other in the circumferential direction in order to intermittently engage the driven gear 47 of the rotor 10 (see FIG. 8B). As shown in FIG. 8B, the gear portion 12a is formed with a plurality of teeth in the circumferential direction. The tooth shape may be any of an involute tooth shape, a cycloid tooth shape, and the like. The teeth of the driving gear 12 are not formed on the arc portion 12b. The outer edge of the arc portion 12b is formed in an arc shape concentric with the center of the second shaft 22 (that is, the rotation center of the driving gear 12). The radius of the arc portion 12b is larger than the radius of the root circle of the gear portion 12a and smaller than the radius of the tip circle. The radius of the circular arc part 12b is equal to the pitch circle of the gear part 12a, for example.

ロータ軸４１に結合される従動歯車４７は、第一の実施形態のような円形の歯車ではなく、従動歯車４７には略三角形の突出部４７ａが形成される。従動歯車４７には、略半周に渡って歯が形成されるが、突出部４７ａが形成される残りの略半周には歯が形成されない。従動歯車４７の歯の形は、インボリュート歯形、サイクロイド歯形等のいずれでもよい。従動歯車４７の突出部４７ａは、外縁が原動歯車１２の回転中心と同心の円弧形の円弧部４８を有する。図８（ｃ）に示すように、円弧部４８は、従動歯車４７の歯先円４９よりも内側の内側領域５０と、歯先円４９よりも外側の外側領域５１と、を含む。従動歯車４７の円弧部４８は原動歯車１２の円弧部１２ｂに接触するか、又は従動歯車４７の円弧部４８と原動歯車１２の円弧部１２ｂとの間には僅かな隙間がある。なお、円弧部４８は少なくとも外側領域５１を有すればよく、円弧部４８を全て歯先円４９の外側に形成することもできる。 The driven gear 47 coupled to the rotor shaft 41 is not a circular gear as in the first embodiment, and the driven gear 47 is formed with a substantially triangular protrusion 47a. In the driven gear 47, teeth are formed over substantially a half circumference, but no teeth are formed in the remaining substantially half circumference where the protrusion 47a is formed. The tooth shape of the driven gear 47 may be an involute tooth profile, a cycloid tooth profile, or the like. The protrusion 47 a of the driven gear 47 has an arcuate arc portion 48 whose outer edge is concentric with the rotation center of the driving gear 12. As shown in FIG. 8C, the arc portion 48 includes an inner region 50 inside the addendum circle 49 of the driven gear 47 and an outer region 51 outside the addendum circle 49. The arc portion 48 of the driven gear 47 contacts the arc portion 12 b of the driving gear 12, or there is a slight gap between the arc portion 48 of the driven gear 47 and the arc portion 12 b of the driving gear 12. The arc portion 48 only needs to have at least the outer region 51, and the arc portion 48 can be formed entirely outside the addendum circle 49.

本発明の第二の実施形態のヒンジ装置の動作は以下のとおりである。図７（ａ）に示す扉２の開き位置では、図８（ａ）の拡大図に示すように、原動歯車１２の円弧部１２ｂが従動歯車４７の円弧部４８に向かい合う。このため、原動歯車１２が反時計方向に図８（ｂ）に示す中間位置まで回転しても、従動歯車４７の回転は拘束され、従動歯車４７は一定の位置に保持される。従動歯車４７に結合されるロータ１０も回転することはなく、ダンパ１１の制動力も発生しない。 The operation of the hinge device of the second embodiment of the present invention is as follows. At the open position of the door 2 shown in FIG. 7A, the arc portion 12 b of the driving gear 12 faces the arc portion 48 of the driven gear 47 as shown in the enlarged view of FIG. For this reason, even if the driving gear 12 rotates counterclockwise to the intermediate position shown in FIG. 8B, the rotation of the driven gear 47 is restrained and the driven gear 47 is held at a fixed position. The rotor 10 coupled to the driven gear 47 also does not rotate, and the braking force of the damper 11 is not generated.

図８（ｂ）に示す中間位置を過ぎて原動歯車１２が反時計方向に回転すると、原動歯車１２の歯車部１２ａが従動歯車４７に噛み合い始める。このため、原動歯車１２の反時計方向の回転によってダンパ１１のロータ１０が時計方向に回転し、制動力が発生する。原動歯車１２の歯車部１２ａと従動歯車４７との噛み合いは、図８（ｃ）に示す扉２の閉じ位置まで継続する。 When the driving gear 12 rotates counterclockwise past the intermediate position shown in FIG. 8 (b), the gear portion 12 a of the driving gear 12 starts to mesh with the driven gear 47. For this reason, the rotor 10 of the damper 11 rotates in the clockwise direction by the counterclockwise rotation of the driving gear 12, and a braking force is generated. The meshing between the gear portion 12a of the driving gear 12 and the driven gear 47 continues until the door 2 is closed as shown in FIG.

本発明の第二の形態のヒンジ装置によれば、以下の効果を奏する。ロータ１０の回転が停止するとき、間欠機構４４がロータ１０の回転を拘束するので、ロータ１０の位置を保持することができる。このため、ロータ１０の位置ずれを防止することができ、再び内側リンク５の原動歯車１２とロータ１０の従動歯車４７とが噛み合うとき、これらの歯が正規の位置で噛み合う。従動歯車４７の円弧部４８が歯先円４９よりも外側の外側領域５１を有するので、従動歯車４７の円弧部４８を長くすることができ、従動歯車４７の回転を確実に拘束することができる。 The hinge device according to the second aspect of the present invention has the following effects. When the rotation of the rotor 10 stops, the intermittent mechanism 44 restrains the rotation of the rotor 10, so that the position of the rotor 10 can be maintained. For this reason, the position shift of the rotor 10 can be prevented, and when the driving gear 12 of the inner link 5 and the driven gear 47 of the rotor 10 are engaged again, these teeth are engaged at a regular position. Since the arc portion 48 of the driven gear 47 has the outer region 51 outside the addendum circle 49, the arc portion 48 of the driven gear 47 can be lengthened and the rotation of the driven gear 47 can be reliably restrained. .

図９及び図１０は、本発明の第二の実施形態のヒンジ装置の他の例を示す。この例のヒンジ装置も、ヒンジ８、ダンパ１１、及び間欠機構４４を備える。ヒンジ８、ダンパ１１の構成は、第一の実施形態のヒンジ装置と略同一なので、同一の符号を附してその説明を省略する。 9 and 10 show another example of the hinge device according to the second embodiment of the present invention. The hinge device of this example also includes the hinge 8, the damper 11, and the intermittent mechanism 44. Since the structure of the hinge 8 and the damper 11 is substantially the same as that of the hinge device of the first embodiment, the same reference numerals are given and description thereof is omitted.

図９（ａ）に示すように、この例のヒンジ装置では、間欠機構４４の原動歯車５５が内側リンク５ではなく、外側リンク６に一体に設けられている点が、第二の実施形態のヒンジ装置と異なる。原動歯車５５は、外側リンク６の側板部６ａに一体に形成される。原動歯車５５は、ロータ１０の従動歯車５２との噛み合いを間欠的にするために、歯車部５５ａと、円弧部５５ｂと、を円周方向に隣接して有する（図１０（ｂ）参照）。図１０（ｂ）に示すように、円弧部５５ｂはその外縁が、第一の軸２１の中心（すなわち原動歯車５５の回転中心）と同心の円弧形に形成される。この円弧部５５ｂの半径は、歯車部５５ａの歯底円の半径よりも大きく、歯先円の半径よりも小さい。 As shown in FIG. 9A, in the hinge device of this example, the driving gear 55 of the intermittent mechanism 44 is provided integrally with the outer link 6 instead of the inner link 5 in the second embodiment. Different from hinge device. The driving gear 55 is formed integrally with the side plate portion 6 a of the outer link 6. The driving gear 55 has a gear portion 55a and an arc portion 55b adjacent to each other in the circumferential direction in order to intermittently engage the driven gear 52 of the rotor 10 (see FIG. 10B). As shown in FIG. 10B, the outer edge of the arc portion 55 b is formed in an arc shape concentric with the center of the first shaft 21 (that is, the rotation center of the driving gear 55). The radius of the arc portion 55b is larger than the radius of the root circle of the gear portion 55a and smaller than the radius of the tip circle.

図１０（ｂ）に示すように、ロータ１０に結合される従動歯車５２は、半円状の突出部５２ａを備える。従動歯車５２には、略半周に渡って歯が形成されるが、突出部５２ａが形成される残りの略半周には歯が形成されない。従動歯車５２の突出部５２ａは、外縁が原動歯車５５の回転中心と同心の円弧形の円弧部５３を有する。図１０（ｃ）に示すように、円弧部５３は、従動歯車５２の歯先円５６よりも内側の内側領域５４と、歯先円５６よりも外側の外側領域５７と、を含む。 As shown in FIG. 10B, the driven gear 52 coupled to the rotor 10 includes a semicircular protruding portion 52a. In the driven gear 52, teeth are formed over substantially half of the circumference, but no teeth are formed in the remaining substantially half of the circumference where the protrusion 52a is formed. The protrusion 52 a of the driven gear 52 has an arcuate arc portion 53 whose outer edge is concentric with the rotation center of the driving gear 55. As shown in FIG. 10C, the arc portion 53 includes an inner region 54 inside the addendum circle 56 of the driven gear 52 and an outer region 57 outside the addendum circle 56.

図９（ａ）に示す開き位置にある扉２を閉じるとき、外側リンク６は図９（ｂ）に示す中間位置までは時計方向に回転し、図９（ｂ）に示す中間位置を過ぎると、逆に反時計方向に回転する。図１０（ａ）に示す開き位置から図１０（ｂ）に示す中間位置までは、原動歯車５５の円弧部５５ｂが従動歯車５２の円弧部５３に向かい合う。このため、原動歯車５５が時計方向に回転しても、従動歯車５２の回転は拘束される。図１０（ｂ）に示す中間位置を過ぎて原動歯車５５が反時計方向に回転すると、図１０（ｃ）に示すように原動歯車５５の歯車部５５ａが従動歯車５２に噛み合い始める。このため、原動歯車５５の反時計方向の回転によってダンパ１１のロータ１０が時計方向に回転し、制動力が発生する。原動歯車５５の歯車部５５ａと従動歯車５２との噛み合いは、図１０（ｃ）に示す扉２の閉じ位置まで継続する。 When closing the door 2 in the open position shown in FIG. 9A, the outer link 6 rotates clockwise to the intermediate position shown in FIG. 9B, and passes the intermediate position shown in FIG. 9B. Conversely, it rotates counterclockwise. From the open position shown in FIG. 10A to the intermediate position shown in FIG. 10B, the arc portion 55 b of the driving gear 55 faces the arc portion 53 of the driven gear 52. For this reason, even if the driving gear 55 rotates clockwise, the rotation of the driven gear 52 is restrained. When the driving gear 55 rotates counterclockwise past the intermediate position shown in FIG. 10B, the gear portion 55a of the driving gear 55 starts to mesh with the driven gear 52 as shown in FIG. For this reason, the rotor 10 of the damper 11 rotates in the clockwise direction by the counterclockwise rotation of the driving gear 55, and a braking force is generated. The meshing between the gear portion 55a of the driving gear 55 and the driven gear 52 continues until the door 2 is closed as shown in FIG.

図１１及び図１２は、本発明の第三の実施形態のヒンジ装置を示す。図１１（ａ）に示すように、この例のヒンジ装置も、ヒンジ８、ダンパ１１、及び間欠機構６３を備える。ヒンジ８、ダンパ１１の構成は、第一の実施形態のヒンジ装置と略同一なので、同一の符号を附してその説明を省略する。 11 and 12 show a hinge device according to a third embodiment of the present invention. As shown in FIG. 11A, the hinge device of this example also includes a hinge 8, a damper 11, and an intermittent mechanism 63. Since the structure of the hinge 8 and the damper 11 is substantially the same as that of the hinge device of the first embodiment, the same reference numerals are given and description thereof is omitted.

この例のヒンジ装置では、間欠機構６３は、原動部材６１と、従動部材６２と、を備える。扇形の原動部材６１は、内側リンク５に一体に形成される。原動部材６１には、軸部としてのピン６４が設けられる。ピン６４は、第二の軸２２の中心（原動部材６１の回転中心）から所定距離だけ離れた位置に配置される。 In the hinge device of this example, the intermittent mechanism 63 includes a driving member 61 and a driven member 62. The fan-shaped driving member 61 is formed integrally with the inner link 5. The driving member 61 is provided with a pin 64 as a shaft portion. The pin 64 is disposed at a position away from the center of the second shaft 22 (rotation center of the driving member 61) by a predetermined distance.

従動部材６２は、ロータ軸４１に結合される。従動部材６２は、細長い板状に形成されており、長手方向の一端部がロータ軸４１に結合される。図１２（ａ）に示すように、従動部材６２は、原動部材６１の回転中心と同心の円弧溝６５を有する。円弧溝６５の横幅はピン６４の直径に略等しい。円弧溝６５は、従動部材６２の長手方向の一端から従動部材６２の途中まで形成される。従動部材６２には、円弧溝６５に対して傾斜する傾斜溝６６が形成される。傾斜溝６６は、円弧溝６５の奥側の端部からロータ１０に向かって伸びる。傾斜溝６６は直線的に形成されても、曲線的に形成されてもよい。傾斜溝６６の横幅はピン６４の直径に略等しい。なお、上記実施形態では、従動部材６２に円弧溝６５及び傾斜溝６６が形成され、原動部材６１にピン６４が設けられているが、従動部材６２にピン６４を設け、原動部材６１に円弧溝６５及び傾斜溝６６を形成することもできる。 The driven member 62 is coupled to the rotor shaft 41. The driven member 62 is formed in an elongated plate shape, and one end portion in the longitudinal direction is coupled to the rotor shaft 41. As shown in FIG. 12A, the driven member 62 has an arc groove 65 concentric with the rotation center of the driving member 61. The horizontal width of the arc groove 65 is substantially equal to the diameter of the pin 64. The arc groove 65 is formed from one end in the longitudinal direction of the driven member 62 to the middle of the driven member 62. An inclined groove 66 that is inclined with respect to the arc groove 65 is formed in the driven member 62. The inclined groove 66 extends from the end of the arcuate groove 65 toward the rotor 10. The inclined groove 66 may be formed linearly or curvedly. The lateral width of the inclined groove 66 is substantially equal to the diameter of the pin 64. In the above embodiment, the arcuate groove 65 and the inclined groove 66 are formed in the driven member 62 and the pin 64 is provided in the driving member 61. However, the pin 64 is provided in the driven member 62 and the arcing groove is provided in the driving member 61. 65 and the inclined groove 66 can also be formed.

本発明の第三の実施形態のヒンジ装置の動作は以下のとおりである。図１１（ａ）に示す扉２の開き位置では、図１２（ａ）の拡大図に示すように、原動部材６１のピン６４が従動部材６２の円弧溝６５に嵌まる。このため、従動部材６２の回転が拘束される。原動部材６１が反時計方向に図１２（ｂ）に示す中間位置まで回転しても、原動部材６１のピン６４は、従動部材６２の円弧溝６５に嵌まったままである。このため、従動部材６２は回転することが不可能であり、従動部材６２の回転は拘束される。従動部材６２に結合されるロータ１０も回転することはなく、ダンパ１１の制動力も発生しない。 The operation of the hinge device according to the third embodiment of the present invention is as follows. In the open position of the door 2 shown in FIG. 11A, the pin 64 of the driving member 61 fits into the arc groove 65 of the driven member 62 as shown in the enlarged view of FIG. For this reason, the rotation of the driven member 62 is restrained. Even when the driving member 61 rotates counterclockwise to the intermediate position shown in FIG. 12B, the pin 64 of the driving member 61 remains fitted in the arc groove 65 of the driven member 62. For this reason, the driven member 62 cannot be rotated, and the rotation of the driven member 62 is restricted. The rotor 10 coupled to the driven member 62 also does not rotate, and the braking force of the damper 11 is not generated.

図１２（ｂ）に示す中間位置では、原動部材６１のピン６４は、円弧溝６５と傾斜溝６６の交差部に位置する。図１２（ｂ）に示す中間位置を過ぎて原動部材６１が反時計方向に回転すると、図１２（ｃ）に示すように原動部材６１のピン６４が従動部材６２の傾斜溝６６に入る。すると、原動部材６１の反時計方向の回転によって、原動部材６１のピン６４が傾斜溝６６の奥の方に移動し、従動部材６２が時計方向に回転する。従動部材６２の回転は、図１２（ｃ）に示す扉２の閉じ位置まで継続する。 In the intermediate position shown in FIG. 12B, the pin 64 of the driving member 61 is located at the intersection of the arc groove 65 and the inclined groove 66. When the driving member 61 rotates counterclockwise past the intermediate position shown in FIG. 12B, the pin 64 of the driving member 61 enters the inclined groove 66 of the driven member 62 as shown in FIG. Then, by the counterclockwise rotation of the driving member 61, the pin 64 of the driving member 61 moves toward the back of the inclined groove 66, and the driven member 62 rotates in the clockwise direction. The rotation of the driven member 62 continues to the closed position of the door 2 shown in FIG.

本発明の第三の形態のヒンジ装置によれば、以下の効果を奏する。ロータ１０の回転が停止するとき、間欠機構６３がロータ１０の回転を拘束するので、ロータ１０の位置を保持することができる。このため、ロータ１０の位置ずれを防止することができる。また、原動部材６１のピン６４及び従動部材６２の円弧溝６５を利用して、従動部材６２の回転を拘束するので、間欠機構６３の形状をシンプルにすることができる。 The hinge device according to the third aspect of the present invention has the following effects. When the rotation of the rotor 10 stops, the intermittent mechanism 63 restrains the rotation of the rotor 10, so that the position of the rotor 10 can be maintained. For this reason, position shift of the rotor 10 can be prevented. Further, since the rotation of the driven member 62 is restrained by using the pin 64 of the driving member 61 and the arc groove 65 of the driven member 62, the shape of the intermittent mechanism 63 can be simplified.

図１３及び図１４は、本発明の第三の実施形態のヒンジ装置の他の例を示す。この例のヒンジ装置も、ヒンジ８、ダンパ１１、及び間欠機構６３を備える。ヒンジ８、ダンパ１１の構成は、第一の実施形態のヒンジ装置と略同一なので、同一の符号を附してその説明を省略する。 13 and 14 show another example of the hinge device according to the third embodiment of the present invention. The hinge device of this example also includes a hinge 8, a damper 11, and an intermittent mechanism 63. Since the structure of the hinge 8 and the damper 11 is substantially the same as that of the hinge device of the first embodiment, the same reference numerals are given and description thereof is omitted.

図１３（ａ）に示すように、この例のヒンジ装置では、間欠機構６３の原動部材７１が内側リンク５ではなく、外側リンク６に一体に設けられている点が、第三の実施形態のヒンジ装置と異なる。原動部材７１は、第三の実施形態のヒンジ装置と同様にピン７３（図１４（ａ）参照）を有する。 As shown in FIG. 13A, in the hinge device of this example, the driving member 71 of the intermittent mechanism 63 is provided integrally with the outer link 6 instead of the inner link 5 in the third embodiment. Different from hinge device. The driving member 71 has a pin 73 (see FIG. 14A) similarly to the hinge device of the third embodiment.

図１４（ａ）に示すように、従動部材７２は、第一の軸２１の中心（原動部材７１の回転中心）と同心の円弧溝７４を有する。円弧溝７４の横幅はピン７３の直径に略等しい。従動部材７２には、円弧溝７４の奥側の端部から傾斜する傾斜溝７６が形成される。傾斜溝７６は円弧溝７４の端部からロータ１０に向かって伸びる。傾斜溝７６は直線的に形成されても、曲線的に形成されてもよい。傾斜溝７６の横幅は、ピン７３の直径に略等しい。 As shown in FIG. 14A, the driven member 72 has an arc groove 74 concentric with the center of the first shaft 21 (the rotation center of the driving member 71). The lateral width of the arc groove 74 is substantially equal to the diameter of the pin 73. The driven member 72 is formed with an inclined groove 76 that is inclined from the end on the back side of the arc groove 74. The inclined groove 76 extends from the end of the arc groove 74 toward the rotor 10. The inclined groove 76 may be formed linearly or curvedly. The lateral width of the inclined groove 76 is substantially equal to the diameter of the pin 73.

図１３（ａ）に示す開き位置にある扉２を閉じるとき、原動部材７１は図１３（ｂ）に示す中間位置までは時計方向に回転し、図１３（ｂ）に示す中間位置を過ぎると、逆に反時計方向に回転する。図１４（ａ）に示す開き位置から図１４（ｂ）に示す中間位置までは、原動部材７１のピン７３が従動部材７２の円弧溝７４に嵌まったままであり、従動部材７２の回転が拘束される。 When closing the door 2 in the open position shown in FIG. 13 (a), the driving member 71 rotates clockwise to the intermediate position shown in FIG. 13 (b) and passes the intermediate position shown in FIG. 13 (b). Conversely, it rotates counterclockwise. From the open position shown in FIG. 14A to the intermediate position shown in FIG. 14B, the pin 73 of the driving member 71 remains fitted in the arc groove 74 of the driven member 72, and the rotation of the driven member 72 is restrained. Is done.

図１４（ｂ）に示す中間位置を過ぎて原動部材７１が反時計方向に回転すると、図１４（ｃ）に示すように原動部材７１のピン７３が従動部材７２の傾斜溝７６に嵌まり始める。このため、原動部材７１の反時計方向の回転によってダンパ１１のロータ１０が時計方向に回転し、制動力が発生する。原動部材７１のピン７３と従動部材７２の傾斜溝７６との係合は、図１４（ｃ）に示す扉２の閉じ位置まで継続する。 When the driving member 71 rotates counterclockwise past the intermediate position shown in FIG. 14B, the pin 73 of the driving member 71 starts to fit into the inclined groove 76 of the driven member 72 as shown in FIG. . For this reason, the rotor 10 of the damper 11 is rotated in the clockwise direction by the counterclockwise rotation of the driving member 71, and a braking force is generated. The engagement between the pin 73 of the driving member 71 and the inclined groove 76 of the driven member 72 continues until the door 2 is closed as shown in FIG.

図１５は、ヒンジの他の例を示す。本実施形態のヒンジは、上記第一ないし上記第三の実施形態のように、四つのリンクが全て回り対偶で連結される四節回転連鎖のヒンジに限られることはない。例えば、図１５（ａ）（ｂ）に示すように、本体側部材８１に第一のリンク８３の一端部を回転可能に連結し、扉側部材８２に第一のリンク８３の他端部を回転可能にかつスライド可能に連結し、扉側部材８２に第二のリンク８４の一端部を回転可能に連結し、本体側部材８１に第二のリンク８４の他端部をスライド可能に連結し、第一のリンク８３と第二のリンク８４とを回転可能に連結するヒンジを使用することもできる。また、第一のリンク８３の他端部を図示しない連結リンクを介して扉側部材８２に回転可能に連結し、第二のリンク８４の他端部を図示しない連結リンクを介して本体側部材８１に回転可能に連結するヒンジ（軸が７個のヒンジ）を用いることもできる。 FIG. 15 shows another example of the hinge. The hinge of this embodiment is not limited to the hinge of a four-node rotation chain in which all four links are connected in pairs as in the first to third embodiments. For example, as shown in FIGS. 15A and 15B, one end of the first link 83 is rotatably connected to the main body side member 81, and the other end of the first link 83 is connected to the door side member 82. The second link 84 is rotatably connected to the door-side member 82 and the other end of the second link 84 is slidably connected to the body-side member 81. A hinge that rotatably connects the first link 83 and the second link 84 can also be used. Further, the other end portion of the first link 83 is rotatably connected to the door side member 82 via a connection link (not shown), and the other end portion of the second link 84 is connected to the main body side member via a connection link (not shown). It is also possible to use a hinge (a hinge having seven shafts) that is rotatably connected to 81.

なお、本発明は、上記実施形態に具現化されるのに限られることはなく、本発明の要旨を変更しない範囲で様々な実施形態に具現化可能である。上記第一ないし上記第三の実施形態のヒンジ装置のヒンジ、ダンパ、間欠機構の形状、構造は一例であり、本発明の要旨を変更しない範囲で他の形状、構造を採用し得る。 The present invention is not limited to the embodiment described above, and can be embodied in various embodiments without departing from the scope of the present invention. The shapes and structures of the hinges, dampers, and intermittent mechanisms of the hinge devices of the first to third embodiments are merely examples, and other shapes and structures can be adopted without departing from the scope of the present invention.

１…本体
２…扉
４…本体側部材
５…内側リンク（リンク）
６…外側リンク（リンク）
７…カップ部材（扉側部材）
８…ヒンジ
９…ダンパ本体
１０…ロータ
１１…ダンパ
１２…原動歯車
１２ａ…歯車部
１２ｂ…円弧部
１３…従動歯車
１３ａ，１３ｂ…従動歯車の一対の歯
１４…間欠機構
２１〜２４…第一〜第四の軸
４４…間欠機構
４６…原動歯車
４６ａ…歯車部
４６ｂ…円弧部
４７…従動歯車
４８…円弧部
４９…歯先円
５５…原動歯車
５５ａ…歯車部
５５ｂ…円弧部
５２…従動歯車
５３…円弧部
５４…内側領域
５６…歯先円
５７…外側領域
６１…原動部材
６２…従動部材
６３…間欠機構
６４…ピン（軸部）
６５…円弧溝
６６…傾斜溝
７１…原動部材
７２…従動部材
７３…ピン（軸部）
７４…円弧溝
７６…傾斜溝 DESCRIPTION OF SYMBOLS 1 ... Main body 2 ... Door 4 ... Main body side member 5 ... Inner link (link)
6 ... Outside link (link)
7 ... Cup member (door side member)
DESCRIPTION OF SYMBOLS 8 ... Hinge 9 ... Damper main body 10 ... Rotor 11 ... Damper 12 ... Driving gear 12a ... Gear part 12b ... Arc part 13 ... Driven gear 13a, 13b ... A pair of teeth 14 of a driven gear ... Intermittent mechanism 21-24 ... First- Fourth shaft 44 ... Intermittent mechanism 46 ... Drive gear 46a ... Gear portion 46b ... Arc portion 47 ... Drive gear 48 ... Arc portion 49 ... Tip circle 55 ... Drive gear 55a ... Gear portion 55b ... Arc portion 52 ... Drive gear 53 ... Arc portion 54 ... Inner region 56 ... Tooth circle 57 ... Outer region 61 ... Primary member 62 ... Following member 63 ... Intermittent mechanism 64 ... Pin (shaft)
65 ... Circular groove 66 ... Inclined groove 71 ... Driving member 72 ... Follower member 73 ... Pin (shaft)
74 ... Arc groove 76 ... Inclined groove

Claims

A main body side member, a door side member, and a hinge having at least one link rotatably connected to at least one of the main body side member and the door side member;
A damper body and a rotor rotatable relative to the damper body, and a damper for braking relative rotation of the rotor with respect to the damper body;
An intermittent mechanism for intermittently rotating one of the rotor and the damper main body by the rotation of the link,
The intermittent mechanism is a hinge device with a damper that restrains one rotation of the rotor and the damper main body when one rotation of the rotor and the damper main body stops.

The intermittent mechanism includes a driven gear provided on one of the rotor and the damper main body, and a driving gear that rotates together with the link and meshes with the driven gear.
The driving gear has an arc portion formed in an arc shape concentric with the rotation center of the driving gear,
When the rotation of one of the rotor and the damper body stops, the arc portion of the driving gear faces a pair of adjacent teeth of the driven gear and restrains the rotation of the driven gear using the pair of teeth. The hinge device with a damper according to claim 1, wherein:

The intermittent mechanism includes a driven gear provided on one of the rotor and the damper main body, and a driving gear that rotates together with the link and meshes with the driven gear.
The driving gear has an arc portion formed in an arc shape concentric with the rotation center of the driving gear,
The driven gear has an arc portion formed in an arc shape concentric with the rotation center of the driving gear;
The hinge device with a damper according to claim 1, wherein when one of the rotor and the damper main body stops rotating, the arc portion of the driving gear faces the arc portion of the driven gear.

The hinge device with a damper according to claim 3, wherein the arc portion of the driven gear includes an outer region outside a tooth tip circle of the driven gear.

The intermittent mechanism includes a driven member provided on one of the rotor and the damper main body, and a driving member that rotates together with the link and engages the driven member.
Any one of the driven member and the driving member has an arc groove concentric with the rotation center of the driving member, and an inclined groove inclined with respect to the arc groove,
The other of the driven member and the driving member has a shaft portion,
When the rotation of one of the rotor and the damper main body stops, the shaft portion fits into the arc groove,
2. The hinge device with a damper according to claim 1, wherein when one of the rotor and the damper main body is rotated by the rotation of the link, the shaft portion is fitted into the inclined groove.

6. The hinge device with a damper according to claim 2, wherein the driving gear or the driving member is formed integrally with the link.

The hinge device with a damper according to any one of claims 1 to 6, wherein the damper is a finite damper in which relative rotation of the rotor with respect to the damper main body is restricted by a predetermined angle or more.