Hinge device

Abstract

The invention provides a hinge device capable of avoiding impact when a cover is closed. A hinge device (5) is provided with: a first hinge body (6) fixed to a housing (2) (a first object); a second hinge body (7) fixed to the cover (3) (second object); and a shaft member (8) that connects the two hinge bodies (6, 7). The hinge device (5) is further provided with a one-way clutch (30), a frictional resistance generation mechanism (40), and a damping mechanism (50). By means of the one-way clutch (30), frictional resistance is generated only when the cover (3) is closed, and frictional resistance is not generated when the cover (3) is opened. The cover (3) is stationary at any position by frictional resistance from an upright position to a predetermined angle. The cover (3) rotates in the closing direction against the frictional resistance by the torque generated by the weight of the cover (3) within the angular range close to the closed position. At this time, in addition to frictional resistance, the damping effect of the damping mechanism (50) also acts, so that rotation of the cover (3) is suppressed, and impact during closing can be avoided.

Description

Technical Field

[0001] The invention relates to a hinge device with a friction resistance generating mechanism and a one-way clutch. Background Art

[0002] Patent Document 1 (Japanese Utility Model Registration No. 3152248) discloses a hinge device that rotatably supports a piano cover (second object) on a piano body (first object). The hinge device includes a first hinge body fixed to the piano body, a second hinge body fixed to the cover, and a shaft member that rotatably connects the first hinge body and the second hinge body.

[0003] The hinge device of Patent Document 1 also has a friction resistance generating mechanism and a one-way clutch. In short, both ends of the shaft member are rotatably supported on either the first hinge body or the second hinge body via the one-way clutch. A friction resistance generating mechanism is provided between the middle portion of the shaft member and the other hinge body.

[0004] When the lid is opened, the one-way clutch releases the engagement state between the shaft member and the hinge body on one side. As a result, the two hinge bodies can rotate without being subjected to the friction resistance generated by the friction resistance generating mechanism, and the operator can open the lid to a specified angle only by overcoming the operating force of the weight of the lid. When the lid rotates in the closing direction by the torque (self-weight torque) generated by its own weight, the one-way clutch causes the shaft member to be engaged with the hinge body on one side. As a result, the shaft member rotates relative to the hinge body on the other side. As a result, friction resistance is generated, the rotation speed of the lid is suppressed, and the impact when the lid is closed can be avoided.

[0005] The hinge device of patent document 2 (Japanese invention publication No. 6208916) also has a friction resistance generating mechanism and a one-way clutch. In this hinge device, the friction resistance generating mechanism can make the second object fixed with the second hinge body stationary at any angle relative to the first object fixed with the first hinge body. Summary of the invention

[0006] Problems to be solved by the invention

[0007] When the hinge device having the above-mentioned one-way clutch and friction resistance generating mechanism is applied to the opening and closing of the lid, for example, in the case where the lid can be stationary at any angle by friction resistance as shown in Patent Document 2, the lid cannot be completely closed by friction resistance, and the so-called opening problem will occur. This is because the torque in the closing direction does not act on the lid. Therefore, it is possible to consider reducing the friction resistance so that the deadweight torque overcomes the friction resistance within the angle range close to the closed position. However, if the friction resistance is reduced, the lid will reach the closed position rapidly and the impact will become larger. When the weight of the lid is large, this undesirable situation becomes obvious.

[0008] Solutions for solving problems

[0009] The hinge device of the present invention is completed to solve the above-mentioned problems, and is characterized in that it comprises: a first hinge body to be fixed to a first object; a second hinge body to be fixed to a second object; a rotation connection mechanism having at least one shaft member to connect the first hinge body and the second hinge body in a relatively rotatable manner; a one-way clutch arranged between the hinge body of one of the first hinge body and the second hinge body and the shaft member; and a friction resistance generating mechanism to generate friction resistance when the hinge body of the other of the first hinge body and the second hinge body and the shaft member rotate relative to each other.

[0010] The second hinge body is given a torque in a first direction toward a first rotation limit position,

[0011] The one-way clutch is configured such that when the second hinge body rotates in the first direction, the hinge body on one side and the shaft member are in an engaged state capable of transmitting torque, and when the second hinge body rotates in a second direction away from the first rotation limit position, the hinge body on one side and the shaft member are in a non-engaged state capable of not transmitting torque.

[0012] When the second hinge body rotates in the first direction, at least within a first angle range between the first rotation limit position and a predetermined angle position, the torque overcomes the friction resistance.

[0013] The hinge device further includes a damping mechanism that exerts a damping effect on the second hinge body within at least a part of the first angle range when the second hinge body rotates in the first direction.

[0014] According to the above structure, when the second hinge body rotates in the first direction toward the first rotation limit position through torque, in addition to the friction resistance, the damping effect achieved by the damping mechanism is also exerted, thereby suppressing the rotation of the second hinge body and even the rotation of the second object, and avoiding the impact when reaching the first rotation limit position.

[0015] Preferably, the torque is a deadweight torque caused by the deadweight of the second object, and when the second hinge body is at the first rotation limit position, the second object is in a horizontal state or in a state inclined relative to a horizontal state.

[0016] Preferably, when the angular position of the second hinge body when the second object is erected so that the self-weight torque is zero is set as a reference angular position, within a second angular range between the reference angular position and the specified angular position, the frictional resistance counteracts the self-weight torque to make the second object stationary.

[0017] According to the above configuration, convenience can be improved by making the second object stationary within the second angle range.

[0018] Preferably, the second hinge body can rotate within a third angle range from the reference angle position to a second rotation limit position opposite to the first rotation limit position, and when the second hinge body rotates in the second direction within the third angle range, the damping mechanism also exerts a damping effect.

[0019] When the second hinge body rotates toward the second rotation limit position, the friction resistance does not work, but the damping effect achieved by the damping mechanism can avoid the impact when the second hinge body reaches the second rotation limit position.

[0020] Preferably, the friction resistance generating mechanism includes an adjustment mechanism for adjusting the friction resistance.

[0021] According to the above configuration, by adjusting the frictional resistance, the second angle range in which the second object can be brought to rest and the first angle range in which the second object naturally rotates toward the first rotation limit position by deadweight torque can be adjusted.

[0022] More preferably, the friction resistance generating mechanism further comprises: a fastening member having a holding portion with a C-shaped cross-section surrounding the outer periphery of the shaft member and a pair of fastening plates protruding radially outward from the holding portion; and a friction member arranged between the holding portion of the fastening member and the outer periphery of the shaft member, and the adjustment mechanism comprises: an internal threaded portion and an adjustment screw that are threaded together, and friction resistance is generated between the friction member and the shaft member by fastening the pair of fastening plates in a direction approaching each other.

[0023] Effects of the Invention

[0024] According to the present invention, it is possible to avoid an impact when the second hinge body reaches the first rotation limit position. BRIEF DESCRIPTION OF THE DRAWINGS

[0025] Figure 1AThis is a side view of the hinge device according to one embodiment of the present invention, showing a state in which the lid is fully opened (opening angle 120 degrees).

[0026] Figure 1B It is a side view of the hinge device, showing a state where the cover is closed (opened at an angle of 0°).

[0027] Figure 2 It is a three-dimensional diagram of the hinge device.

[0028] Figure 3 yes Figure 2 Sectional view viewed in the direction III-III.

[0029] Figure 4 It is an exploded perspective view of the hinge device.

[0030] Figure 5A It is a plan cross-sectional view of the hinge device when the cover is at an opening angle of 120°.

[0031] Figure 5B yes Figure 5A Side sectional view taken along the B-B line.

[0032] Fig. 6A It is a plan cross-sectional view of the hinge device when the cover is at an opening angle of 80°.

[0033] Figure 6B It is a side sectional view of the hinge device when the cover is at an opening angle of 80°.

[0034] Fig. 7A It is a plan cross-sectional view of the hinge device when the cover is at an opening angle of 60°.

[0035] Figure 7B It is a side sectional view of the hinge device when the cover is at an opening angle of 60°.

[0036] Fig. 8A It is a plan cross-sectional view of the hinge device when the cover is in the closed position (opening angle 0°).

[0037] Figure 8B is a side cross-sectional view of the hinge assembly when the lid is in the closed position. DETAILED DESCRIPTION

[0038] Hereinafter, an embodiment of the present invention will be described with reference to the accompanying drawings. Figure 1A , Figure 1B As shown, for example, a storage box 1 for storing medical inspection materials includes a housing 2 (first object), a cover 3 (second object) for opening and closing an upper end opening 2x of the housing 2, and a plurality of hinge devices 5 for rotatably supporting the cover 3. Figure 1A , Figure 1BIn the figure, since a plurality of hinge devices 5 are arranged in a direction perpendicular to the paper surface, only one is shown. Figure 1A The fully open position (opening angle 120°) and Figure 1B The lever can be rotated between a closed position (opening angle 0°).

[0039] The cover 3 is heavy so as to seal the opening 2x, and a torque (deadweight torque) generated by its own weight acts on the cover 3. This deadweight torque is zero when the center of gravity of the cover 3 is located in an upright position (a position of (90+α)° where the opening angle is close to 90° in this embodiment) directly above the rotation center L described later, and increases from this upright position as the inclination of the cover 3 increases (that is, as the opening angle decreases), and reaches a maximum at the closed position (opening angle 0°) where the cover 3 becomes horizontal.

[0040] <Basic structure of hinge device>

[0041] The structure of the hinge device 5 is described in detail below. Figure 3 As shown, 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; a second hinge body 7 fixed to the upper surface of the cover 3 (the upper surface of the cover 3 in the closed state); and a single shaft member 8 (rotational connection mechanism) that rotatably connects the two hinge bodies 6 and 7. The axis of the shaft member 8 is provided as the rotation axis L.

[0042] <Structure of the first hinge body>

[0043] like Figure 4 As shown, the first hinge body 6 has two hinge components 10A, 10B and a cover 10C arranged along the direction of the rotation axis L (hereinafter, simply referred to as the axial direction). The hinge components 10A, 10B have the same structure and have a fixing portion 11 and a guide portion 12 in order from their axial outer ends toward the inside, and a bearing portion 13 is provided next to the fixing portion 11 (adjacent to the direction perpendicular to the rotation axis L). For the convenience of the following description, the horizontal direction perpendicular to the rotation axis L is referred to as the T direction (refer to Figure 2 ~Figure 5).

[0044] The bearing portions 13 of the hinge members 10A and 10B are formed with bearing holes 13a facing each other for supporting both ends of the shaft member 8. The guide portion 12 is used to guide a cam follower 52 described later, and has a pair of rising walls 12a facing each other in the T direction.

[0045] The hinge member 10A on one side has a pair of connecting portions 14 separated in the T direction formed on the axial inner side of the guide portion 12. The hinge member 10B on the other side also has a pair of connecting portions 15 formed on the axial inner side of the guide portion 12. These connecting portions 14 and 15 are staggered in the vertical direction, such as Figure 3 The connecting parts 14 and 15 of the hinge members 10A and 10B are connected to the center of the cover 10C by screwing screws 16a passing through the connecting parts 14 and 15 into screw holes 19a formed on the lower surface of the cover 10C.

[0046] like Figure 3 , Figure 4 As shown, one hinge member 10A has a pair of semi-cylindrical guide surfaces 17 formed between a pair of connecting portions 14. Figure 3 As shown, a pair of semi-cylindrical guide surfaces 18 are also formed on the lower surface of the cover 10C and are opposed to the pair of guide surfaces 17 in the vertical direction. The pair of guide surfaces 17 and 18 are respectively connected to the lower half and the upper half of the cylinder body 51a of the pair of linear dampers 51 described later, and support the cylinder body 51a in a manner that it can slide in the axial direction.

[0047] By passing the screws 16b ( Figure 4 ), and both ends of the cover 10C are connected in a state of covering the hinge members 10A and 10B. A fixing hole 19b is formed in the fixing portion 11 of the hinge members 10A and 10B, and a fixing hole 19c is also formed in the cover 10C. By screwing screws (not shown) passing through these fixing holes 19b and 19c into the support wall 2y, the first hinge body 6 is fixed to the support wall 2y.

[0048] <Structure of the second hinge body>

[0049] like Figure 4 As shown, the second hinge body 7 has an axially elongated hinge block 20A and a cover 20B. The cover 20B is embedded in the lower surface of the hinge block 20A and fixed by a screw 21. The hinge block 20A has a fixing portion 22 and a bearing portion 23 next to the fixing portion 22 (adjacent in the T direction). Fixing holes 24 are formed at both ends of the fixing portion 22 in the long dimension direction, and an adjustment hole 25 that plays a role described later is formed in the center. The second hinge body 7 is fixed to the cover 3 by screwing the screw passing through the fixing hole 24 of the hinge block 20A into the upper surface of the side edge portion of the cover 3.

[0050] The bearing portion 23 is cylindrical, and both ends of the bearing portion 23 in the longitudinal direction are provided as bearing holes 23a. A receiving space 26 is formed in the middle of the bearing portion 23. The inner diameter of the receiving space 26 is larger than the inner diameter of the bearing hole 23a and the lower part is open. Figure 3As shown, the lower portion of the accommodation space 26 is covered by a cover 20B.

[0051] <Shaft member and one-way clutch>

[0052] like Figure 4 As shown in FIG. 5 , the middle portion of the shaft member 8 is inserted into a pair of bearing holes 23a of the hinge block 20A of the second hinge body 7 via a sleeve 35, and both ends of the shaft member 8 are inserted into a pair of bearing holes 13a of the first hinge body 6 via a one-way clutch 30, thereby the shaft member 8 connects the first hinge body 6 and the second hinge body 7 in a rotatable manner. The one-way clutch 30 is a well-known structure, and when the shaft member 8 is intended to rotate in one direction relative to the bearing portion 13, the one-way clutch 30 releases the engagement (meshing) between the shaft member 8 and the bearing portion 13, allowing the shaft member 8 and the bearing portion 13 to rotate relative to each other. When the shaft member 8 is intended to rotate in the other direction, the one-way clutch 30 engages the shaft member 8 with the bearing portion 13, prohibiting the relative rotation of the two.

[0053] <Friction resistance generating mechanism>

[0054] like Figure 3 , Figure 4 As shown, a friction resistance generating mechanism 40 is arranged in the accommodation space 26 of the second hinge body 7. The friction resistance generating mechanism 40 includes a fastening member 41, a pair of retainers 42, a pair of friction members 43, a nut 44 (internal thread portion) as an adjustment mechanism, and an adjustment screw 45.

[0055] The fastening member 41 has a cylindrical holding portion 41a with a C-shaped cross section and a pair of fastening pieces 41b protruding radially outward from a pair of side edges of the holding portion 41a. A pair of friction members 43 are in a circular arc shape in cross section, are in contact with the outer periphery of the central portion of the shaft member 8, and are held by the holding portion 41a of the fastening member 41 in a non-rotatable manner via a retainer 42 in a circular arc shape in cross section. The pair of fastening pieces 41b of the fastening member 41 are clamped between the wall surface of the accommodating space 26 and the nut 44. A pair of fastening pieces 41b are formed with a notch 41c (insertion portion), and an adjustment screw 45 passes through the notch 41c of the fastening piece 41b from the adjustment hole 25 of the second hinge body 7 and is screwed into the nut 44. When the adjustment screw 45 is screwed into the nut 44, the interval between the pair of fastening pieces 41b becomes narrower, and the friction member 43 strongly contacts the outer periphery of the shaft member 8 via the holding portion 41a, which can generate friction resistance. The friction resistance can be adjusted by adjusting the tightening force of the tightening member 51 by adjusting the screwing amount of the adjusting screw 45 into the nut 44. It should be noted that the outer periphery of the nut 44 is non-circular, and the nut 44 is locked by fitting it into the non-circular support recess 46 of the cover 20B.

[0056] <Damping mechanism>

[0057] like Figure 4 , Figure 5A As shown, the hinge device 5 further includes a damping mechanism 50. The damping 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 pair of linear dampers 51 in the axial direction; a pair of cam members 53 arranged on the axial outer sides of the cam followers 52; and a pair of link arms 54 (linkage mechanism) respectively connected to the pair of cam members 53.

[0058] The hydraulic linear damper 51 is well known, and includes a cylinder 51a containing liquid, a piston (not shown) in the cylinder 51a, and a rod 51b fixed at one end to the piston and protruding from the cylinder 51a. When the rod 51b is pushed in the sinking direction, the flow resistance of the fluid passing through the orifice inside the cylinder exerts a damping effect. In the first hinge body 10, the cylinder 51a of the linear damper 51 is supported between the guide surface 17 of the hinge member 10A and the guide surface 18 of the cover 10C in an axially slidable manner. In this embodiment, the rods 51b of the pair of linear dampers 51 protrude in opposite directions to each other.

[0059] The pair of cam followers 52 are also supported by the guide portion 12 so as to be slidable in the axial direction, and as described later, they approach or move away from each other in the axial direction. A roller 56 is rotatably supported on the axial outer side of the cam followers 52 via a pin 55 .

[0060] The pair of cam members 53 are supported between the fixing portion 11 and the guide portion 12 of the hinge members 10A, 10B of the first hinge body 6 so as to be slidable in the T direction. The cam members 53 are formed with cam surfaces 57 extending in the T direction, and the rollers 56 of the cam followers 52 are in contact with the cam surfaces 57.

[0061] The cam surfaces 57 of the pair of cam members 53 are symmetrically shaped and face each other in the axial direction, and have a flat non-operating area 57a extending parallel to the T direction (i.e., the sliding direction) and inclined operating areas 57b and 57c on both sides of the non-operating area 57a in the T direction. The first operating area 57b close to the rotation axis L is inclined in a manner tending to the axial inner side as it approaches the rotation axis L. The second operating area 57c away from the rotation axis L is inclined in a manner tending to the axial inner side as it moves away from the rotation axis L.

[0062] A pair of link arms 54 extend in the T direction, and each has one end rotatably connected to the end portion of a pair of cam members 53 near the rotation axis L via a pin 58, and each has the other end inserted into a groove 23b formed at both axial ends of the bearing portion 23 of the second hinge body 7, and is rotatably connected to the two ends of the bearing portion 23 via a pin 59.

[0063] <Function of hinge device>

[0064] The operation of the hinge device 5 having the above-described structure will be described.

[0065] will with Figure 1B The position of the second hinge body 7 corresponding to the closed position (opening angle 0°) of the cover 3 shown in FIG. 1 is defined as the first rotation limit position P1. Figure 1A The position of the second hinge body 7 corresponding to the fully open position (opening angle 120°) of the cover 3 shown is defined as the second rotation limit position P2. It should be noted that at the first rotation limit position P1 of the second hinge body 7, the cover 3 abuts against the upper end of the housing 2, and at the second rotation limit position P2, the second hinge body 7 abuts against the cover 10C of the first hinge body 6 (refer to Figure 5B ).

[0066] Further references Figure 1A , Figure 1B The position of the second hinge body 7 corresponding to the upright position (opening angle (90+α)°) of the cover 3 with zero deadweight torque as described above is defined as the reference angle position Pr. The position of the second hinge body 7 corresponding to the opening angle of 30° of the cover 3 is defined as the specified angle position Px. Moreover, the angle range of the second hinge body 7 corresponding to the opening angle of 0° to 30° of the cover 3 is defined as the first angle range θ1, the angle range of the second hinge body 7 corresponding to the opening angle of 30° to (90+α)° of the cover 3 is defined as the second angle range θ2, and the angle range of the second hinge body 7 corresponding to the opening angle of (90+α)° to 120° of the cover 3 is defined as the third angle range θ3.

[0067] First, the cover 3 is Figure 1A 5 is rotated in the closing direction (first direction) to Figure 1B 8. When the cover 3 rotates in the closing direction, the one-way clutch 30 causes the shaft member 8 to engage with the bearing portion 13 of the first hinge body 6. Therefore, the shaft member 8 does not rotate relative to the first hinge body 6, but the friction resistance generating mechanism 40 provided on the second hinge body 6 rotates relative to the shaft member 8. As a result, friction resistance is generated over the entire angle range of the cover 3.

[0068] In the fully open position, the cover 3 tilts from the upright position where the deadweight torque is zero to the opening direction, and the deadweight torque acts in the opening direction. Therefore, the operator rotates the cover 3 to the upright position with an operating force that overcomes the deadweight torque and the friction resistance.

[0069] When the cover 3 is rotated by the operator in the closing direction and exceeds the upright position, the self-weight torque is switched to the closing direction. However, within the angle range from the upright position to the opening angle of 30° (the second angle range θ2), the self-weight torque is small and does not exceed the friction resistance. Therefore, even if the operator removes his hand from the cover 3 within this angle range, the cover 3 can be kept stationary at this angle. When the cover 3 is rotated in the closing direction within this angle range, the operator needs to resist the friction resistance to apply the operating force in the closing direction to the cover 3.

[0070] As the opening angle of the cover 3 becomes smaller and approaches the horizontal, the self-weight torque increases. When the opening angle of the cover 3 is less than 30°, the self-weight torque will overcome the frictional resistance. Therefore, when the operator removes his hand from the cover 3, the cover 3 automatically closes. Within the angle range of 30° to 0° (the first angle range θ1), the self-weight torque is weakened by the frictional resistance, so the rotation speed of the cover 3 is suppressed. However, the self-weight torque increases as the opening angle of the cover 3 approaches 0°, so when the weight of the cover 3 is large, the braking achieved by the frictional resistance will become insufficient. In the present embodiment, the damping effect achieved by the damping mechanism 50 is applied, so the rotation speed of the cover 3 in the closing direction can be fully suppressed, and the impact when the cover 3 is closed can be avoided.

[0071] The function of the damping mechanism 50 is described in detail. As shown in FIG6 and FIG7, when the cover 3 is opened at an angle of 60° to 80°, the rollers 56 of the pair of cam followers 52 are located in the non-operating area 57a of the cam surface 57 of the pair of cam members 53, and the linear damper 51 has the maximum length. When the cover 3 rotates in the closing direction, the link arm 54 of the damping mechanism 50 moves in the left direction as shown in FIG6 and FIG7, and the cam member 53 also moves in the left direction (the direction away from the rotation axis L) via the link arm 54. When the opening angle of the cover 30 is less than 60°, the rollers 56 of the pair of cam followers 52 enter the first operating area 57b of the cam surface 57 of the pair of cam members 53. As a result, the pair of cam followers 52 move in the direction of approaching each other, causing the pair of linear dampers 51 to contract, so that the damping effect achieved by the pair of linear dampers 51 can be exerted.

[0072] In this embodiment, as shown in Fig. 7 and Fig. 8, the roller 56 moves in the first working area 71b of the cam surface 57 until the opening angle of the cover 3 reaches 0° from 60°, so that the damping effect can be exerted within this angle range. The damping effect preferably works within the angle range including the first angle range θ1 of 30° to 0°, but can also be set to work within a narrower angle range within the first angle range θ1.

[0073] The damper mechanism 50 presses the linear damper 51 by the slidable cam member 53 , and thus can increase the pressing stroke, thereby being able to exert a large damping effect.

[0074] The cylinder 51a of the linear damper 51 is not fixed and can move in the axial direction, and the top end of the rod 51b and the base end of the cylinder 51a abut against a pair of cam followers 52 through an internal return spring. Therefore, compared with a structure in which the cylinder is fixed and the top end of the rod abuts against a single cam follower, the stroke can be doubled and a greater damping effect can be exerted. In this embodiment, by further providing a pair (or multiple) of linear dampers, the damping effect can be further increased.

[0075] When the cover 3 is in the closed position and has come to rest, the damping mechanism 50 does not function, and the deadweight torque greater than the friction resistance always acts in the closing direction, so that the cover 3 can reliably close the opening 2x of the shell 2 without causing any adverse opening conditions.

[0076] Next, cover 3 from Figure 1B 8 is rotated toward the opening direction (second direction) to Figure 1A 5. The function of the hinge device 5 at the fully open position shown in FIG. 5 is described. In this process, since the one-way clutch 30 makes the shaft member 8 and the bearing portion 13 non-engaged, the friction resistance does not work. The operator can open the cover 3 only by the force against the self-weight torque. The self-weight torque gradually decreases as the cover 3 approaches the upright position. When the cover 3 exceeds the upright position, even if the operator removes his hand from the cover 3, the cover 3 will rotate toward the fully open position due to the self-weight torque. In this embodiment, within the angle range from the upright position to the fully open position (the third angle range θ3), the rotation speed of the cover 3 in the opening direction is suppressed by the damping effect achieved by the damping mechanism 50, and the impact when the cover 3 reaches the fully open position can be avoided. In the third angle range θ3, since the inclination of the cover 3 is smaller than the first angle range θ1, the self-weight torque is small, so even if there is no friction resistance, the rotation speed of the cover 3 can be fully suppressed by the damping effect.

[0077] The function of the damping mechanism 50 is described in detail. As described above, when the cover 3 is at an opening angle of 60° to 80°, the rollers 56 of the pair of cam followers 52 are located in the non-operating area 57a of the cam surface 57 of the pair of cam members 53, and the linear damper 51 has the maximum length. When the cover 3 rotates in the opening direction from the opening angle of 80°, the link arm 54 and the cam member 53 move in the right direction (the direction approaching the rotation axis L) as the second hinge body 7 rotates. When the opening angle of the cover 30 is greater than 80°, the rollers 56 of the pair of cam followers 52 enter the second operating area 57c of the cam surface 57 of the pair of cam members 53. As a result, the pair of cam followers 52 move in a direction approaching each other, causing the pair of linear dampers 51 to contract, so that the damping effect achieved by the pair of linear dampers 51 can be exerted.

[0078] In this embodiment, as shown in Fig. 6 and Fig. 5, the roller 56 moves in the second working area 57c of the cam surface 57 until the opening angle of the cover 3 reaches 120° from 80°, so that the damping effect can be exerted within this angle range. The damping effect preferably works within the angle range of the third angle range θ3 including (90+α)° to 120°, but can also be set to work within a narrower angle range within the third angle range θ3.

[0079] In this embodiment, the first angle range θ1 and the second angle range θ2 can be adjusted by adjusting the friction resistance of the friction resistance generating mechanism 40 by the adjusting screw 45. That is, when the adjusting screw 45 is loosened, the friction resistance decreases, so the first angle range θ1 becomes wider and the second angle range θ2 becomes narrower. Conversely, when the adjusting screw 45 is tightened, the friction resistance increases, so the first angle range θ1 becomes narrower and the second angle range θ2 becomes wider.

[0080] The present invention is not limited to the above-described embodiment, and various modifications can be adopted without departing from the gist of the present invention.

[0081] In the above embodiment, the second object is kept stationary within the second angle range, but slight rotation may be allowed.

[0082] In the above embodiment, the second hinge body is in the first rotation limit position when the cover 2 is horizontal, but the second hinge body may be in the first rotation limit position when the cover is inclined relative to the horizontal (for example, inclined within 30°).

[0083] The first hinge body may be provided with a friction resistance generating mechanism, and the second hinge body may be provided with a one-way clutch.

[0084] The damping mechanism may also use a linkage mechanism composed of multiple components instead of a link arm.

[0085] When a plurality of linear dampers are provided with one link arm, one cam member, and one cam follower, respectively, the cylinders of the linear dampers are set in fixed positions so that all the rods face the single cam follower.

[0086] When one link arm, one cam member, and one linear damper are provided separately, the cam follower may be omitted. In this case, the rod tip of the linear damper directly contacts the cam surface of the cam member.

[0087] The damper mechanism may be composed of 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.

[0088] The rotation coupling mechanism may be constituted by a link mechanism including a plurality of shaft members and a plurality of links.

[0089] The elasticity of the spring may be used to apply torque to the second hinge body instead of the self-weight torque of the cover (second object). This torque application method is used when the hinge device is arranged so that the second object can rotate around a vertical axis relative to the first object.

[0090] In the hinge device of the above embodiment, a friction resistance generating mechanism having a mechanism for adjusting friction resistance is used, but a friction resistance generating mechanism of a simple structure without an adjusting mechanism may also be used. For example, as one embodiment, a metal shaft member may be pressed into a resin bearing portion so that friction is generated between the outer peripheral surface of the shaft member and the inner peripheral surface of the bearing portion. In another embodiment, a friction member may be sandwiched between the outer peripheral surface of the shaft member and the inner peripheral surface of the bearing portion.

[0091] Industrial Applicability

[0092] The present invention can be applied to a hinge device having a friction resistance generating mechanism and a one-way clutch.

[0093] Description of Reference Numerals

[0094] 2: Shell (first object); 3: Door (second object); 5: Hinge device; 6: First hinge body; 7: Second hinge body; 8: Shaft member (rotational connection mechanism); 30: One-way clutch; 40: Friction resistance generating mechanism; 41: Fastening member; 41a: Holding portion; 41b: Fastening plate; 43: Friction member; 44: Nut (internal threaded portion); 45: Adjusting screw; 50: Damping mechanism; 51: Linear damper; 52: Cam follower; 53: Cam member; 54: Link arm; 57: Cam surface; 57a: Non-working area; 57b: First working area; 57c: Second working area; L: Rotation axis; θ1: First angle range; θ2: Second angle range; θ3: Third angle range.

Claims

1. A hinge device, characterized in that: have: A first hinge body (6) to be fixed to a first object (2); A second hinge body (7) to be fixed to a second object (3); A rotation connection mechanism having at least one shaft member (8) for connecting the first hinge body and the second hinge body in a relatively rotatable manner; a one-way clutch (30) disposed between one of the first hinge body and the second hinge body and the shaft member; and A friction resistance generating mechanism (40) generates friction resistance when the other hinge body of the first hinge body and the second hinge body and the shaft member rotate relative to each other. The second hinge body (7) is given a torque in a first direction tending to a first rotation limit position, The one-way clutch (30) is configured such that when the second hinge body (7) rotates in the first direction, the hinge body on one side and the shaft member (8) are in an engaged state capable of transmitting torque, and when the second hinge body rotates in a second direction away from the first rotation limit position, the hinge body on one side and the shaft member are in a non-engaged state capable of not transmitting torque. When the second hinge body (7) rotates in the first direction, at least within a first angle range (θ1) between the first rotation limit position and a specified angle position, the torque overcomes the friction resistance. The hinge device further comprises a damping mechanism (50) which exerts a damping effect on the second hinge body within at least a part of the first angle range (θ1) when the second hinge body (7) rotates in the first direction.

2. The hinge device according to claim 1, characterized in that: The torque is a deadweight torque caused by the deadweight of the second object (4), and when the second hinge body (7) is at the first rotation limit position, the second object (4) is in a horizontal state or in a state inclined relative to the horizontal.

3. The hinge device according to claim 2, characterized in that: When the angular position of the second hinge body (7) when the second object (4) is erected so that the self-weight torque is zero is set as a reference angular position, within a second angular range (θ2) between the reference angular position and the specified angular position, the frictional resistance counteracts the self-weight torque to make the second object stationary.

4. The hinge device according to claim 3, characterized in that: The second hinge body (7) can rotate within a third angle range (θ3) from the reference angle position to a second rotation limit position on the opposite side of the first rotation limit position, and when the second hinge body rotates in the second direction within the third angle range, the damping mechanism (50) also exerts a damping effect.

5. The hinge device according to claim 3, characterized in that: The friction resistance generating mechanism (40) includes an adjusting mechanism for adjusting the friction resistance.

6. The hinge device according to claim 5, characterized in that: The friction resistance generating mechanism (40) further comprises: a fastening member (41) having a gripping portion (41a) with a C-shaped cross section surrounding the outer periphery of the shaft member (8) and a pair of fastening pieces (41b) protruding radially outward from the gripping portion; and a friction member (43) disposed between the gripping portion of the fastening member and the outer periphery of the shaft member. The adjustment mechanism comprises: an internal thread portion (44) and an adjustment screw (45) which are threadedly engaged with each other, and by tightening the pair of fastening pieces in directions approaching each other, friction resistance is generated between the friction member (43) and the shaft member (8).

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