JP2016133213A

JP2016133213A - Hinge device

Info

Publication number: JP2016133213A
Application number: JP2015010416A
Authority: JP
Inventors: 和征石ヶ谷; Kazumasa Ishigaya
Original assignee: Sugatsune Kogyo Co Ltd
Current assignee: Sugatsune Kogyo Co Ltd
Priority date: 2015-01-22
Filing date: 2015-01-22
Publication date: 2016-07-25
Anticipated expiration: 2035-01-22
Also published as: JP6038968B2

Abstract

PROBLEM TO BE SOLVED: To hold a second member at a desired rotating angle without increasing a diameter of a rotating shaft of a hinge device.SOLUTION: A first hinge main body 10 of a hinge device 3 is installed at a first member 1 such as a casing and the like and a second hinge main body 20 is installed at a second member 2 such as a door and the like. Hinge main bodies 10, 20 are connected by a plurality of links 31 to 36. In at least a part of rotatable range of the second hinge main body 20, a friction mechanism 40 generates a frictional resistance capable of holding a rotating angle of the second hinge main body 20. A first operating member 41 of the friction mechanism 40 is rotatably connected to the link 31 of the first hinge main body 10 or 20. A second operating member 42 is rotatably connected to another link 34 and its linear motion can be carried out in respect to the first operating member 41.SELECTED DRAWING: Figure 2

Description

本発明は、例えば筐体等の第１部材に対して扉等の第２部材を回転可能に連結するヒンジ装置に関する。 The present invention relates to a hinge device that rotatably connects a second member such as a door to a first member such as a housing.

例えば、パチスロ等の遊戯機（開閉扉装置）においては、正面部が開き戸式の扉になっており、かつ閉状態で少し上向きに傾けられている。そのため、半開状態の扉には自重によって自然に閉じる向きにトルクが働く。一方、遊戯機の内部をメンテナンス等する際は、扉を半開状態ないしは開状態に維持しておく必要がある。扉を９０度以上開けば、扉がより開く側に倒れようとするが、そうすると隣の遊戯機の利用者の邪魔になってしまう。 For example, in a game machine (opening / closing door device) such as a pachislot, the front portion is a hinged door and is tilted upward slightly in a closed state. Therefore, a torque is applied to the half-open door in a direction in which the door is naturally closed by its own weight. On the other hand, when maintaining the inside of the game machine, it is necessary to keep the door half open or open. If the door is opened 90 degrees or more, it will fall to the side where the door opens more, but this will disturb the user of the adjacent game machine.

そこで、例えば特許文献１、２のヒンジ装置では、リンクどうしを連結する回転軸に摩擦抵抗を発生されている。詳しくは、特許文献１では、１つの回転軸の外周に環状の圧接部材を巻き付けて圧接している。これによって、扉が自重で閉まろうとすると、回転軸の外周面と圧接部材の内周面との間に摩擦抵抗を起こさせることで回転軸の回転を阻止し、ひいては、扉を所望の半開き角度に保持している。 Therefore, for example, in the hinge devices of Patent Documents 1 and 2, frictional resistance is generated on the rotating shaft that connects the links. Specifically, in Patent Document 1, an annular pressure contact member is wound around the outer periphery of one rotating shaft to be in pressure contact. As a result, when the door is closed by its own weight, the rotation of the rotating shaft is prevented by causing a frictional resistance between the outer peripheral surface of the rotating shaft and the inner peripheral surface of the pressure contact member, and thus the door is opened to a desired half-open angle. Hold on.

特許文献２のヒンジ装置では、板状の圧接部材が回転軸を軸線方向に押圧することで、摩擦抵抗を得ている。 In the hinge device of Patent Document 2, the plate-like press contact member presses the rotating shaft in the axial direction to obtain a frictional resistance.

実用新案登録第３１８８３９１号公報Utility Model Registration No. 3188391 特許第５４５１９７８号公報Japanese Patent No. 5451978

上掲特許文献１、２のヒンジ装置においては、所要の摩擦抵抗を得るには回転軸を太くすることで、回転軸と圧接部材との接触面積を大きくする必要がある。そのため、ヒンジ装置が大型化していた。 In the hinge devices disclosed in Patent Documents 1 and 2, it is necessary to increase the contact area between the rotating shaft and the pressure contact member by thickening the rotating shaft in order to obtain the required frictional resistance. Therefore, the hinge device has been enlarged.

本発明は、上記事情に鑑み、遊技機等の開閉扉装置に用いられるヒンジ装置において、回転軸を太くすることなく、扉等の第２部材を所望の回転角度に保持することを目的とする。 In view of the above circumstances, an object of the present invention is to hold a second member such as a door at a desired rotation angle without increasing the rotation axis in a hinge device used in an opening / closing door device such as a gaming machine. .

上記課題を解決するために、本発明は、第１部材に対して第２部材を回転可能に連結するヒンジ装置であって、
前記第１部材に設けられる第１ヒンジ本体と、
前記第２部材に設けられる第２ヒンジ本体と、
前記第１ヒンジ本体と前記第２ヒンジ本体とを連繋する複数のリンクと、
前記第１ヒンジ本体に対する前記第２ヒンジ本体の回転可能範囲の少なくとも一部で前記第２ヒンジ本体の回転角度を保持可能な摩擦抵抗を発生させる摩擦機構と、
を備えたヒンジ装置において、
前記摩擦機構は、
前記第１、第２ヒンジ本体及び前記複数のリンクのうち１の部材に回転可能に連結された第１作動部材と、
前記第１、第２ヒンジ本体及び前記複数のリンクのうち他の１の部材に回転可能に連結されるとともに、前記第１作動部材に対して直線移動可能な第２作動部材と、
を含むことを特徴とする。 In order to solve the above problems, the present invention is a hinge device that rotatably connects a second member to a first member,
A first hinge body provided on the first member;
A second hinge body provided on the second member;
A plurality of links connecting the first hinge body and the second hinge body;
A friction mechanism that generates a frictional resistance capable of maintaining a rotation angle of the second hinge body in at least a part of a rotatable range of the second hinge body with respect to the first hinge body;
In the hinge device with
The friction mechanism is
A first actuating member rotatably connected to one member of the first and second hinge bodies and the plurality of links;
A second actuating member that is rotatably connected to another member of the first and second hinge bodies and the plurality of links, and is linearly movable with respect to the first actuating member;
It is characterized by including.

このヒンジ装置によれば、第２部材が第１部材に対して相対回転しようとすると、摩擦機構の第２作動部材が第１作動部材に対して直線移動しようとすることで、これら第１、第２作動部材どうし間に第２ヒンジ本体の回転角度を保持可能な摩擦抵抗を発生させることができる。したがって、ヒンジ装置の回転軸を太くすることなく、第２部材を所望の回転角度に確実に保持できる。 According to this hinge device, when the second member tries to rotate relative to the first member, the second operating member of the friction mechanism tries to move linearly with respect to the first operating member. A frictional resistance capable of maintaining the rotation angle of the second hinge body between the second actuating members can be generated. Therefore, the second member can be reliably held at a desired rotation angle without increasing the rotation axis of the hinge device.

前記ヒンジ装置が、前記第１作動部材に設けられた環状部材を更に備え、前記第２作動部材が、前記環状部材の内部に配置されていることが好ましい。これによって、第２部材の前記相対回転時に第１、第２作動部材どうし間に摩擦抵抗を確実に発現させることができる。また、第２作動部材の各箇所が環状部材に出し入れされることで圧入抵抗を発現させることもできる。この結果、第２部材を所望の回転角度に確実に保持できる。 It is preferable that the hinge device further includes an annular member provided on the first actuating member, and the second actuating member is disposed inside the annular member. Thus, it is possible to reliably cause a friction resistance between the first and second actuating members during the relative rotation of the second member. Moreover, press-fit resistance can also be made to express by each part of a 2nd action | operation member being taken in / out of an annular member. As a result, the second member can be reliably held at a desired rotation angle.

前記ヒンジ装置が、前記環状部材の内部に設けられた摩擦板を更に備え、前記摩擦板が、前記第２作動部材と圧接されることが好ましい。これによって、第２作動部材に働く摩擦抵抗を大きくでき、第２部材を所望の回転角度に確実に保持できる。 It is preferable that the hinge device further includes a friction plate provided inside the annular member, and the friction plate is in pressure contact with the second operating member. Accordingly, the frictional resistance acting on the second operating member can be increased, and the second member can be reliably held at a desired rotation angle.

前記環状部材と前記摩擦板との間に弾性部材が介在されていることが好ましい。これによって、前記摩擦抵抗を十分に大きくでき、第２部材を所望の回転角度に確実に保持できる。 It is preferable that an elastic member is interposed between the annular member and the friction plate. Thereby, the frictional resistance can be sufficiently increased, and the second member can be reliably held at a desired rotation angle.

前記第２ヒンジ本体が前記第１ヒンジ本体に対して単位回転角度だけ回転したときの前記第２作動部材の前記第１作動部材に対する移動量が、前記回転可能範囲の両端部では相対的に小さく、前記回転可能範囲の中間部では相対的に大きいことが好ましい。これによって、前記回転可能範囲の中間部における回転抵抗トルクを前記回転可能範囲の両端部における回転抵抗トルクよりも大きくできる。この結果、第２部材を回転可能範囲の前記中間部あたりの回転角度に確実に保持することができる。 When the second hinge body rotates relative to the first hinge body by a unit rotation angle, the movement amount of the second actuation member relative to the first actuation member is relatively small at both ends of the rotatable range. It is preferable that the intermediate portion of the rotatable range is relatively large. Thereby, the rotational resistance torque at the intermediate portion of the rotatable range can be made larger than the rotational resistance torque at both ends of the rotatable range. As a result, the second member can be reliably held at the rotation angle around the intermediate portion of the rotatable range.

前記第１作動部材又は第２作動部材が、前記第１、第２ヒンジ本体及び前記複数のリンクのうち２つの部材どうし間の回転軸と同軸まわりに前記２つの部材に対して回転可能であることが好ましい。これによって、前記２つの部材どうし間の回転軸が、前記第１作動部材又は第２作動部材の連結軸を兼ねることができる。
前記第１、第２作動部材の他方は、他のリンクの中間部に連結されていることが好ましい。
前記第１、第２ヒンジ本体及び４つのリンクによって七節リンク機構が構成されており、前記第１、第２作動部材の一方が、前記第１ヒンジ本体と１のリンクとの回転軸に連結され、前記第１、第２作動部材の他方が、他のリンクの中間部に連結されていることが好ましい。 The first actuating member or the second actuating member is rotatable with respect to the two members around the same axis as a rotation axis between two members of the first and second hinge bodies and the plurality of links. It is preferable. Thereby, the rotating shaft between the two members can also serve as the connecting shaft of the first operating member or the second operating member.
The other of the first and second actuating members is preferably connected to an intermediate part of another link.
The first and second hinge bodies and the four links form a seven-bar linkage mechanism, and one of the first and second actuating members is connected to the rotation shaft of the first hinge body and the one link. It is preferable that the other of the first and second actuating members is connected to an intermediate portion of another link.

前記第２部材の回転軸が、鉛直に対して傾けられており、
前記回転可能範囲の一部の自然回転阻止範囲では、前記第１、第２作動部材どうし間の摩擦による回転抵抗トルクが、前記第２部材の自重による自然回転トルクを上回ることが好ましい。これによって、第２部材が上向きに傾いていても自重で自然と回転するのを阻止でき、第２部材を所望の回転角度に確実に保持できる。 The rotation axis of the second member is inclined with respect to the vertical;
In a part of the natural rotation prevention range of the rotatable range, it is preferable that the rotational resistance torque due to the friction between the first and second actuating members exceeds the natural rotational torque due to the weight of the second member. Thereby, even if the second member is inclined upward, it can be prevented from rotating naturally by its own weight, and the second member can be reliably held at a desired rotation angle.

本発明によれば、ヒンジ装置の回転軸を太くすることなく、第２部材を所望の回転角度に保持することができる。 According to the present invention, the second member can be held at a desired rotation angle without increasing the rotation axis of the hinge device.

図１（ａ）は、本発明の第１実施形態に係るヒンジ装置を、扉が全開のときの状態で示す側面図である。図１（ｂ）は、上記ヒンジ装置の斜視図である。Fig.1 (a) is a side view which shows the hinge apparatus based on 1st Embodiment of this invention in the state when a door is fully open. FIG. 1B is a perspective view of the hinge device. 図２（ａ）は、図１（ａ）のＩＩａ−ＩＩａ線に沿う、上記ヒンジ装置の断面図である。図２（ｂ）は、上記ヒンジ装置を、扉が半開きのときの状態にて示す断面図である。図２（ｃ）は、上記ヒンジ装置を、扉が閉じているときの状態にて示す断面図である。Fig.2 (a) is sectional drawing of the said hinge apparatus in alignment with the IIa-IIa line | wire of Fig.1 (a). FIG.2 (b) is sectional drawing which shows the said hinge apparatus in the state when a door is half open. FIG.2 (c) is sectional drawing which shows the said hinge apparatus in the state when a door is closed. 図３は、上記ヒンジ装置の分解斜視図である。FIG. 3 is an exploded perspective view of the hinge device. 図４（ａ）は、上記ヒンジ装置の摩擦機構の側面図である。図４（ｂ）は、上記摩擦機構の底面図である。FIG. 4A is a side view of the friction mechanism of the hinge device. FIG. 4B is a bottom view of the friction mechanism. 図５は、図４（ａ）のＶ−Ｖ線に沿う、上記摩擦機構の縦断面図である。FIG. 5 is a longitudinal sectional view of the friction mechanism taken along line VV in FIG. 図６は、図４（ｂ）のＶＩ−ＶＩ線に沿う、上記摩擦機構の横断面図である。FIG. 6 is a cross-sectional view of the friction mechanism taken along the line VI-VI in FIG. 図７（ａ）は、上記摩擦機構の分解斜視図である図７（ｂ）は、上記摩擦機構を別の角度から見た分解斜視図である。FIG. 7A is an exploded perspective view of the friction mechanism. FIG. 7B is an exploded perspective view of the friction mechanism as seen from another angle. 図８（ａ）は、上記摩擦機構の環状部材の両端部の分解斜視図である。図８（ｂ）は、上記環状部材の底面図である。FIG. 8A is an exploded perspective view of both ends of the annular member of the friction mechanism. FIG. 8B is a bottom view of the annular member. 図９（ａ）は、上記ヒンジ装置を備えた遊技機を、扉を開いた状態で示す斜視図である。図９（ｂ）は、上記遊技機を、扉を閉じた状態で示す側面図である。FIG. 9A is a perspective view showing a gaming machine provided with the hinge device in a state where a door is opened. FIG. 9B is a side view showing the gaming machine with the door closed. 図１０は、扉の開き角度に対する、単位回転角度あたりの摩擦機構の伸縮量及び回転抵抗トルク、並びに自然回転トルクの関係を示すグラフである。FIG. 10 is a graph showing the relationship between the amount of expansion and contraction of the friction mechanism per unit rotation angle, the rotation resistance torque, and the natural rotation torque with respect to the door opening angle. 図１１（ａ）は、本発明の第２実施形態に係るヒンジ装置を、扉が全開のときの状態で示す側面図である。図１１（ｂ）は、図１１（ａ）のヒンジ装置の斜視図である。Fig.11 (a) is a side view which shows the hinge apparatus which concerns on 2nd Embodiment of this invention in the state when a door is fully open. FIG.11 (b) is a perspective view of the hinge apparatus of Fig.11 (a). 図１２（ａ）は、図１１（ａ）のＸＩＩａ−ＸＩＩａ線に沿う断面図である。図１２（ｂ）は、上記第２実施形態のヒンジ装置、を扉が閉じているときの状態にて示す断面図である。Fig.12 (a) is sectional drawing which follows the XIIa-XIIa line | wire of Fig.11 (a). FIG. 12B is a cross-sectional view showing the hinge device of the second embodiment when the door is closed. 図１３は、上記第２実施形態のヒンジ装置の分解斜視図である。FIG. 13 is an exploded perspective view of the hinge device of the second embodiment. 図１４（ａ）は、本発明の第３実施形態に係るヒンジ装置を、扉が全開のときの状態で示す側面図である。図１４（ｂ）は、図１４（ａ）のヒンジ装置の斜視図である。Fig.14 (a) is a side view which shows the hinge apparatus based on 3rd Embodiment of this invention in the state when a door is fully open. FIG.14 (b) is a perspective view of the hinge apparatus of Fig.14 (a). 図１５（ａ）は、図１４（ａ）のＸＶａ−ＸＶａ線に沿う断面図である。図１５（ｂ）は、上記第３実施形態のヒンジ装置を、扉が閉じているときの状態にて示す断面図である。Fig.15 (a) is sectional drawing which follows the XVa-XVa line | wire of Fig.14 (a). FIG. 15B is a cross-sectional view showing the hinge device of the third embodiment in a state where the door is closed.

以下、本発明の実施形態を図面にしたがって説明する。
図１〜図１０は、本発明の第１実施形態を示したものである。図９に示すように、パチスロ台等の遊技機Ｍは、筐体１（第１部材）と、扉２（第２部材）と、ヒンジ装置３を有している。図９（ａ）に示すように、扉２が、ヒンジ装置３を介して筐体１に開閉可能に連結されている。図９（ｂ）に示すように、扉２の回転軸Ｌ_２は、鉛直に対して僅かな角度αだけ傾けられている。閉状態の扉２は、正面（同図において左側）へ向けられるとともに、鉛直に対して角度αだけ上向きに傾けられている。傾斜角度αは、例えば、α＝５°程度である。このため、開状態（開き角度９０°未満）のときの扉２には、自重によって自然と閉じようとする自然回転トルクが作用する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
1 to 10 show a first embodiment of the present invention. As shown in FIG. 9, the gaming machine M such as a pachislot base has a housing 1 (first member), a door 2 (second member), and a hinge device 3. As shown in FIG. 9A, the door 2 is connected to the housing 1 through a hinge device 3 so as to be opened and closed. As shown in FIG. 9B, the rotation axis L2 of the door ₂ is inclined by a slight angle α with respect to the vertical. The closed door 2 is directed to the front (left side in the figure) and is tilted upward by an angle α with respect to the vertical. The inclination angle α is, for example, about α = 5 °. For this reason, the natural rotational torque which tries to close naturally by the dead weight acts on the door 2 at the time of an open state (opening angle is less than 90 degrees).

図９（ａ）に示すように、ヒンジ装置３は、扉２の幅方向の一端部の上下に離れて２つ（複数）設けられている。図１に示すように、各ヒンジ装置３は、第１ヒンジ本体１０と、第２ヒンジ本体２０と、リンク機構３０を備えている。第１ヒンジ本体１０は、ベース部材１１とマウント部材１２とを含む。図２（ｃ）に示すように、ベース部材１１は、筐体１にネジ止めにて固定されている。マウント部材１２は、ベース部材１１に着脱可能に装着されている。第２ヒンジ本体２０は、扉２にネジ止めにて固定されている。 As shown in FIG. 9 (a), two (a plurality) of hinge devices 3 are provided apart from each other at the top and bottom of one end portion in the width direction of the door 2. As shown in FIG. 1, each hinge device 3 includes a first hinge body 10, a second hinge body 20, and a link mechanism 30. The first hinge body 10 includes a base member 11 and a mount member 12. As shown in FIG. 2C, the base member 11 is fixed to the housing 1 with screws. The mount member 12 is detachably attached to the base member 11. The second hinge body 20 is fixed to the door 2 with screws.

図２に示すように、リンク機構３０は、４つ（複数）のリンク３１〜３４と、７つ（複数）の軸部材５１〜５７（回転軸）を含む。リンク機構３０によって、マウント部材１２と第２ヒンジ本体２０とが相対変位可能に連繋されている。リンク３１〜３４及びヒンジ本体１０，２０並びに軸部材５１〜５７によって、七節リンク機構が構成されている。 As shown in FIG. 2, the link mechanism 30 includes four (plural) links 31 to 34 and seven (plural) shaft members 51 to 57 (rotating shafts). By the link mechanism 30, the mount member 12 and the second hinge main body 20 are connected so as to be capable of relative displacement. The links 31 to 34, the hinge main bodies 10 and 20, and the shaft members 51 to 57 constitute a seven-bar linkage mechanism.

図３に示すように、各リンク３１〜３４は、鋼材等の金属によって概略断面コ字状に形成されている。図２（ａ）に示すように、第１リンク３１の第１端部３１ａは、第１軸部材５１を介してマウント部材１２に相対回転可能に連結されている。第１リンク３１の第２端部３１ｂと、第２リンク３２の第１端部３２ａとが、第２軸部材５２を介して互いに相対回転可能に連結されている。第２リンク３２の第２端部３２ｂは、第３軸部材５３を介して第２ヒンジ本体２０に相対回転可能に連結されている。
なお、第３軸部材５３の外周部には鋼製の筒状スペーサ５９が嵌められている。 As shown in FIG. 3, each of the links 31 to 34 is formed in a generally U-shaped cross section with a metal such as a steel material. As shown in FIG. 2A, the first end 31 a of the first link 31 is connected to the mount member 12 via the first shaft member 51 so as to be relatively rotatable. The second end 31 b of the first link 31 and the first end 32 a of the second link 32 are connected to each other via a second shaft member 52 so as to be relatively rotatable. The second end 32 b of the second link 32 is connected to the second hinge body 20 via the third shaft member 53 so as to be relatively rotatable.
A steel cylindrical spacer 59 is fitted on the outer periphery of the third shaft member 53.

第２リンク３２の中間部と、第３リンク３３の中間部とが、第４軸部材５４を介して相対回転可能に連結されている。第３リンク３３の第１端部３３ａは、第５軸部材５５を介してマウント部材１２に相対回転可能に連結されている。第３リンク３３の第２端部３３ｂと、第４リンク３４の第１端部３４ａとが、第６軸部材５６を介して互いに相対回転可能に連結されている。第４リンク３４の第２端部３４ｂは、第７軸部材５７を介して第２ヒンジ本体２０に相対回転可能に連結されている。軸部材５１〜５７の軸線は、互いに平行をなし、リンク３１〜３４の幅方向（図２において紙面と直交する方向）へ向けられている。 An intermediate portion of the second link 32 and an intermediate portion of the third link 33 are connected via a fourth shaft member 54 so as to be relatively rotatable. The first end 33 a of the third link 33 is coupled to the mount member 12 via the fifth shaft member 55 so as to be relatively rotatable. The second end 33 b of the third link 33 and the first end 34 a of the fourth link 34 are connected to each other via a sixth shaft member 56 so as to be relatively rotatable. The second end 34 b of the fourth link 34 is coupled to the second hinge body 20 via the seventh shaft member 57 so as to be relatively rotatable. The axes of the shaft members 51 to 57 are parallel to each other, and are directed in the width direction of the links 31 to 34 (a direction orthogonal to the paper surface in FIG. 2).

図３に示すように、第３リンク３３の両側面には、それぞれ板状の滑面スペーサ３５が設けられている。滑面スペーサ３５は、例えばポリアセタール等の樹脂にて構成されている。第２リンク３２と第３リンク３３との相対回転時には、第２リンク３２が滑面スペーサ３５と摺擦されることで滑りを良くしている。 As shown in FIG. 3, plate-like smooth spacers 35 are provided on both side surfaces of the third link 33. The smooth spacer 35 is made of a resin such as polyacetal. When the second link 32 and the third link 33 are rotated relative to each other, the second link 32 is rubbed against the smooth surface spacer 35 to improve the slip.

図２に示すように、ヒンジ装置３のリンク機構３０内に摩擦機構４０が組み込まれている。摩擦機構４０は、第１作動部材４１と、第２作動部材４２を含む。第１作動部材４１は、ヒンジ本体１０，２０及びリンク３１〜３４のうち１の部材に回転可能に連結されている。第２作動部材４２は、ヒンジ本体１０，２０及びリンク３１〜３４のうち他の１の部材に回転可能に連結されている。これら作動部材４１，４２どうしが、相対的に直線移動可能に係合されるとともに、後述する圧接手段４３によって互いに圧接されている。この摩擦機構４０によって、扉２に対する回転抵抗トルクが発現される。図１０に示すように、回転抵抗トルクは、扉２の回転可能範囲の少なくとも一部の自然回転阻止範囲において、扉２の自重による自然回転を阻止可能な大きさになる。 As shown in FIG. 2, a friction mechanism 40 is incorporated in the link mechanism 30 of the hinge device 3. The friction mechanism 40 includes a first operating member 41 and a second operating member 42. The first actuating member 41 is rotatably connected to one member of the hinge bodies 10 and 20 and the links 31 to 34. The second operating member 42 is rotatably connected to the other one of the hinge bodies 10 and 20 and the links 31 to 34. The operating members 41 and 42 are engaged with each other so as to be relatively linearly movable, and are pressed against each other by a pressing means 43 described later. By this friction mechanism 40, a rotational resistance torque with respect to the door 2 is expressed. As shown in FIG. 10, the rotation resistance torque has a magnitude that can prevent the natural rotation due to the weight of the door 2 in the natural rotation prevention range of at least a part of the rotatable range of the door 2.

詳しくは、図５に示すように、第１作動部材４１は、第１本体板４１ｘと、第１軸支部４１ａを一体に有している。図７（ａ）に示すように、第１本体板４１ｘの内側面（同図において上側を向く面）には、嵌合凹部４１ｄ及び嵌合凸部４１ｅが形成されている。図６に示すように、第１本体板４１ｘの幅方向（同図において左右）の両縁からそれぞれ係止壁４１ｆが直角に突設されている。図７に示すように、係止壁４１ｆの一部が切り欠かれることで、係止凹部４１ｉが形成されている。図６に示すように、一方の係止壁４１ｆと第１本体板４１ｘの内側面との間には、ガイド溝４１ｇが形成されている。ガイド溝４１ｇは、第１作動部材４１の長手方向（図６において紙面と直交する方向）に真っ直ぐ延びている。 Specifically, as shown in FIG. 5, the first operating member 41 integrally includes a first main body plate 41 x and a first shaft support portion 41 a. As shown in FIG. 7A, a fitting concave portion 41d and a fitting convex portion 41e are formed on the inner side surface (the surface facing the upper side in the drawing) of the first main body plate 41x. As shown in FIG. 6, locking walls 41 f are provided at right angles from both edges in the width direction (left and right in the figure) of the first main body plate 41 x. As shown in FIG. 7, a locking recess 41i is formed by cutting out a part of the locking wall 41f. As shown in FIG. 6, a guide groove 41g is formed between one locking wall 41f and the inner side surface of the first main body plate 41x. The guide groove 41g extends straight in the longitudinal direction of the first actuating member 41 (the direction orthogonal to the paper surface in FIG. 6).

図５に示すように、第１本体板４１ｘの長手方向の一端部（同図において左端部）の側部には、第１軸支部４１ａが設けられている。第１軸支部４１ａは、軸線を第１本体板４１ｘの幅方向（図５において紙面と直交する方向）に向けた概略筒形状に形成されている。また、第１本体板４１ｘの上記一端部には、連通孔４１ｈが形成されている。連通孔４１ｈは、第１軸支部４１ａの内部へ貫通している。 As shown in FIG. 5, a first shaft support portion 41a is provided on the side of one end portion (left end portion in the figure) in the longitudinal direction of the first main body plate 41x. The first shaft support portion 41a is formed in a substantially cylindrical shape whose axis is directed in the width direction of the first main body plate 41x (a direction orthogonal to the paper surface in FIG. 5). In addition, a communication hole 41h is formed in the one end portion of the first main body plate 41x. The communication hole 41h penetrates into the first shaft support portion 41a.

図２に示すように、第１軸支部４１ａに第５軸部材５５が挿通されている。これによって、第１作動部材４１が、第５軸部材５５を介して、第１ヒンジ本体１０（１の部材）と回転可能に連結されるとともに、第３リンク３３（１の部材）とも回転可能に連結されている。すなわち、第１作動部材４１は、ヒンジ本体１０，２０及びリンク３１〜３４のうち２つの部材１０，３３どうし間の回転軸と同軸まわりに上記２つの部材１０，３３に対して回転可能になっている。第５軸部材５５が、上記２つの部材１０，３３どうし間の回転軸と、第１作動部材４１の各部材１０，３３への連結軸とを兼ねている。 As shown in FIG. 2, the fifth shaft member 55 is inserted through the first shaft support portion 41a. Accordingly, the first actuating member 41 is rotatably connected to the first hinge body 10 (one member) via the fifth shaft member 55 and is also rotatable with the third link 33 (one member). It is connected to. In other words, the first actuating member 41 is rotatable with respect to the two members 10 and 33 about the rotation axis between the two members 10 and 33 of the hinge bodies 10 and 20 and the links 31 to 34. ing. The fifth shaft member 55 serves as a rotation shaft between the two members 10 and 33 and a connection shaft to the members 10 and 33 of the first operating member 41.

図７に示すように、第２作動部材４２は、第２本体板４２ｘと、第２軸支部４２ｂと、凸縁４２ｆとを一体に有している。第２本体板４２ｘは、直線状に延びる長い平板形状になっている。第２本体板４２ｘの幅方向の一側から直角に凸縁４２ｆが突設されている。図６に示すように、第２作動部材４２の断面形状は概略Ｌ字になっている。 As shown in FIG. 7, the second actuating member 42 integrally includes a second main body plate 42x, a second shaft support portion 42b, and a convex edge 42f. The second main body plate 42x has a long flat plate shape extending linearly. A convex edge 42f protrudes at a right angle from one side in the width direction of the second main body plate 42x. As shown in FIG. 6, the cross-sectional shape of the second actuating member 42 is substantially L-shaped.

図４に示すように、第２作動部材４２の長手方向における第１作動部材４１とは反対側（同図（ｂ）において右側）の端部に第２軸支部４２ｂが設けられている。第２軸支部４２ｂは、第２作動部材４２の幅方向（同図（ａ）において上下）の両側に一対設けられている。各第２軸支部４２ｂは、第２本体板４２ｘから直角に突設されている。凸縁４２ｆと同じ側（同図（ｂ）において紙面手前側）の第２軸支部４２ｂは、凸縁４２ｆと一体に連なっている。各第２軸支部４２ｂに軸穴４２ｃが形成されている。 As shown in FIG. 4, a second shaft support portion 42 b is provided at the end of the second operation member 42 in the longitudinal direction opposite to the first operation member 41 (on the right side in FIG. 4B). A pair of second shaft support portions 42b is provided on both sides in the width direction of the second operating member 42 (up and down in FIG. 4A). Each of the second shaft support portions 42b protrudes from the second main body plate 42x at a right angle. The second shaft support portion 42b on the same side as the convex edge 42f (the front side in the drawing in FIG. 5B) is integrally connected to the convex edge 42f. A shaft hole 42c is formed in each second shaft support portion 42b.

図２に示すように、軸穴４２ｃに連結軸部材５８が通されている。連結軸部材５８の軸線は、軸部材５１〜５７と平行に向けられている。この連結軸部材５８が、第４リンク３４の中間部に連結されている。ひいては、第２作動部材４２が、連結軸部材５８を介して、第４リンク３４（他の１の部材）と回転可能に連結されている。 As shown in FIG. 2, the connecting shaft member 58 is passed through the shaft hole 42c. The axis of the connecting shaft member 58 is directed parallel to the shaft members 51 to 57. The connecting shaft member 58 is connected to the intermediate portion of the fourth link 34. As a result, the 2nd operation member 42 is connected with the 4th link 34 (other 1 member) via the connecting shaft member 58 so that rotation is possible.

図５に示すように、第１作動部材４１の先端部（第２作動部材４２側の端部）に圧接手段４３が設けられている。圧接手段４３は、環状部材４４と、弾性部材４５と、一対の摩擦板４６，４７を有している。 As shown in FIG. 5, the pressure contact means 43 is provided at the distal end portion (the end portion on the second actuation member 42 side) of the first actuation member 41. The pressure contact means 43 includes an annular member 44, an elastic member 45, and a pair of friction plates 46 and 47.

図７に示すように、環状部材４４は、ステンレス鋼等の金属にて構成されている。環状部材４４の成形前の形状は、帯板状であり、この帯板状の環状部材４４が長手方向の４箇所でほぼ直角に折り曲げられることで、四角筒形状（環状）に成形されている。図８（ａ）に示すように、環状部材４４の長手方向（周方向）の両端部には、それぞれ逆三角形状ないしは逆さ台形状の嵌合部４４ｆが形成されている。嵌合部４４ｆは、環状部材４４の長手方向（周方向）へ突出するにしたがって幅広になるように幅方向へ張り出しており、これによって、張り出し部４４ｇが形成されている。逆に言うと、嵌合部４４ｆの基端部が幅方向に引っ込むことで、陥入部４４ｈが形成されている。図８（ｂ）に示すように、各嵌合部４４ｆの張り出し部４４ｇが他方の嵌合部４４ｆの陥入部４４ｈに嵌り込むようにして、環状部材４４の両端の嵌合部４４ｆ，４４ｆが互いに噛み合わさっている。環状部材４４の周方向（長手方向）に引張応力が作用すると、両端の嵌合部４４ｆ，４４ｆの張り出し部４４ｇ，４４ｇの斜面どうしが強く当たることで、嵌合部４４ｆ，４４ｆどうしが外れるのが阻止され、ひいては環状部材４４が環状（四角筒形状）に維持される。これによって、環状部材４４が、後述する締付力（圧接力）を担うことができる。 As shown in FIG. 7, the annular member 44 is made of a metal such as stainless steel. The shape of the annular member 44 before molding is a band plate shape, and the band plate-shaped annular member 44 is bent at substantially right angles at four positions in the longitudinal direction, thereby being formed into a rectangular tube shape (annular). . As shown in FIG. 8 (a), fitting portions 44f having an inverted triangular shape or an inverted trapezoidal shape are formed at both ends in the longitudinal direction (circumferential direction) of the annular member 44, respectively. The fitting portion 44f projects in the width direction so as to become wider as it protrudes in the longitudinal direction (circumferential direction) of the annular member 44, thereby forming a projecting portion 44g. In other words, the recess 44h is formed by retracting the base end of the fitting portion 44f in the width direction. As shown in FIG. 8B, the fitting portions 44f and 44f at both ends of the annular member 44 are engaged with each other so that the protruding portion 44g of each fitting portion 44f fits into the indented portion 44h of the other fitting portion 44f. I'm waiting. When a tensile stress acts in the circumferential direction (longitudinal direction) of the annular member 44, the fitting portions 44f and 44f are disengaged by the strong contact between the slopes of the protruding portions 44g and 44g of the fitting portions 44f and 44f at both ends. Is prevented, and as a result, the annular member 44 is maintained in an annular shape (square tube shape). Thereby, the annular member 44 can bear a tightening force (pressure contact force) described later.

図６に示すように、圧接手段４３における環状部材４４の内部には、弾性部材４５及び第１、第２摩擦板４６，４７が収容されている。弾性部材４５は、ポリアセタール等の樹脂にて構成され、波形断面の板形状になっている。これによって、弾性部材４５は、特に厚み方向（図６において上下）に弾性変形可能になっている。図７（ｂ）に示すように、弾性部材４５の下面には、嵌合凹部４５ｄと、嵌合凸部４５ｅが形成されている。弾性部材４５の幅方向の両端部には係止突起４５ｆが形成されている。詳細な図示は省略するが、係止突起４５ｆが、係止凹部４１ｉに嵌め込まれることで、弾性部材４５が第１作動部材４１に固定されている。 As shown in FIG. 6, the elastic member 45 and the first and second friction plates 46 and 47 are accommodated inside the annular member 44 in the press contact means 43. The elastic member 45 is made of a resin such as polyacetal and has a plate shape with a corrugated cross section. Thereby, the elastic member 45 can be elastically deformed particularly in the thickness direction (up and down in FIG. 6). As shown in FIG. 7B, a fitting recess 45 d and a fitting protrusion 45 e are formed on the lower surface of the elastic member 45. Locking protrusions 45 f are formed at both ends in the width direction of the elastic member 45. Although detailed illustration is omitted, the elastic member 45 is fixed to the first actuating member 41 by fitting the locking protrusion 45f into the locking recess 41i.

図６に示すように、環状部材４４が、第１本体板４１ｘ及び弾性部材４５の外周を囲んでいる。環状部材４４の裏側（図６において下側）の面板部４４ｂが、第１本体板４１ｘに宛がわれている。環状部材４４の表側（図６において上側）の面板部４４ａが、弾性部材４５に宛がわれている。 As shown in FIG. 6, the annular member 44 surrounds the outer periphery of the first main body plate 41 x and the elastic member 45. A face plate portion 44b on the back side (the lower side in FIG. 6) of the annular member 44 is assigned to the first main body plate 41x. A face plate portion 44 a on the front side (the upper side in FIG. 6) of the annular member 44 is addressed to the elastic member 45.

図７に示すように、第１摩擦板４６は、リン青銅等の金属にて構成され、四角形の平板状になっている。第１摩擦板４６には、嵌合穴部４６ｄと、嵌合凸部４６ｅが形成されている。嵌合穴部４６ｄは、第１摩擦板４６を厚み方向に貫通している。図７（ａ）に示すように、嵌合凸部４６ｅは、同図において上方（弾性部材４５側）へ突出されている。 As shown in FIG. 7, the first friction plate 46 is made of a metal such as phosphor bronze and has a rectangular flat plate shape. The first friction plate 46 is formed with a fitting hole 46d and a fitting convex portion 46e. The fitting hole 46d penetrates the first friction plate 46 in the thickness direction. As shown in FIG. 7A, the fitting convex portion 46e protrudes upward (to the elastic member 45 side) in FIG.

図５に示すように、この第１摩擦板４６が、弾性部材４５に宛がわれている。言い換えると、環状部材４４の表側面板部４４ａと第１摩擦板４６との間に弾性部材４５が介在されている。第１摩擦板４６の嵌合穴部４６ｄに弾性部材４５の嵌合凸部４５ｅが嵌め込まれている。図６に示すように、嵌合凸部４６ｅが嵌合凹部４５ｄに嵌め込まれている。これによって、第１摩擦板４６が弾性部材４５に固定されている。 As shown in FIG. 5, the first friction plate 46 is assigned to the elastic member 45. In other words, the elastic member 45 is interposed between the front side plate portion 44 a of the annular member 44 and the first friction plate 46. The fitting protrusion 45e of the elastic member 45 is fitted into the fitting hole 46d of the first friction plate 46. As shown in FIG. 6, the fitting convex portion 46e is fitted into the fitting concave portion 45d. Thus, the first friction plate 46 is fixed to the elastic member 45.

図７に示すように、第２摩擦板４７は、リン青銅等の金属にて構成され、四角形の平板状になっている。第２摩擦板４７には、嵌合穴部４７ｄと、嵌合凸部４７ｅが形成されている。嵌合穴部４７ｄは、第２摩擦板４７を厚み方向に貫通している。図７（ｂ）に示すように、嵌合凸部４７ｅは、同図において下方（第１本体板４１ｘ側）へ突出されている。 As shown in FIG. 7, the second friction plate 47 is made of a metal such as phosphor bronze and has a rectangular flat plate shape. The second friction plate 47 is formed with a fitting hole 47d and a fitting projection 47e. The fitting hole 47d penetrates the second friction plate 47 in the thickness direction. As shown in FIG. 7B, the fitting convex portion 47e protrudes downward (to the first main body plate 41x side) in the drawing.

図５に示すように、この第２摩擦板４７が、第１本体板４１ｘに宛がわれている。言い換えると、環状部材４４の裏側面板部４４ｂと第２摩擦板４６との間に第１本体板４１ｘが挟まれている。環状部材４４内において第１摩擦板４６と第２摩擦板４７とが平行に対峙している。図６に示すように、第２摩擦板４７の嵌合穴部４７ｄに第１作動部材４１の嵌合凸部４１ｅが嵌め込まれている。また、嵌合凸部４７ｅが嵌合凹部４１ｄに嵌め込まれている。これによって、第２摩擦板４７が第１作動部材４１に固定されている。 As shown in FIG. 5, the second friction plate 47 is assigned to the first main body plate 41x. In other words, the first main body plate 41 x is sandwiched between the back side surface plate portion 44 b of the annular member 44 and the second friction plate 46. In the annular member 44, the first friction plate 46 and the second friction plate 47 face each other in parallel. As shown in FIG. 6, the fitting convex portion 41 e of the first operating member 41 is fitted in the fitting hole portion 47 d of the second friction plate 47. Further, the fitting convex portion 47e is fitted into the fitting concave portion 41d. As a result, the second friction plate 47 is fixed to the first operating member 41.

環状部材４４の自然状態（無負荷時）における内周長は、環状部材４４内において一体をなす第１作動部材４１及び弾性部材４５の自然状態（無負荷時）における外周長（環状部材４４の内周面と接する部分の周長）よりも小さく設定されている。このため、環状部材４４に引張応力が作用することによって、第１作動部材４１及び弾性部材４５が互いの対向方向に接近するように付勢されている。更には、第１、第２摩擦板４６，４７どうしが互いに接近方向に付勢されている。 The inner circumferential length of the annular member 44 in the natural state (no load) is the outer circumferential length (the annular member 44 of the annular member 44) in the natural state (no load) of the first actuating member 41 and the elastic member 45 integrated in the annular member 44. It is set smaller than the peripheral length of the portion in contact with the inner peripheral surface. For this reason, when the tensile stress acts on the annular member 44, the first actuating member 41 and the elastic member 45 are urged so as to approach each other. Further, the first and second friction plates 46 and 47 are biased toward each other.

図５に示すように、摩擦機構４０の第１作動部材４１と第２作動部材４２とは、互いに長手方向を一致させて一直線上に配置されている。これら作動部材４１，４２の本体板４１ｘ，４２ｘどうしが、長手方向の同一位置において第２摩擦板４７を挟んで互いに重ねられている。かつ、第２本体板４２ｘが、第１摩擦板４６と第２摩擦板４７との間に圧入され、ひいては環状部材４４の内部に圧入されている。そして、第１摩擦板４６及び第２摩擦板４７が、第２本体板４２ｘの両面に圧接されている。したがって、本体板４１ｘ，４２ｘの上記重ねられた部分どうしが、第２摩擦板４７を挟んで互いに圧接されている。言い換えると、圧接手段４３が、作動部材４１，４２の上記重なった部分どうしを間接的に圧接している。
第２作動部材４２の凸縁４２ｆは、第１作動部材４１のガイド溝４１ｇに長手方向へスライド可能に嵌め込まれている。 As shown in FIG. 5, the first actuating member 41 and the second actuating member 42 of the friction mechanism 40 are arranged on a straight line with their longitudinal directions coinciding with each other. The body plates 41x and 42x of the operating members 41 and 42 are overlapped with each other with the second friction plate 47 interposed therebetween at the same position in the longitudinal direction. In addition, the second main body plate 42 x is press-fitted between the first friction plate 46 and the second friction plate 47, and as a result, is press-fitted into the annular member 44. The first friction plate 46 and the second friction plate 47 are pressed against both surfaces of the second main body plate 42x. Therefore, the overlapped portions of the main body plates 41x and 42x are pressed against each other with the second friction plate 47 interposed therebetween. In other words, the pressing means 43 indirectly presses the overlapping portions of the operating members 41 and 42.
The convex edge 42f of the second operating member 42 is fitted in the guide groove 41g of the first operating member 41 so as to be slidable in the longitudinal direction.

図２（ａ）〜（ｃ）に示すように、扉２を回転（開閉）させると、ヒンジ装置３の各リンク３１〜３４が互いに相対回転する。これによって、軸部材５１〜５８どうしの相対位置が変位し、更には摩擦機構４０の両端部４１ａ，４２ｂどうしの相対位置が変位する。この結果、摩擦機構４０が第５軸部材５５の周りに回転するとともに、第２作動部材４２が第１作動部材４１に対して長手方向に沿って相対的に直線移動する。これによって、摩擦機構４０が伸縮される。図２（ｃ）に示すように、扉２が閉状態のとき、摩擦機構４０は最も縮んでいる。図２（ａ）に示すように、扉２が全開状態のとき、摩擦機構４０は最も伸びている。したがって、扉２を開いていくとき、摩擦機構４０は伸長し、扉２を閉じていくとき、摩擦機構４０は収縮する。 As shown in FIGS. 2A to 2C, when the door 2 is rotated (opened / closed), the links 31 to 34 of the hinge device 3 rotate relative to each other. As a result, the relative positions of the shaft members 51 to 58 are displaced, and further, the relative positions of both end portions 41a and 42b of the friction mechanism 40 are displaced. As a result, the friction mechanism 40 rotates around the fifth shaft member 55 and the second operating member 42 linearly moves relative to the first operating member 41 along the longitudinal direction. As a result, the friction mechanism 40 is expanded and contracted. As shown in FIG. 2C, the friction mechanism 40 is most contracted when the door 2 is in the closed state. As shown to Fig.2 (a), when the door 2 is a full open state, the friction mechanism 40 is extended most. Therefore, the friction mechanism 40 expands when the door 2 is opened, and the friction mechanism 40 contracts when the door 2 is closed.

図１０に示すように、しかも、扉２の単位回転角度あたりの摩擦機構４０の伸縮量は、扉２の開き角度（回転角度）に応じて増減する。すなわち、第２ヒンジ本体２０が第１ヒンジ本体１０に対して単位回転角度だけ回転したときの、第２作動部材４２の第１作動部材４１に対する移動量（摩擦機構４０の伸縮量）は、扉２の回転可能範囲の両端部では相対的に小さく、回転可能範囲の中間部では相対的に大きい。具体的には、扉２を閉状態（開き角度０°）から開方向へ回転させていくにしたがって、単位回転角度あたりの摩擦機構４０の伸び量が漸次増大する。扉２の開き角度が回転可能範囲の中間部の例えば４０°〜５０°程度のとき、好適には４５°程度のとき、単位回転角度あたりの摩擦機構４０の伸び量が最大になる。この最大値を超えて扉２を更に開いていくと、単位回転角度あたりの摩擦機構４０の伸び量が漸次減少する。ヒンジ装置３内における摩擦機構４０の両端部４１ａ，４２ｂの位置を適切に設定することによって、上記のような伸縮特性を得ることができる。 As shown in FIG. 10, the expansion / contraction amount of the friction mechanism 40 per unit rotation angle of the door 2 increases or decreases according to the opening angle (rotation angle) of the door 2. That is, when the second hinge body 20 is rotated by a unit rotation angle with respect to the first hinge body 10, the amount of movement of the second operating member 42 relative to the first operating member 41 (the amount of expansion and contraction of the friction mechanism 40) is the door. 2 is relatively small at both ends of the rotatable range, and relatively large at an intermediate portion of the rotatable range. Specifically, as the door 2 is rotated in the opening direction from the closed state (opening angle 0 °), the amount of elongation of the friction mechanism 40 per unit rotation angle gradually increases. When the opening angle of the door 2 is, for example, about 40 ° to 50 ° in the middle of the rotatable range, preferably about 45 °, the amount of elongation of the friction mechanism 40 per unit rotation angle is maximized. When the door 2 is further opened exceeding this maximum value, the amount of elongation of the friction mechanism 40 per unit rotation angle gradually decreases. By appropriately setting the positions of both end portions 41a and 42b of the friction mechanism 40 in the hinge device 3, the above-described expansion / contraction characteristics can be obtained.

上記構造の遊技機Ｍにおいて、扉２の開閉に伴い、摩擦機構４０の第２作動部材４２が第１作動部材４１に対して直線移動しようとすると、環状部材４４内の摩擦板４６，４７と、第２作動部材４２との間に摩擦抵抗が生じる。ひいては、第１作動部材４１と第２作動部材４２との間に間接的に摩擦抵抗が生じる。また、第２本体板４２ｘの各箇所が摩擦板４６，４７どうし間に出し入れされることで、圧入抵抗が生じるようにすることもできる。これによって、摩擦機構４０による回転抵抗トルクを発現させることができる。
また、上述したように、扉２には、自重によって閉じ方向に自然回転トルクが作用している。
上記回転抵抗トルク及び自然回転トルクの合計を上回る回転トルクを扉２に開方向へ付与することによって、扉２を開くことができる。 In the gaming machine M having the above structure, when the second operating member 42 of the friction mechanism 40 tries to move linearly with respect to the first operating member 41 as the door 2 is opened and closed, the friction plates 46 and 47 in the annular member 44 A frictional resistance is generated between the second actuating member 42 and the second actuating member 42. As a result, a frictional resistance is indirectly generated between the first operating member 41 and the second operating member 42. Further, press-fitting resistance can be generated by inserting / removing each portion of the second main body plate 42x between the friction plates 46, 47. Thereby, the rotational resistance torque by the friction mechanism 40 can be expressed.
Further, as described above, the natural rotational torque acts on the door 2 in the closing direction by its own weight.
The door 2 can be opened by giving the door 2 a rotational torque exceeding the total of the rotational resistance torque and the natural rotational torque in the opening direction.

図１０に示すように、扉２の開き角度が小さいとき（例えば１０°〜２０°程度未満、好ましくは１８°程度未満）は、扉２の自重による自然回転トルクのほうが摩擦機構４０による回転抵抗トルクよりも大きい。したがって、扉２が自然と閉方向へ回転することで、しっかりと閉じることができる。 As shown in FIG. 10, when the opening angle of the door 2 is small (for example, less than about 10 ° to 20 °, preferably less than about 18 °), the natural rotational torque due to the weight of the door 2 is more rotational resistance due to the friction mechanism 40. Greater than torque. Therefore, the door 2 can be securely closed by naturally rotating in the closing direction.

扉２を、例えば１０°〜２０°程度以上、好ましくは１８°程度以上の半開き状態にすると、摩擦機構４０による回転抵抗トルクが、扉２の自重による自然回転トルクを上回ることで、自然回転阻止範囲に入る。これによって、扉２が自然と閉じるのを阻止でき、半開きの角度を保持することができる。この半開きの状態で遊技機Ｍの内部をメンテナンスすることができる。図２（ｂ）に示すように、好適には、扉２の開き角度を６０°程度とすることで、作業者が扉２の内側に入って遊技機Ｍの内部を確実にメンテナンスすることができる。また、扉２が遊技機Ｍの前方の通路を遮って通行の邪魔になるのを防止できる。
扉２を９０°以上開く必要はなく、扉２が隣の遊技機Ｍの利用者の邪魔になるのを回避することができる。 When the door 2 is in a half-opened state of, for example, about 10 ° to 20 ° or more, preferably about 18 ° or more, the rotation resistance torque by the friction mechanism 40 exceeds the natural rotation torque due to the dead weight of the door 2, thereby preventing natural rotation. Enter the range. As a result, the door 2 can be prevented from closing naturally, and a half-open angle can be maintained. The inside of the gaming machine M can be maintained in this half-open state. As shown in FIG. 2 (b), preferably, the opening angle of the door 2 is set to about 60 ° so that an operator can enter the inside of the door 2 and reliably maintain the inside of the gaming machine M. it can. Further, it is possible to prevent the door 2 from obstructing the passage by blocking the passage in front of the gaming machine M.
It is not necessary to open the door 2 by 90 ° or more, and the door 2 can be prevented from interfering with the user of the adjacent gaming machine M.

しかも、図１０に示すように、摩擦機構４０による回転抵抗トルクは、扉２の単位回転角度あたりの摩擦機構４０の伸縮量と相関しており、扉２の開き角度に応じて増減する。すなわち、回転抵抗トルクは、扉２を閉状態（開き角度０°）から開方向へ回転させていくにしたがって増大する。扉２の開き角度が回転可能範囲の中間部の例えば４０°〜５０°程度のとき、好適には４５°程度のとき、回転抵抗トルクが最大になる。この角度を超えて扉２を更に開いていくと、回転抵抗トルクが漸次減少する。 Moreover, as shown in FIG. 10, the rotational resistance torque by the friction mechanism 40 correlates with the amount of expansion / contraction of the friction mechanism 40 per unit rotation angle of the door 2, and increases or decreases according to the opening angle of the door 2. That is, the rotation resistance torque increases as the door 2 is rotated in the opening direction from the closed state (opening angle 0 °). When the opening angle of the door 2 is, for example, about 40 ° to 50 °, preferably about 45 °, in the middle of the rotatable range, the rotational resistance torque is maximized. When the door 2 is further opened beyond this angle, the rotational resistance torque gradually decreases.

したがって、扉２の開き角度が上記最大回転抵抗トルクでの角度（約４５°）超〜９０°未満の範囲では、扉２が自重で自然と閉まろうとすると、摩擦機構４０による回転抵抗トルクが増大する。これによって、扉２が閉まるのを確実に阻止することができる。この結果、扉２を好適な半開き角度（例えば６０°程度）に確実に保持することができ、この半開き角度で遊技機Ｍのメンテナンスを確実に行なうことができる。 Therefore, when the opening angle of the door 2 is in the range of more than the angle (about 45 °) at the maximum rotational resistance torque (less than about 45 °) to less than 90 °, the rotational resistance torque by the friction mechanism 40 increases when the door 2 tries to close naturally with its own weight. To do. This can reliably prevent the door 2 from closing. As a result, the door 2 can be reliably held at a suitable half-open angle (for example, about 60 °), and the gaming machine M can be reliably maintained at this half-open angle.

ヒンジ装置３によれば、第１、第２作動部材４１，４２どうしの圧接面積（直接には第２作動部材４２と摩擦板４６，４７との圧接面積）を大きくすることで、摩擦機構４０による回転抵抗トルクを十分に大きくすることができる。軸部材５５，５８の直径を太くする必要はない。したがって、ヒンジ装置３の大型化を回避できる。 According to the hinge device 3, the friction mechanism 40 is increased by increasing the pressure contact area between the first and second operating members 41 and 42 (directly, the pressure contact area between the second operating member 42 and the friction plates 46 and 47). The rotation resistance torque due to can be sufficiently increased. It is not necessary to increase the diameter of the shaft members 55 and 58. Therefore, the enlargement of the hinge device 3 can be avoided.

次に、本発明の他の実施形態を説明する。以下の実施形態において、既述の形態と重複する構成に関しては図面に同一符号を付して説明を省略する。
［第２実施形態］
摩擦機構４０は、種々のヒンジ装置に適用できる。
図１１〜図１３は、本発明の第２実施形態を示したものである。第２実施形態のヒンジ装置３Ｂは、４節リンク機構を構成している。詳しくは、図１２に示すように、ヒンジ装置３Ｂは、２つのヒンジ本体１０Ｂ，２０Ｂと、２つのリンク３６，３７を有している。第１ヒンジ本体１０Ｂが、筐体１に取り付けられている。第２ヒンジ本体２０Ｂが、扉２に取り付けられている。これらヒンジ本体１０Ｂ，２０Ｂが、リンク３６，３７からなるリンク機構３０を介して相対変位可能に連繋されている。 Next, another embodiment of the present invention will be described. In the following embodiments, the same reference numerals are given to the drawings for the same configurations as those already described, and the description thereof is omitted.
[Second Embodiment]
The friction mechanism 40 can be applied to various hinge devices.
11 to 13 show a second embodiment of the present invention. The hinge device 3B of the second embodiment forms a four-bar linkage mechanism. Specifically, as shown in FIG. 12, the hinge device 3B includes two hinge bodies 10B and 20B and two links 36 and 37. A first hinge body 10B is attached to the housing 1. A second hinge body 20 B is attached to the door 2. The hinge bodies 10B and 20B are connected to each other through a link mechanism 30 including links 36 and 37 so as to be capable of relative displacement.

図１２（ａ）に示すように、第１リンク３６の第１端部３６ａは、第１軸部材６１を介して第１ヒンジ本体１０Ｂに相対回転可能に連結されている。第１リンク３６の第２端部３６ｂは、第２軸部材６２を介して第２ヒンジ本体２０Ｂに相対回転可能に連結されている。第２リンク３７の第１端部３７ａは、第３軸部材６３を介して第１ヒンジ本体１０Ｂに相対回転可能に連結されている。第２リンク３７の第２端部３７ｂは、第４軸部材６４を介して第２ヒンジ本体２０Ｂに相対回転可能に連結されている。図１３に示すように、第２ヒンジ本体２０Ｂの内面と第２リンク３７との間には、ポリアセタール等の樹脂からなる板状の滑面スペーサ２５が設けられている。
軸部材６１〜６４の軸線は、互いに平行に向けられている。 As shown in FIG. 12A, the first end 36a of the first link 36 is connected to the first hinge body 10B via the first shaft member 61 so as to be relatively rotatable. The second end portion 36b of the first link 36 is connected to the second hinge body 20B via the second shaft member 62 so as to be relatively rotatable. The first end 37a of the second link 37 is coupled to the first hinge body 10B via the third shaft member 63 so as to be relatively rotatable. The second end portion 37b of the second link 37 is connected to the second hinge body 20B via the fourth shaft member 64 so as to be relatively rotatable. As shown in FIG. 13, a plate-like smooth spacer 25 made of a resin such as polyacetal is provided between the inner surface of the second hinge body 20 B and the second link 37.
The axis lines of the shaft members 61 to 64 are directed parallel to each other.

ヒンジ装置３Ｂの内部には摩擦機構４０Ｂが組み込まれている。摩擦機構４０Ｂは、第１作動部材４１と、第２作動部材４２を備えている。図１２（ａ）に示すように、第１作動部材４１の第１軸支部４１ａが、第１軸部材６１を介して第１リンク３６（１の部材）と回転可能に連結されるとともに、第１ヒンジ本体１０Ｂ（１の部材）とも回転可能に連結されている。言い換えると、第１作動部材４１は、ヒンジ本体１０Ｂ，２０Ｂ及びリンク３６，３７のうち２つの部材１０Ｂ，３６どうし間の回転軸と同軸まわりにこれら２つの部材１０Ｂ，３６に対して回転可能になっている。第１軸部材６１が、上記２つの部材１０Ｂ，３６どうし間の回転軸と、第１作動部材４１の各部材１０Ｂ，３６への連結軸とを兼ねている。 A friction mechanism 40B is incorporated in the hinge device 3B. The friction mechanism 40 B includes a first operating member 41 and a second operating member 42. As shown in FIG. 12A, the first shaft support portion 41a of the first actuating member 41 is rotatably connected to the first link 36 (one member) via the first shaft member 61, and the first One hinge body 10B (one member) is also rotatably connected. In other words, the first actuating member 41 is rotatable relative to the two members 10B and 36 about the axis of rotation between the two members 10B and 36 of the hinge bodies 10B and 20B and the links 36 and 37. It has become. The first shaft member 61 serves as a rotation shaft between the two members 10B and 36 and a connection shaft to the members 10B and 36 of the first operating member 41.

第２作動部材４２の第２軸支部４２ｂは、連結軸部材６８を介して第２リンク３７（他の１の部材）の中間部に回転可能に連結されている。連結軸部材６８の軸線は、軸部材６１〜６４と平行に向けられている。 The second shaft support portion 42 b of the second actuating member 42 is rotatably connected to an intermediate portion of the second link 37 (other one member) via a connecting shaft member 68. The axis of the connecting shaft member 68 is directed parallel to the shaft members 61 to 64.

摩擦機構４０Ｂの第１作動部材４１には、圧接手段４３Ｂが一体に設けられている。つまり、第１作動部材４１が圧接手段４３Ｂを兼ねている。詳しくは、第１作動部材４１の第１本体板４１ｘは、圧入孔４３ｃを有する四角筒形に形成されている。圧入孔４３ｃは、第１作動部材４１を長手方向に沿って真っ直ぐ貫通している。この圧入孔４３ｃに第２作動部材４２が圧入されている。これによって、第１作動部材４１と第２作動部材４２とが直接的に圧接されている。 The first operating member 41 of the friction mechanism 40B is integrally provided with a pressure contact means 43B. That is, the first operating member 41 also serves as the pressure contact means 43B. Specifically, the first main body plate 41x of the first operating member 41 is formed in a square cylinder shape having a press-fit hole 43c. The press-fit hole 43c passes straight through the first actuating member 41 along the longitudinal direction. The second operating member 42 is press-fitted into the press-fitting hole 43c. As a result, the first operating member 41 and the second operating member 42 are in direct pressure contact.

図１２（ａ）及び（ｂ）に示すように、ヒンジ装置３Ｂにおいても、扉２の開閉に伴って、第２作動部材４２が、上記圧入状態で第１作動部材４１に対して直線移動する。このとき、摩擦機構４０Ｂに回転抵抗トルクが作用する。これによって、第１実施形態のヒンジ装置３と同様に、扉２を自然回転阻止範囲内の所望の開き角度（例えば６０°前後）に維持することができる。 As shown in FIGS. 12A and 12B, also in the hinge device 3B, the second operating member 42 linearly moves with respect to the first operating member 41 in the press-fitted state as the door 2 is opened and closed. . At this time, rotational resistance torque acts on the friction mechanism 40B. Accordingly, similarly to the hinge device 3 of the first embodiment, the door 2 can be maintained at a desired opening angle (for example, around 60 °) within the natural rotation prevention range.

［第３実施形態］
図１４及び図１５は、本発明の第３実施形態を示したものである。第３実施形態のヒンジ装置３Ｃは、第１実施形態の七節リンク機構からなるヒンジ装置３の変形例であり、第１リンク３１が省略されている。第１ヒンジ本体１０Ｃと第２リンク３２とが、スライド軸３８を介して連繋されている。 [Third Embodiment]
14 and 15 show a third embodiment of the present invention. The hinge device 3C of the third embodiment is a modification of the hinge device 3 including the seven-bar linkage mechanism of the first embodiment, and the first link 31 is omitted. The first hinge body 10 C and the second link 32 are connected via a slide shaft 38.

詳しくは、図１４に示すように、第１ヒンジ本体１０Ｃには、ガイド孔１０ｄが形成されている。ガイド孔１０ｄは直線状に延びている。図１５に示すように、第２リンク３２の第１端部３２ａには、スライド軸３８が設けられている。スライド軸３８は、回転軸５３〜５８と平行になっている。このスライド軸３８が、ガイド孔１０ｄに通されている。スライド軸３８は、ガイド孔１０ｄの延び方向に沿って案内可能になっている。 Specifically, as shown in FIG. 14, a guide hole 10d is formed in the first hinge body 10C. The guide hole 10d extends linearly. As shown in FIG. 15, a slide shaft 38 is provided at the first end 32 a of the second link 32. The slide shaft 38 is parallel to the rotation shafts 53 to 58. The slide shaft 38 is passed through the guide hole 10d. The slide shaft 38 can be guided along the extending direction of the guide hole 10d.

ヒンジ装置３Ｃの摩擦機構４０の構造は、第１実施形態のヒンジ装置３と同様である。 The structure of the friction mechanism 40 of the hinge device 3C is the same as that of the hinge device 3 of the first embodiment.

ヒンジ装置３Ｃにおいては、扉２の開閉に伴って、ヒンジ本体１０Ｃ，２０及びリンク３２〜３４が互いに相対変位する。このとき、スライド軸３８がガイド孔１０ｄに沿ってスライドされる。
摩擦機構４０の回転抵抗トルクによって、扉２を自然回転阻止範囲内の所望の開き角度（例えば６０°前後）に保持できる点は、第１実施形態のヒンジ装置３と同様である。 In the hinge device 3 C, as the door 2 is opened and closed, the hinge bodies 10 C and 20 and the links 32 to 34 are relatively displaced from each other. At this time, the slide shaft 38 is slid along the guide hole 10d.
The point that the door 2 can be held at a desired opening angle (for example, around 60 °) within the natural rotation prevention range by the rotational resistance torque of the friction mechanism 40 is the same as the hinge device 3 of the first embodiment.

本発明は、上記の実施形態に限定されるものではなく、発明の趣旨に反しない限りにおいて種々の改変をなすことができる。
例えば、ヒンジ装置３内における、摩擦機構４０の両端部４１ａ，４２ｂの配置箇所は適宜設定することができる。すなわち、第１作動部材４１は、ヒンジ本体１０，２０及びリンク３１〜３４のうち何れか１の部材に連結され、第２作動部材４２は、ヒンジ本体１０，２０及びリンク３１〜３４のうち他の何れか１の部材に連結されていればよい。例えば、第１作動部材４１の第１軸支部４１ａを、回転軸５５以外の回転軸５１〜５４，５６，５７に連結してもよく、何れかのリンク３１〜３４の中間部に連結してもよい。第２作動部材４２の第２軸支部４２ｂを、第４リンク３４以外のリンク３１〜３３又はヒンジ本体１０，２０に連結してもよく、何れかの回転軸５１〜５７に連結してもよい。ヒンジ装置３Ｂ，３Ｃにおいても同様である。
圧接手段４３，４３Ｂが、第２作動部材４２に設けられていてもよい。第１作動部材４１が、第２作動部材４２に設けられた圧接手段４３に圧入されるようになっていてもよい。第１、第２作動部材４１，４２の両方に圧接手段４３，４３Ｂが設けられていてもよい。
圧接手段４３，４３Ｂが、作動部材４１，４２の何れか一方又は両方に一体に設けられた板バネ等で構成されていてもよい。 The present invention is not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the invention.
For example, the arrangement locations of the both end portions 41a and 42b of the friction mechanism 40 in the hinge device 3 can be set as appropriate. That is, the first operating member 41 is connected to any one of the hinge bodies 10 and 20 and the links 31 to 34, and the second operating member 42 is the other of the hinge bodies 10 and 20 and the links 31 to 34. What is necessary is just to be connected with any one member. For example, the first shaft support portion 41 a of the first operating member 41 may be connected to the rotation shafts 51 to 54, 56, 57 other than the rotation shaft 55, or connected to the intermediate portion of any one of the links 31 to 34. Also good. The second shaft support portion 42b of the second actuating member 42 may be connected to the links 31 to 33 or the hinge bodies 10 and 20 other than the fourth link 34, or may be connected to any one of the rotating shafts 51 to 57. . The same applies to the hinge devices 3B and 3C.
The pressure contact means 43, 43B may be provided on the second operating member. The first operating member 41 may be press-fitted into the press contact means 43 provided on the second operating member 42. Both the first and second actuating members 41 and 42 may be provided with pressure contact means 43 and 43B.
The press contact means 43, 43B may be configured by a leaf spring or the like integrally provided on one or both of the operating members 41, 42.

複数の実施形態の独自構成を互いに組み合わせてもよい。例えば、第１、第３実施形態のヒンジ装置３，３Ｃの圧接手段として、第２実施形態の圧接手段４３Ｂを適用してもよい。また、第２実施形態のヒンジ装置３Ｂの圧接手段として、第１実施形態の圧接手段４３を適用してもよい。 You may combine the original structure of several embodiment mutually. For example, the pressure contact means 43B of the second embodiment may be applied as the pressure contact means of the hinge devices 3 and 3C of the first and third embodiments. Moreover, you may apply the press-contact means 43 of 1st Embodiment as a press-contact means of the hinge apparatus 3B of 2nd Embodiment.

扉２の回転可能範囲の全域で第１作動部材４１と第２作動部材４２とが圧接している必要はない。扉２の回転可能範囲の一部（例えば中間部）でだけ、第１作動部材４１と第２作動部材４２とが圧接するようになっていてもよい。例えば、摩擦板４６，４７の厚みや第２本体板４２ｘの厚みを摩擦機構４０の長手方向の位置に応じて変化させることで、扉２の回転可能範囲の一部の領域でだけ第１作動部材４１と第２作動部材４２とが圧接し、他の領域では第１作動部材４１と第２作動部材４２とが圧接しないようにしてもよい。 It is not necessary for the first operating member 41 and the second operating member 42 to be in pressure contact with each other over the entire rotatable range of the door 2. The first actuating member 41 and the second actuating member 42 may be in pressure contact with each other only in a part (for example, an intermediate part) of the rotatable range of the door 2. For example, by changing the thickness of the friction plates 46 and 47 and the thickness of the second main body plate 42x according to the position in the longitudinal direction of the friction mechanism 40, the first operation is performed only in a part of the rotatable range of the door 2. The member 41 and the second actuating member 42 may be in pressure contact, and the first actuating member 41 and the second actuating member 42 may not be in pressure contact in other regions.

扉２は、必ずしも上向きに傾いていなくてもよく、鉛直になっていてもよい。
本発明は、パチンコ台等の遊技機Ｍに限られず、第１部材と、該第１部材に対して回転可能な第２部材を備えた各種装置のヒンジ装置に適用できる。第１部材は筐体に限られず、建物躯体等であってもよい。第２部材は、扉に限られず、蓋等であってもよい。 The door 2 does not necessarily have to be inclined upward and may be vertical.
The present invention is not limited to the gaming machine M such as a pachinko machine, but can be applied to a hinge device of various devices including a first member and a second member rotatable with respect to the first member. The first member is not limited to the housing, and may be a building frame or the like. The second member is not limited to a door, and may be a lid or the like.

本発明は、例えばパチンコ台等の遊技機の扉の開閉構造に適用可能である。 The present invention can be applied to a door opening / closing structure of a gaming machine such as a pachinko machine.

Ｌ_２回転軸
１筐体（第１部材）
２扉（第２部材）
３，３Ｂ，３Ｃヒンジ装置
１０，１０Ｂ，２０Ｃ第１ヒンジ本体
２０，２０Ｂ第２ヒンジ本体
３１〜３４リンク
３３第３リンク（１の部材）
３４第４リンク（他の１の部材）
３６，３７リンク
４０摩擦機構
４１第１作動部材
４２第２作動部材
４４環状部材
４５弾性部材
４６第１摩擦板（摩擦板）
４７第２摩擦板（摩擦板） L ₂ rotating shaft 1 housing (first member)
2 Door (second member)
3, 3B, 3C Hinge device 10, 10B, 20C First hinge body 20, 20B Second hinge body 31-34 Link 33 Third link (one member)
34 Fourth link (other one member)
36, 37 Link 40 Friction mechanism 41 First operating member 42 Second operating member 44 Annular member 45 Elastic member 46 First friction plate (friction plate)
47 Second friction plate (friction plate)

Claims

A hinge device for rotatably connecting the second member to the first member,
A first hinge body provided on the first member;
A second hinge body provided on the second member;
A plurality of links connecting the first hinge body and the second hinge body;
A friction mechanism that generates a frictional resistance capable of maintaining a rotation angle of the second hinge body in at least a part of a rotatable range of the second hinge body with respect to the first hinge body;
In the hinge device with
The friction mechanism is
A first actuating member rotatably connected to one member of the first and second hinge bodies and the plurality of links;
A second actuating member that is rotatably connected to another member of the first and second hinge bodies and the plurality of links, and is linearly movable with respect to the first actuating member;
The hinge apparatus characterized by including.

An annular member provided on the first actuating member;
The hinge device according to claim 1, wherein the second actuating member is disposed inside the annular member.

A friction plate provided inside the annular member;
The hinge device according to claim 2, wherein the friction plate is pressed against the second operating member.

The hinge device according to claim 3, wherein an elastic member is interposed between the annular member and the friction plate.

When the second hinge body rotates relative to the first hinge body by a unit rotation angle, the movement amount of the second actuation member relative to the first actuation member is relatively small at both ends of the rotatable range. The hinge device according to claim 1, wherein the hinge device is relatively large at an intermediate portion of the rotatable range.

The first actuating member or the second actuating member is rotatable with respect to the two members around the same axis as a rotation axis between two members of the first and second hinge bodies and the plurality of links. The hinge device according to claim 1, wherein the hinge device is a hinge device.

The rotation axis of the second member is inclined with respect to the vertical;
The rotation resistance torque caused by friction between the first and second actuating members exceeds the natural rotation torque caused by the weight of the second member in a part of the natural rotation prevention range of the rotatable range. Item 7. The hinge device according to any one of Items 1 to 6.