WO2024009808A1 - Dispositif charnière - Google Patents

Dispositif charnière Download PDF

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Publication number
WO2024009808A1
WO2024009808A1 PCT/JP2023/023313 JP2023023313W WO2024009808A1 WO 2024009808 A1 WO2024009808 A1 WO 2024009808A1 JP 2023023313 W JP2023023313 W JP 2023023313W WO 2024009808 A1 WO2024009808 A1 WO 2024009808A1
Authority
WO
WIPO (PCT)
Prior art keywords
hinge
lid
frictional resistance
shaft member
torque
Prior art date
Application number
PCT/JP2023/023313
Other languages
English (en)
Japanese (ja)
Inventor
裕一 幡野
Original Assignee
スガツネ工業株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by スガツネ工業株式会社 filed Critical スガツネ工業株式会社
Publication of WO2024009808A1 publication Critical patent/WO2024009808A1/fr

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    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D3/00—Hinges with pins
    • E05D3/02—Hinges with pins with one pin
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05D—HINGES OR SUSPENSION DEVICES FOR DOORS, WINDOWS OR WINGS
    • E05D7/00—Hinges or pivots of special construction
    • E05D7/08—Hinges or pivots of special construction for use in suspensions comprising two spigots placed at opposite edges of the wing, especially at the top and the bottom, e.g. trunnions
    • E05D7/082—Hinges or pivots of special construction for use in suspensions comprising two spigots placed at opposite edges of the wing, especially at the top and the bottom, e.g. trunnions the pivot axis of the wing being situated at a considerable distance from the edges of the wing, e.g. for balanced wings
    • E05D7/086—Braking devices structurally combined with hinges
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C11/00—Pivots; Pivotal connections
    • F16C11/04—Pivotal connections
    • F16C11/10—Arrangements for locking

Definitions

  • the present invention relates to a hinge device equipped with a frictional resistance generating mechanism and a one-way clutch.
  • Patent Document 1 Utility Model Registration No. 31522478 discloses a hinge device that rotatably supports a piano lid (second object) on a piano body (first object).
  • This hinge device includes a first hinge body fixed to the piano body, a second hinge body fixed to the lid, and a shaft member rotatably connecting the first hinge body and the second hinge body. There is.
  • the hinge device of Patent Document 1 further includes a frictional resistance generating mechanism and a one-way clutch. Briefly, both ends of the shaft member are rotatably supported by one of the first hinge body and the second hinge body via a one-way clutch. A frictional resistance generating mechanism is provided between the intermediate portion of the shaft member and the other hinge body.
  • the one-way clutch When opening the lid, the one-way clutch releases the engagement between the shaft member and the one hinge body.
  • the two hinge bodies can rotate without receiving frictional resistance from the frictional resistance generating mechanism, and the operator can open the lid to a predetermined angle using only an operating force that overcomes the weight of the lid.
  • the one-way clutch engages the shaft member and the one hinge body. Thereby, the shaft member rotates relative to the other hinge body. As a result, frictional resistance is generated, the rotational speed of the lid is suppressed, and an impact when the lid is closed can be avoided.
  • the hinge device disclosed in Patent Document 2 also includes a frictional resistance generating mechanism and a one-way clutch.
  • the frictional resistance generating mechanism allows the second object, to which the second hinge body is fixed, to stand still at any angular position relative to the first object, to which the first hinge body is fixed.
  • the hinge device of the present invention was made to solve the above problem, and includes a first hinge body to be fixed to a first object, a second hinge body to be fixed to a second object, and at least one a rotational coupling mechanism that has two shaft members and connects the first hinge main body and the second hinge main body in a relatively rotatable manner; one of the first and second hinge main bodies and the shaft member; a one-way clutch disposed between the two hinge bodies, and a frictional resistance generation mechanism that generates frictional resistance when the other one of the first and second hinge bodies and the shaft member rotate relative to each other, Torque in a first direction toward a first rotation limit position is applied to the second hinge body, The one-way clutch brings the one hinge body and the shaft member into an engaged state capable of transmitting torque when the second hinge body rotates in the first direction, and the second hinge body rotates in the first rotation limit.
  • the one hinge body and the shaft member When rotating in a second direction away from the position, the one hinge body and the shaft member are configured to be in a disengaged state in which torque cannot be transmitted; When the second hinge body rotates in the first direction, the torque overcomes the frictional resistance at least in a first angular range between the first rotation limit position and a predetermined angular position.
  • a damper mechanism is provided, and the damper mechanism has a damping effect on the second hinge body in at least a part of the first angular range when the second hinge body rotates in the first direction. It is characterized by exhibiting
  • the torque is a dead weight torque caused by the dead weight of the second object, and when the second hinge main body is at the first rotation limit position, the second object is horizontal or tilted from the horizontal. .
  • the angular position of the second hinge main body when the second object stands up and the self-weight torque becomes zero is set as a reference angular position, there is a difference between this reference angular position and the predetermined angular position.
  • the frictional resistance holds the second object stationary against the self-weight torque.
  • the second hinge body is rotatable in a third angular range from the reference angular position to a second rotation limit position opposite to the first rotation limit position, and the damper mechanism
  • the damper effect is also exhibited when the hinge body rotates in the second direction within the third angle range. Frictional resistance does not work when the second hinge body rotates toward the second rotation limit position, but the damper effect of the damper mechanism avoids the impact when the second hinge body reaches the second rotation limit position. can do.
  • the frictional resistance generating mechanism includes an adjustment mechanism for adjusting the frictional resistance.
  • the frictional resistance generating mechanism includes an adjustment mechanism for adjusting the frictional resistance.
  • the frictional resistance generating mechanism further includes a tightening member having a gripping portion having a C-shaped cross section surrounding the outer periphery of the shaft member, and a pair of tightening pieces protruding radially outward from the gripping portion; a friction member disposed between the gripping portion of the tightening member and the outer periphery of the shaft member, and the adjustment mechanism tightens the pair of tightening pieces in a direction in which they are screwed together and are brought closer to each other. It has a female screw portion and an adjustment screw that generate frictional resistance between the friction member and the shaft member.
  • FIG. 3 is a side view of the hinge device, showing a state in which the lid is closed (opening angle is 0°). It is a perspective view of a hinge device. 3 is a sectional view taken along the line III-III in FIG. 2. FIG. FIG. 3 is an exploded perspective view of the hinge device. FIG. 3 is a plan cross-sectional view of the hinge device when the lid is at an opening angle of 120°.
  • FIG. 5A is a side sectional view taken along the line BB in FIG. 5A.
  • FIG. 3 is a plan cross-sectional view of the hinge device when the lid is at an opening angle of 80°.
  • FIG. 3 is a side sectional view of the hinge device when the lid is at an opening angle of 80°.
  • FIG. 3 is a plan cross-sectional view of the hinge device when the lid is at an opening angle of 60°.
  • FIG. 6 is a side sectional view of the hinge device when the lid is at an opening angle of 60°.
  • FIG. 3 is a plan cross-sectional view of the hinge device when the lid is in the closed position (opening angle 0°).
  • FIG. 3 is a side sectional view of the hinge device when the lid is in the closed position.
  • a storage box 1 that accommodates, for example, medical test materials, etc., includes a housing 2 (first object) and a lid 3 (second object) that opens and closes an upper end opening 2x of the housing 2. object) and a plurality of hinge devices 5 that rotatably support the lid 3.
  • a housing 2 first object
  • a lid 3 second object
  • a plurality of hinge devices 5 that rotatably support the lid 3.
  • the lid 3 is rotatable between a fully open position (opening angle 120°) in FIG. 1A and a closed position (opening angle 0°) in FIG. 1B.
  • the lid 3 is relatively heavy in order to seal the opening 2x, and a torque due to its own weight (dead weight torque) acts on the lid 3.
  • This self-weight torque is zero when the center of gravity of the lid 3 is in the upright position located directly above the rotation center L (described later) (in this embodiment, the opening angle is (90+ ⁇ ) degrees close to 90 degrees), and this torque is zero. It increases as the inclination of the lid 3 increases from the upright position (that is, as the opening angle decreases), and reaches a maximum at the closed position (opening angle 0°) where the lid 3 is horizontal.
  • the hinge device 5 includes a first hinge body 6 fixed to the upper surface of the support wall 2y at the side edge of the opening 2x of the housing 2, and the upper surface of the lid 3 (the lid 3 in the closed state).
  • the second hinge body 7 is fixed to the upper surface of the second hinge body 7, and a single shaft member 8 (rotation connection mechanism) rotatably connects the hinge bodies 6 and 7.
  • the axis of the shaft member 8 is provided as a rotation axis L.
  • the first hinge main body 6 includes two hinge members 10A and 10B arranged along the rotation axis L direction (hereinafter simply referred to as the axial direction) and a cover 10C. ing.
  • the hinge members 10A and 10B have, as a common configuration, a fixed part 11 and a guide part 12 in order from the outer end in the axial direction toward the inner side, and a fixed part 11 and a guide part 12 are arranged next to the fixed part 11 (in a direction perpendicular to the rotational axis L). ) has a bearing portion 13 (adjacent to).
  • the horizontal direction perpendicular to the rotational axis L will be referred to as the T direction (see FIGS. 2 to 5).
  • Bearing holes 13a that support both ends of the shaft member 8 are formed in the bearing portions 13 of the hinge members 10A, 10B so as to face each other.
  • the guide portion 12 is for guiding a cam follower 52, which will be described later, and has a pair of upright walls 12a facing each other in the T direction.
  • One hinge member 10A has a pair of connecting portions 14 formed axially inwardly than the guide portion 12 and spaced apart in the T direction.
  • the other hinge member 10B also has a pair of connecting portions 15 formed inside the guide portion 12 in the axial direction. These connecting parts 14 and 15 are shifted in position in the vertical direction, and are overlapped with each other as shown in FIG. 3.
  • the connecting portions 14 and 15 of the hinge members 10A and 10B are connected to the center portion of the cover 10C by screwing screws 16a passing through the connecting portions 14 and 15 into screw holes 19a formed on the lower surface of the cover 10C.
  • a pair of semi-cylindrical guide surfaces 17 are formed between a pair of connecting portions 14.
  • a pair of semi-cylindrical guide surfaces 18 are also formed on the lower surface of the cover 10C, and are vertically opposed to the guide surfaces 17. These guide surfaces 17 and 18 are in contact with a lower half and an upper half of a cylinder 51a of a pair of linear dampers 51, which will be described later, respectively, and support the cylinder 51a so as to be slidable in the axial direction.
  • Both ends of the cover 10C are connected over the hinge members 10A, 10B by screws 16b (FIG. 4) passing through the corners of the fixing portions 11 of the hinge members 10A, 10B.
  • Fixing holes 19b are formed in the fixing parts 11 of the hinge members 10A and 10B, and fixing holes 19c are also formed in the cover 10C, and screws (not shown) passing through these fixing holes 19b and 19c are screwed into the support wall 2y.
  • the first hinge main body 6 is fixed to the support wall 2y.
  • the second hinge main body 7 includes an axially elongated hinge block 20A and a cover 20B.
  • the cover 20B is fitted onto the lower surface of the hinge block 20A and fixed with screws 21.
  • the hinge block 20A has a fixed part 22 and a bearing part 23 on the side thereof (adjacent in the T direction).
  • Fixing holes 24 are formed at both ends in the longitudinal direction of the fixing portion 22, and an adjustment hole 25 is formed in the center, which functions as will be described later.
  • the second hinge main body 7 is fixed to the lid 3 by screwing a screw passing through the fixing hole 24 of the hinge block 20A into the upper surface of the side edge of the lid 3.
  • the bearing portion 23 has a cylindrical shape, and both ends in the longitudinal direction are provided as bearing holes 23a.
  • a housing space 26 is formed in the intermediate portion of the bearing portion 23.
  • the housing space 26 has an inner diameter larger than the bearing hole 23a and is open at the bottom. As shown in FIG. 3, the lower part of this accommodation space 26 is covered with a cover 20B.
  • the intermediate portion of the shaft member 8 is inserted into the pair of bearing holes 23a of the hinge block 20A of the second hinge main body 7 via the bush 35, and both ends thereof are inserted into the one-way clutch 30. are inserted into the pair of bearing holes 13a of the first hinge main body 6 through the openings, thereby rotatably connecting the first hinge main body 6 and the second hinge main body 7.
  • the one-way clutch 30 has a well-known structure, and when the shaft member 8 is about to rotate in one direction with respect to the bearing part 13, the engagement (meshing) between the shaft member 8 and the bearing part 13 is released, and the shaft member 8 The relative rotation of the bearing portion 13 is allowed. When the shaft member 8 is about to rotate in the other direction, the shaft member 8 and the bearing portion 13 are engaged, and relative rotation between the two is prohibited.
  • a frictional resistance generating mechanism 40 is arranged in the accommodation space 26 of the second hinge main body 7. As shown in FIGS. The frictional resistance generating mechanism 40 includes a tightening member 41, a pair of holders 42, a pair of friction members 43, and a nut 44 (female threaded portion) and an adjusting screw 45 as an adjusting mechanism.
  • the tightening member 41 includes a gripping portion 41a having a cylindrical shape with a C-shaped cross section, and a pair of tightening pieces 41b protruding radially outward from a pair of side edges of the gripping portion 41a.
  • the pair of friction members 43 have an arcuate cross section, are in contact with the outer periphery of the central portion of the shaft member 8, and are gripped by the gripping portion 41a of the tightening member 41 through a holder 42 having an arcuate cross section so as not to rotate relative to each other. There is.
  • a pair of tightening pieces 41b of the tightening member 41 are held between the wall surface of the housing space 26 and the nut 44.
  • a notch 41c (insertion part) is formed in the pair of tightening pieces 41b, and the adjustment screw 45 is screwed into the nut 44 from the adjustment hole 25 of the second hinge body 7 through the notch 41c of the tightening piece 41b. has been done.
  • the adjustment screw 45 is screwed into the nut 44, the distance between the pair of tightening pieces 41b narrows, and the friction member 43 comes into strong contact with the outer periphery of the shaft member 8 via the grip portion 41a, thereby generating frictional resistance.
  • the frictional resistance can be adjusted.
  • the nut 44 has a non-circular outer periphery, and is prevented from rotating by fitting the nut 44 into the non-circular support recess 46 of the cover 20B.
  • the hinge device 5 further includes a damper mechanism 50.
  • This damper mechanism 50 includes a pair (plurality) of linear dampers 51 arranged parallel to the rotation axis L, a pair of cam followers 52 arranged on both sides of the linear dampers 51 in the axial direction, and further arranged outside in the axial direction. It includes a pair of cam members 53 and a pair of link arms 54 (cooperation mechanism) connected to these cam members 53, respectively.
  • the hydraulic linear damper 51 is well known and includes a cylinder 51a containing a liquid, a piston (not shown) within the cylinder 51a, and a rod 51b having one end fixed to the piston and protruding from the cylinder 51a.
  • a damper effect is exerted due to the flow resistance of the fluid passing through the orifice inside the cylinder.
  • the cylinder 51a of the linear damper 51 is supported slidably in the axial direction in the first hinge body 10 between the guide surface 17 of the hinge member 10A and the guide surface 18 of the cover 10C.
  • the rods 51b of the pair of linear dampers 51 protrude in opposite directions.
  • the pair of cam followers 52 are also supported by the guide 12 so as to be able to slide in the axial direction, and as will be described later, can approach or move away from each other in the axial direction.
  • a roller 56 is rotatably supported on the axially outer side of the cam follower 52 via a pin 55 .
  • Each of the pair of cam members 53 is supported between the fixed portion 11 of the hinge members 10A, 10B of the first hinge main body 6 and the guide 12 so as to be slidable in the T direction.
  • a cam surface 57 extending in the T direction is formed on the cam member 53, and the roller 56 of the cam follower 52 is in contact with this cam surface 57.
  • the cam surfaces 57 of the pair of cam members 53 face each other in the axial direction and have a symmetrical shape, with a flat non-operating area 57a extending parallel to the T direction (that is, the sliding direction) and an inclined operating area 57a on both sides of the T direction. It has regions 57b and 57c.
  • the first operating region 57b closer to the rotation axis L is inclined axially inward as it approaches the rotation axis L.
  • the second operating region 57c that is further away from the rotation axis L is inclined toward the inner side in the axial direction as it moves away from the rotation axis L.
  • the pair of link arms 54 extend in the T direction, and one end of each is rotatably connected to the end of the pair of cam members 53 near the rotational axis L via a pin 58, and the other end of each 2 is inserted into grooves 23b formed at both axial ends of the bearing section 23 of the hinge main body 7, and is rotatably connected to both ends of the bearing section 23 via a pin 59.
  • the operation of the hinge device 5 having the above-described configuration will be explained.
  • the position of the second hinge body 7 corresponding to the closed position (opening angle 0°) of the lid 3 shown in FIG. 1B is defined as the first rotation limit position P1
  • the fully open position (opening angle 120°) of the lid 3 shown in FIG. ) is defined as the second rotation limit position P2.
  • the first rotation limit position P1 of the second hinge body 7 the lid 3 hits the upper end of the housing 2
  • the second rotation limit position P2 the second hinge body 7 hits the cover 10C of the first hinge body 6 (Fig. (See 5B).
  • the position of the second hinge body 7 corresponding to the upright position of the lid 3 (opening angle (90+ ⁇ )°) where the self-weight torque becomes zero is defined as the reference angular position Pr. do.
  • the position of the second hinge main body 7 corresponding to the opening angle of the lid 3 of 30 degrees is defined as a predetermined angular position Px.
  • the angular range of the second hinge body 7 corresponding to the opening angle of the lid 3 from 0° to 30° is defined as a first angular range ⁇ 1
  • the second angular range corresponding to the opening angle of the lid 3 from 30° to (90+ ⁇ )° is defined as a first angular range ⁇ 1.
  • the angular range of the hinge body 7 is defined as a second angular range ⁇ 2, and the angular range of the second hinge body 7 corresponding to the opening angle of the lid 3 (90+ ⁇ )° to 120° is defined as a third angular range ⁇ 3.
  • the lid 3 At the fully open position, the lid 3 is tilted in the opening direction from the upright position where the dead weight torque is zero, and the dead weight torque is acting in the opening direction. Therefore, the operator turns the lid 3 to the upright position using an operating force that overcomes the weight torque and frictional resistance.
  • the dead weight torque is switched to the closing direction.
  • the angular range from the standing position to the opening angle of 30° second angular range ⁇ 2
  • the dead weight torque is relatively small and does not exceed the frictional resistance. Therefore, even if the operator releases his/her hand from the lid 3 within this angle range, the lid 3 can remain stationary at that angle.
  • the operator needs to apply an operating force in the closing direction to the lid 3 against frictional resistance.
  • the dead weight torque increases as the opening angle of the lid 3 decreases and approaches the horizontal position.
  • the dead weight torque overcomes the frictional resistance when the opening angle of the lid 3 becomes smaller than 30°. Therefore, when the operator releases his hand from the lid 3, the lid 3 is automatically closed.
  • this angular range from 30° to 0° first angular range ⁇ 1
  • the rotational speed of the lid 3 is suppressed because the dead weight torque is weakened by frictional resistance.
  • the dead weight torque increases as the opening angle of the lid 3 approaches 0°, when the weight of the lid 3 is large, braking due to frictional resistance becomes insufficient.
  • a damper effect is added by the damper mechanism 50, the rotational speed of the lid 3 in the closing direction can be sufficiently suppressed, and an impact when the lid 3 is closed can be avoided.
  • the roller 56 moves in the first operating area 71b of the cam surface 57 until the opening angle of the lid 3 reaches from 60° to 0°, so the damper is activated within this angle range. It can be effective.
  • the damper effect preferably works in an angular range that includes the first angular range ⁇ 1 from 30° to 0°, but it may work in a narrower angular range within the first angular range ⁇ 1.
  • the damper mechanism 50 presses the linear damper 51 with the slidable cam member 53, the pressing stroke can be increased, and thereby a large damping effect can be exhibited.
  • the cylinder 51a of the linear damper 51 is not fixed and is movable in the axial direction, and the tip of the rod 51b and the base end of the cylinder 51a abut against a pair of cam followers 52 by an internal return spring. Therefore, compared to a structure in which the cylinder is fixed and the rod tip hits a single cam follower, the stroke can be doubled and a greater damping effect can be achieved. In this embodiment, by further providing a pair (plurality) of linear dampers, the damper effect can be further increased.
  • the damper mechanism 50 When the lid 3 is in the closed position and already stationary, the damper mechanism 50 does not function and the self-weight torque that is greater than the frictional resistance is always acting in the closing direction, so the lid 3 reliably closes the opening 2x of the housing 2. can be closed, and the inconvenience of opening the mouth does not occur.
  • the one-way clutch 30 disengages the shaft member 8 and the bearing portion 13, so that no frictional resistance acts.
  • the operator can open the lid 3 with just enough force to resist its own weight torque.
  • the dead weight torque gradually decreases as the lid 3 moves toward the upright position.
  • the damper effect of the damper mechanism 50 suppresses the rotational speed of the lid 3 in the opening direction, and the lid 3 returns to the fully open position. You can avoid the shock when reaching.
  • the inclination of the lid 3 is smaller than in the first angular range ⁇ 1, and the dead weight torque is smaller, so the rotational speed of the lid 3 can be sufficiently suppressed by the damper effect alone even without frictional resistance.
  • the rollers 56 of the pair of cam followers 52 are in the non-operating area 57a of the cam surface 57 of the pair of cam members 53, and the linear damper 51 has a maximum length. have.
  • the link arm 54 and the cam member 53 move to the right (towards the rotation axis L) as the second hinge main body 7 rotates.
  • the rollers 56 of the pair of cam followers 52 ride on the second operating area 57c of the cam surface 57 of the pair of cam members 53.
  • the pair of cam followers 52 move toward each other and contract the pair of linear dampers 51, so that the linear dampers 51 can exert a damping effect.
  • the roller 56 moves in the second operating area 57c of the cam surface 57 until the opening angle of the lid 3 ranges from 80° to 120°, so the damper is activated within this angle range. It can be effective.
  • the damper effect preferably works in an angular range including the third angular range ⁇ 3 from (90+ ⁇ )° to 120°, but it may work in a narrower angular range within the third angular range ⁇ 3.
  • the first angular range ⁇ 1 and the second angular range ⁇ 2 can be adjusted by adjusting the frictional resistance of the frictional resistance generating mechanism 40 with the adjustment screw 45. That is, when the adjusting screw 45 is loosened, the frictional resistance is reduced, so the first angular range ⁇ 1 becomes wider and the second angular range ⁇ 2 becomes narrower. On the contrary, when the adjustment screw 45 is tightened, the frictional resistance increases, so the first angular range ⁇ 1 becomes narrower and the second angular range ⁇ 2 becomes wider.
  • the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the gist thereof.
  • the second object is kept stationary within the second angle range, but some rotation may be allowed.
  • the second hinge body when the lid 2 is in a horizontal position, the second hinge body is at the first rotation limit position, but when the lid is tilted from the horizontal position (for example, at a tilted position of 30 degrees or less), the second hinge body is in the first rotation limit position.
  • the main body may be in the first rotation limit position.
  • the first hinge body may be provided with a frictional resistance generating mechanism, and the second hinge body may be provided with a one-way torque.
  • the damper mechanism may use a cooperation mechanism consisting of a plurality of members instead of the link arm.
  • a link arm, a cam member, and a cam follower are each provided, and when a plurality of linear dampers are provided, the cylinders of these linear dampers are installed in fixed positions, and all rods are directed toward a single cam follower. If one link arm, one cam member, and one linear damper are provided, the cam follower may be omitted. In this case, the tip of the rod of the linear damper directly hits the cam surface of the cam member.
  • the damper mechanism may include a linear damper provided on one hinge body and extending in a direction perpendicular to the shaft member, and a cam portion provided on the other hinge body and pressing the linear damper.
  • the rotation coupling mechanism may be configured by a link mechanism having a plurality of shaft members and a plurality of links.
  • the elasticity of the spring may be used to apply torque to the second hinge body. This torque application method is employed when the hinge device is arranged so that the second object rotates about an axis perpendicular to the first object.
  • a frictional resistance generating mechanism having a mechanism for adjusting frictional resistance is used, but a simply configured frictional resistance generating mechanism without an adjusting mechanism may be used.
  • a metal shaft member may be press-fitted into a resin bearing part, and friction may be generated between the outer peripheral surface of the shaft member and the inner peripheral surface of the bearing part.
  • a friction member may be interposed between the outer peripheral surface of the shaft member and the inner peripheral surface of the bearing part.
  • the present invention can be applied to a hinge device equipped with a frictional resistance generating mechanism and a one-way clutch.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Pivots And Pivotal Connections (AREA)
  • Closing And Opening Devices For Wings, And Checks For Wings (AREA)

Abstract

L'invention concerne un dispositif charnière qui peut éviter un choc lorsqu'un couvercle est fermé. Ce dispositif charnière (5) comprend un premier corps de charnière (6) qui est fixé à un boîtier (2) (premier objet), un second corps de charnière (7) qui est fixé à un couvercle (3) (second objet), et un élément d'arbre (8) qui relie les deux corps de charnière (6, 7). Le dispositif de charnière (5) comprend en outre un embrayage unidirectionnel (30), un mécanisme de génération de résistance de frottement (40), et un mécanisme d'amortissement (50). L'embrayage unidirectionnel (30) ne génère pas de résistance au frottement lorsque le couvercle (3) est ouvert, et génère une résistance au frottement uniquement lorsque le couvercle (3) est fermé. Le couvercle (3) est ancré à une position discrétionnaire d'une position verticale à un angle prescrit par la résistance au frottement. Le couple produit par le poids du couvercle (3) surmonte la résistance au frottement dans une plage angulaire proche d'une position fermée, et le couvercle (3) tourne dans une direction de fermeture. Lorsque cela se produit, un effet d'amortisseur du mécanisme d'amortissement fonctionne en plus de la résistance au frottement, ce qui permet d'éviter un choc lorsque le couvercle (3) est supprimé de la rotation et est fermé.
PCT/JP2023/023313 2022-07-07 2023-06-23 Dispositif charnière WO2024009808A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2022109469 2022-07-07
JP2022-109469 2022-07-07

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WO2024009808A1 true WO2024009808A1 (fr) 2024-01-11

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PCT/JP2023/023313 WO2024009808A1 (fr) 2022-07-07 2023-06-23 Dispositif charnière

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TW (1) TW202413783A (fr)
WO (1) WO2024009808A1 (fr)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000356065A (ja) * 1999-06-17 2000-12-26 Iris Co Ltd ロータリーダンパ
JP3152248U (ja) * 2009-05-13 2009-07-23 株式会社三渡工業所 片方向制動ヒンジ
US20120174339A1 (en) * 2011-01-01 2012-07-12 South, Inc. Detent hinge
WO2022030173A1 (fr) * 2020-08-06 2022-02-10 スガツネ工業株式会社 Charnière d'amortissement unidirectionnelle

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2000356065A (ja) * 1999-06-17 2000-12-26 Iris Co Ltd ロータリーダンパ
JP3152248U (ja) * 2009-05-13 2009-07-23 株式会社三渡工業所 片方向制動ヒンジ
US20120174339A1 (en) * 2011-01-01 2012-07-12 South, Inc. Detent hinge
WO2022030173A1 (fr) * 2020-08-06 2022-02-10 スガツネ工業株式会社 Charnière d'amortissement unidirectionnelle

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