Damper hinge, range hood having damper hinge and turn braking method of rectification plate

Abstract

To provide a damper hinge which can smoothly adjust a turning position, a range hood having the same, and a turn braking method of a rectification plate.SOLUTION: A damper hinge comprises: a shaft body having a shaft part; and a bearing body having a bearing hole into which the shaft part is turnably fitted. The shaft body has: a disc part protruding to a radial outward direction of the shaft part; a tapered part protruding to the radial outward direction of the shaft part, and having a tapered face inclined to a turning direction of the shaft part at a face facing a side face of the disc part; and a first recess formed between the disc part and the tapered part. The tapered face is formed at the tapered part so that an interval between the side face of the disc part and the tapered face is expanded toward a first turning direction of the shaft part, the bearing body has a first elastic part arranged in the first recess, and the tapered face pushes the first elastic part to the side face of the disc part by turning of the shaft part to the first turning direction.SELECTED DRAWING: Figure 5

Description

[Technical field]

[0001] The present invention relates to a damper hinge, a range hood equipped with the damper hinge, and a method for braking the rotation of a baffle plate. [Background technology]

[0002] A range hood has an airflow generator such as a sirocco fan or turbo fan built in, and takes in indoor air through an opening on the underside of the hood and exhausts it. A filter is attached to the intake port to capture oily smoke and other substances generated during cooking from the intake air.

[0003] Some range hoods have a baffle plate arranged upstream of the air being drawn into the opening to narrow the area of ​​the suction port. The baffle plate is provided to increase the suction power by narrowing the area of ​​the suction port, thereby improving suction efficiency.

[0004] A range hood is known that includes a hinge that supports a baffle plate so that it can rotate up and down, and a support part that detachably supports the baffle plate on the underside of the hood. In a closed state in which the support part supports the baffle plate on the underside of the hood, when the support by the support part is released, the baffle plate rotates downward by its own weight due to the hinge. When the baffle plate is in an open state suspended by the hinge on the underside of the hood, the range hood can be efficiently cleaned and the filter replaced.

[0005] It is known that a damper hinge that utilizes the viscous resistance of oil is used as a hinge that supports a baffle plate. In addition, Patent Documents 1, 2, and 3 disclose a range hood that includes a hinge mechanism having a damper including a one-way clutch as an opening and closing mechanism for the baffle plate. [Prior art documents] [Patent documents]

[0006] [Patent Document 1] JP 2011-007245 A [Patent Document 2] JP 2011-012750 A [Patent Document 3] JP 2011-007403 A Summary of the Invention [Problem to be solved by the invention]

[0007] When a damper hinge that utilizes the viscous resistance of general oil is used as a hinge supporting the baffle plate, the baffle plate cannot be adjusted to a predetermined open position. Also, the baffle plate is restricted from rotating downward from the initial stage of its rotation from the closed state to the open state. Therefore, the load on the worker when opening the baffle plate is large, and the baffle plate cannot be opened quickly.

[0008] In the range hoods equipped with the hinge mechanism having the damper described in Patent Documents 1, 2, and 3, an operator can manually adjust the open position of the baffle plate. However, because the one-way clutch restricts the downward rotation of the baffle plate from the initial stage of rotation of the baffle plate from the closed state to the open state, it is not possible to quickly adjust the baffle plate to the desired open position. [Means for solving the problem]

[0009] A damper hinge according to one embodiment of the present invention comprises a shaft body having a shaft portion, and a bearing body having a bearing hole into which the shaft portion is rotatably fitted, the shaft body having a disk portion protruding radially outward from the shaft portion, a tapered portion protruding radially outward from the shaft portion and having a tapered surface inclined with respect to the rotation direction of the shaft portion on a surface facing a side of the disk portion, and a first recess formed between the disk portion and the tapered portion, the tapered surface being formed on the tapered portion toward a first rotation direction of the shaft portion such that the distance between the side of the disk portion and the tapered surface is widened, the bearing body having a first elastic portion arranged in the first recess, and the tapered surface pressing the first elastic portion against the side of the disk portion as the shaft portion rotates in the first rotation direction. Effect of the Invention

[0010] According to the present invention, there is provided a damper hinge capable of smoothly adjusting the rotation position, and a range hood equipped with the damper hinge. Also, according to the present invention, there is provided a method for braking the rotation of a baffle plate, which allows for smooth adjustment of the rotation position of the baffle plate and prevents the back surface of the range hood from colliding with a wall that is in contact with the baffle plate. [Brief description of the drawings]

[0011] [Figure 1] FIG. 2 is a partially cutaway side view of the range hood. [Diagram 2] This is an oblique view from below of the range hood with the baffle plate in a closed state. [Diagram 3] This is an oblique view from below of the range hood with the baffle plate in the open position. [Figure 4] 13 is a perspective view of the attachment / detachment mechanism with the current plate engaged. FIG. [Diagram 5] FIG. 4 is a perspective view showing the internal structure of the damper hinge. [Figure 6] 11 is a perspective view for explaining changes in state of the shaft body and the bearing body due to rotation of the shaft portion. FIG. [Figure 7] 7 is a plan view for explaining changes in state of the shaft body and the bearing body in FIG. 6. FIG. [Figure 8] 11 is a perspective view illustrating a change in state of the shaft body and the bearing body due to rotation of the shaft portion in a first rotation direction after contact braking is generated between the first elastic portion and the first braking surface. FIG. [Figure 9] 9 is a side view for explaining changes in state of the shaft body and the bearing body in FIG. 8. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] [Overview of the embodiment of the present invention] Hereinafter, an outline of an embodiment of the present invention will be described.

[0013] (1) The damper hinge according to this embodiment is, A shaft body having a shaft portion; a bearing body having a bearing hole into which the shaft portion is rotatably fitted; Equipped with The shaft body is a disk portion protruding radially outward from the shaft portion; a tapered portion that protrudes radially outward from the shaft portion and has a tapered surface that is inclined with respect to the rotation direction of the shaft portion on a surface that faces a side surface of the disk portion; a first recess formed between the disk portion and the tapered portion; having The tapered surface is formed on the tapered portion such that a distance between a side surface of the disk portion and the tapered surface increases in a first rotation direction of the shaft portion, the bearing body has a first elastic portion disposed in the first recess, The tapered surface presses the first elastic portion against a side surface of the disk portion when the shaft portion rotates in the first rotation direction.

[0014] According to the above configuration, the rotation of the shaft portion in the first rotation direction is braked by frictional resistance caused by the tapered surface of the tapered portion pressing the first elastic portion against the side surface of the disk portion (hereinafter, may be referred to as a "friction brake"). In addition, the damper hinge according to this embodiment allows the rotation position of the shaft portion to be adjusted by the friction brake.

[0015] According to the above configuration, the force with which the tapered portion presses the first elastic portion against the side surface of the disk portion (hereinafter, may be simply referred to as "pressing force") increases as the rotation of the shaft portion in the first rotation direction progresses. That is, the pressing force is small early in the rotation of the shaft portion in the first rotation direction and increases later in the rotation. In other words, the braking force of the friction brake is small early in the rotation and increases later in the rotation. Therefore, the damper hinge according to this embodiment enables the shaft portion to rotate quickly in the early rotation.

[0016] Furthermore, according to the above-described configuration, there is no need to assemble a viscous oil sealing mechanism or a clutch mechanism, making it easier to assemble the damper hinge.

[0017] (2) The damper hinge according to this embodiment is, The shaft body comprises at least Two of the tapered portions are disposed on either side of the disk portion; two first recesses formed between the disk portion and the tapered portion; The optical fiber 10 may be configured to have the following configuration.

[0018] According to the above configuration, the rotation of the shaft portion in the first rotation direction is braked by the friction brake generated on both side surfaces of the disk portion, thereby improving the braking force against the rotation of the shaft portion.

[0019] (3) The damper hinge according to this embodiment is the bearing body has a plate portion disposed between the tapered surface and the first elastic portion of the first recess, The plate portion has a smaller friction resistance when it comes into contact with the tapered surface than the first elastic portion, The tapered surface may be configured to press the first elastic portion against a side surface of the disk portion via the plate portion.

[0020] According to the above configuration, the tapered portion presses the first elastic portion against the side surface of the disk portion via the plate portion having a small frictional resistance, whereby the rotation of the shaft portion in the first rotation direction is efficiently braked by the friction brake.

[0021] (4) The damper hinge according to this embodiment is the first recess has a first braking surface with which the first elastic portion comes into contact when the shaft portion rotates in the first rotation direction, The first braking surface may be configured to brake further rotation of the shaft portion in the first rotation direction by contacting the first elastic portion with the first braking surface.

[0022] According to the above configuration, further rotation of the shaft portion in the first rotation direction is damped by contact of the first elastic portion with the first damping surface, thereby restricting the range of rotation of the shaft portion in the first rotation direction.

[0023] (5) The damper hinge according to this embodiment may be configured so that the first braking surface is positioned at a position that does not contact the plate portion when the shaft portion rotates in the first rotation direction.

[0024] According to the above configuration, damage and deformation of the plate portion due to collision of the plate portion with the first braking surface is suppressed.

[0025] (6) The damper hinge according to this embodiment is The shaft has a second recess, the bearing body has a second elastic portion disposed in the second recess, the second recess has a second braking surface with which the second elastic portion comes into contact when the shaft portion rotates in a second rotation direction opposite to the first rotation direction, The second braking surface may be configured to brake further rotation of the shaft portion in the second rotation direction by contacting the second elastic portion with the second braking surface.

[0026] According to the above configuration, further rotation of the shaft portion in the second rotation direction is damped by contact of the second elastic portion with the second damping surface, thereby restricting the range of rotation of the shaft portion in the second rotation direction.

[0027] (7) The damper hinge according to this embodiment is the second recess has a third braking surface with which the second elastic portion comes into contact when the shaft portion rotates in the first rotation direction, The third braking surface may be configured to brake further rotation of the shaft portion in the first rotation direction by contacting the second elastic portion with the third braking surface.

[0028] According to the above configuration, further rotation of the shaft portion in the first rotation direction is damped by contact of the second elastic portion with the third damping surface, thereby making it possible to further restrict the range of rotation of the shaft portion in the first rotation direction.

[0029] (8) The damper hinge according to this embodiment may be configured such that, when the second elastic portion is in contact with the third braking surface, the first braking surface is positioned at a position where the first elastic portion is pressed against the first braking surface and elastically deformed.

[0030] According to the above configuration, further rotation of the shaft portion in the first rotation direction after the first elastic portion comes into contact with the first braking surface can be damped by elastic deformation of the first elastic portion.

[0031] (9) The range hood according to this embodiment includes the damper hinge according to this embodiment described above as a hinge that supports the baffle plate so that the baffle plate can rotate up and down.

[0032] According to the above configuration, it is possible to smoothly adjust the rotation position of the straightening plate and to prevent the straightening plate from hitting the wall with which the rear surface of the range hood is in contact.

[0033] (10) The braking method according to this embodiment includes: A method for damping the rotation of a straightening plate in a range hood having a damper hinge that supports the straightening plate so that the straightening plate can rotate in the vertical direction, comprising: The above damper hinge is A shaft body to which the flow plate is fixed; a bearing body into which the shaft body is rotatably fitted and having an elastic portion that brakes the rotation of the shaft body; Equipped with In the rotation of the straightening plate from the top to the bottom, a first step in which the rotation of the straightening plate is damped by frictional resistance between the shaft body and the elastic portion; a second step in which the rotation of the straightening plate is braked by frictional resistance and contact regulation between the shaft body and the elastic portion; has.

[0034] According to the braking method, the rotation of the straightening plate is braked in two steps: a first step of friction braking, and a second step of braking by friction braking and contact restriction (hereinafter sometimes referred to as "contact braking"). This prevents the straightening plate from colliding with the wall that the back surface of the range hood contacts. Even if the shaft of the damper hinge rotates until the straightening plate reaches the wall that the back surface of the range hood contacts, the damper hinge is not damaged and the straightening plate can be returned to a predetermined rotation position.

[0035] According to the above braking method, the braking force against the rotation of the straightening plate in the first rotation direction increases as the plate moves from the first step to the second step. That is, the straightening plate can rotate quickly in the first step at the beginning of the rotation. This allows the straightening plate to be smoothly adjusted to the rotation position.

[0036] (11) The braking method according to this embodiment may also include a third step in which the rotation of the straightening plate is braked by frictional resistance and contact regulation between the shaft body and the elastic portion, and elastic deformation of the elastic portion.

[0037] According to the above braking method, the rotation of the straightening plate in the first rotation direction is braked in three steps. In the third step, the rotation of the straightening plate is braked by a friction brake, a contact brake, and a brake due to elastic deformation of an elastic part (hereinafter, sometimes referred to as an "elastic brake"). This further suppresses the collision of the straightening plate with the wall that the back surface of the range hood contacts.

[0038] (12) The braking method according to this embodiment includes: The elastic portion includes a first elastic portion and a second elastic portion, the first step in which the rotation of the straightening plate is damped by frictional resistance between the shaft body and the first elastic portion; the second step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion; the third step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion, and elastic deformation of the first elastic portion; the fourth step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion, elastic deformation of the first elastic portion, and contact regulation between the shaft body and the second elastic portion; The above formula may be used.

[0039] According to the braking method, the rotation of the baffle plate in the first rotation direction is braked in four steps, which further suppresses the baffle plate from colliding with the wall that the rear surface of the range hood contacts.

[0040] (13) The braking method according to this embodiment may include the fifth step in which the rotation of the straightening plate is braked by frictional resistance and contact regulation between the shaft body and the first elastic portion, elastic deformation of the first elastic portion, contact regulation between the shaft body and the second elastic portion, and elastic deformation of the second elastic portion.

[0041] According to the braking method, the rotation of the baffle plate in the first rotation direction is braked in five steps, which significantly reduces the collision of the baffle plate with the wall that the rear surface of the range hood contacts.

[0042] <Details of the embodiment of the present invention> Hereinafter, the details of the embodiments of the present invention will be described with reference to the drawings. Note that at least some of the embodiments described below may be combined in any desired manner.

[0043] [Range hood] Fig. 1 is a partially cutaway side view of the range hood 1. The two double-headed arrows in Fig. 1 indicate the height and depth directions of the range hood 1, respectively. Fig. 2 is a perspective view of the range hood 1 from below with the baffle plate 10 in a closed state. Fig. 3 is a perspective view of the range hood 1 from below with the baffle plate 10 in an open state. The three double-headed arrows in Figs. 2 and 3 indicate the height, width, and depth directions of the range hood 1, respectively.

[0044] Range hood 1 has airflow box 3 with built-in fan 4, which is an airflow generator, and flat box-shaped hood 2 with an open bottom attached to the lower part of the airflow box 3. Hood 2 has bottom panel 5 that forms the bottom. Bottom panel 5 has opening 5a for taking in air into airflow box 3. Filter 6 is provided in opening 5a.

[0045] A straightening plate 10 is supported on the underside of the lower panel 5 so as to cover the opening 5a while being spaced apart from the lower panel 5. The straightening plate 10 straightens the flow of air sucked through the opening 5a. The straightening plate 10 of the range hood 1 is in the shape of a rectangular plate having a rear edge 10a, a front edge 10b, a right edge 10c, and a left edge 10d.

[0046] In the range hood 1, the air in the room where the range hood 1 is installed rises due to the airflow generated by the fan 4 and hits the lower panel 5 and the air straightening plate 10, and is sucked into the opening 5a through the gap between the lower panel 5 and the air straightening plate 10. At that time, the air passes through the filter 6, which collects oil, dust, and the like contained in the air. The indoor air sucked in from the opening 5a passes through an opening (not shown) in the hood 2 and is taken into the air blower box 3, and then passes through the fan 4 and is exhausted to the outside of the unit.

[0047] The hood 2 is a flat box type that is horizontal or nearly horizontal when the range hood 1 is installed. The back surface of the hood 2 and the back surface of the ventilation box 3 are flush or nearly flush, and the range hood 1 can be installed with its back surface in contact with a wall surface inside the room (wall-mounted type). In the following explanation, the range hood 1 is assumed to be mounted on the wall by its back surface, but the range hood 1 may also be mounted on the wall by its side surface (side-wall-mounted type). The range hood 1 may also be installed in contact with the ceiling without being in contact with a wall surface (ceiling-mounted type).

[0048] The periphery of the opening 5a of the lower panel 5 has a surface shape that is horizontal or approximately horizontal when the range hood 1 is installed. The lower panel 5 contains a magnetic material such as iron, cobalt, or nickel. The lower panel 5 is preferably made of enamel.

[0049] The attachment / detachment mechanism 7 is configured to detachably engage the air straightening plate 10 with the lower panel 5 of the hood 2. The attachment / detachment mechanism 7 has a damper hinge 100 that supports the air straightening plate 10 rotatably in the vertical direction with the rear edge portion 10a of the air straightening plate 10 as a base end. The air straightening plate 10 has two magnetically attached portions 11 near the right edge portion 10c and the left edge portion 10d, which are closer to the front edge portion 10b than the rear edge portion 10a. The magnetically attached portions 11 are magnetically attached to the magnetically attached portion 5b of the lower panel 5.

[0050] When the rectifying plate 10 is in the closed state, the magnetically attached portion 11 is magnetically attached to the magnetically attached portion 5b. In the closed state, the rectifying plate 10 is in position P1 indicated by a solid line in Fig. 1. In the closed state, the rectifying plate 10 is supported by the lower panel 5 by the magnetically attached portion 11 and the attachment / detachment mechanism 7, generally parallel to the surface surrounding the opening 5a of the lower panel 5. In addition, in the closed state, the damper hinge 100 is configured to brake further rotation of the rectifying plate 10 toward the lower panel 5 by a contact brake.

[0051] When the magnetic attraction of the magnetic portion 11 to the magnetically attracted portion 5b is released, the rectifying plate 10 rotates in a first rotation direction indicated by a two-dot chain arrow in Fig. 1 by the damper hinge 100, and enters an open state. The damper hinge 100 is configured to brake the rotation of the rectifying plate 10 in the first rotation direction by at least one braking means selected from a friction brake, a contact brake, and an elastic brake.

[0052] At position P2, the rotation of the rectifier plate 10 in the first rotation direction is braked by a friction brake. At position P3, the rotation of the rectifier plate 10 in the first rotation direction is braked by a friction brake and a contact brake. At position P4, the rotation of the rectifier plate 10 in the first rotation direction is braked by a friction brake, a contact brake, and an elastic brake. In other words, the damper hinge 100 is configured so that the braking force against the rotation of the rectifier plate 10 in the first rotation direction increases as the rotation of the rectifier plate 10 in the first rotation direction progresses. In other words, the damper hinge 100 is configured so that the rectifier plate 10 can rotate quickly in the early stage of its rotation in the first rotation direction.

[0053] Furthermore, the rotation position of the straightening plate 10 can be manually adjusted by the friction brake of the damper hinge 100. For example, the straightening plate 10 can be stopped at the rotation position of position P2 by the friction brake of the damper hinge 100. This allows the worker to stop the straightening plate 10 at a rotation position that makes it easy to perform the attachment and detachment work when attaching and detaching the straightening plate 10 using the attachment and detachment mechanism 7. This improves the workability of attaching and detaching the straightening plate 10.

[0054] As described above, the damper hinge 100 allows for quick rotation of the straightening plate 10 in the initial rotation in the first rotation direction, and allows for adjustment of the rotation position by a friction brake of the straightening plate 10. Therefore, the range hood 1 including the damper hinge 100 that rotatably supports the straightening plate 10 allows for smooth adjustment of the rotation position of the straightening plate 10.

[0055] [Detachable mechanism] Fig. 4 is a perspective view of the attachment / detachment mechanism 7 in a state in which the straightening plate 10 is engaged. Two double-headed arrows in Fig. 4 indicate the rotation direction of the shaft 111 and the rotation direction of the arm 9b, respectively. In the double-headed arrow indicating the rotation direction of the shaft 111, a first rotation direction indicates the direction in which the straightening plate 10 rotates downwardly to the range hood 1. A second rotation direction indicates the direction in which the straightening plate 10 rotates upwardly to the range hood 1.

[0056] The attachment / detachment mechanism 7 has one fixed hanger 8 and one hinge unit 9. The fixed hanger 8 is fixed to approximately the center of the rear edge portion 10a of the baffle plate 10. The hinge unit 9 is fixed to the rear inner wall portion of the lower panel 5 located rearward of the opening 5a. In the attachment / detachment mechanism 7, the baffle plate 10 can be attached and detached to the hood 2 with one fixed hanger 8 and one hinge unit 9. Therefore, in the range hood 1, the cumbersome adjustment of the mounting position of the baffle plate 10 is not required when attaching or detaching the baffle plate 10, improving the ease of attachment and detachment.

[0057] The hinge unit 9 has a joint portion 9a and a damper hinge 100. The damper hinges 100 are disposed on both longitudinal ends of the joint portion 9a. The damper hinges 100 are fixed to the rear inner wall portion of the lower panel 5, and thereby the hinge unit 9 is fixed to the rear inner wall portion of the lower panel 5. The damper hinges 100 rotatably support both ends of the joint portion 9a.

[0058] The fixed hanger 8 has an insertion portion 8a and a fixing portion 8b. The fixing portions 8b are arranged at both longitudinal ends of the insertion portion 8a. The fixing portion 8b is fixed to the straightening plate 10 so that the insertion portion 8a is located approximately in the center of the rear edge portion 10a of the straightening plate 10. The insertion portion 8a has an insertion hole for inserting the arm 9b and the fitting protrusion 9c of the joint portion 9a.

[0059] The joint portion 9a has two arms 9b and a fitting protrusion 9c. The two arms 9b control the engagement state between the joint portion 9a and the insertion portion 8a. More specifically, when the joint portion 9a is inserted into the insertion portion 8a, the arm 9b is rotated in the locking direction shown in FIG. 4 to engage the fixed hanger 8 with the hinge unit 9. This allows the baffle plate 10 to be attached to the range hood 1. When the fixed hanger 8 is engaged with the hinge unit 9, the arm 9b is rotated in the unlocking direction shown in FIG. 4 to release the engagement of the fixed hanger 8 with the hinge unit 9. This allows the baffle plate 10 to be removed from the range hood 1.

[0060] The damper hinge 100 has a shaft body 110 and a bearing body 120. In the damper hinge 100 shown in Fig. 4, a shaft portion 111 of the shaft body 110 and a housing 124 of the bearing body 120 are shown. The joint portion 9a is connected to the shaft body 110. The housing 124 of the bearing body 120 has a bearing hole BH. The shaft portion 111 of the shaft body 110 is rotatably fitted into the bearing hole BH.

[0061] In a state where the fixed hanger 8 is engaged with the hinge unit 9, the straightening plate 10 rotates in a first rotation direction and a second rotation direction by the damper hinge 100 via the fixed hanger 8 and the hinge unit 9. As described above, the first rotation direction is a rotation direction in which the straightening plate 10 is in an open state, and the second rotation direction is a rotation direction in which the straightening plate 10 is in a closed state. That is, the first rotation direction is a direction in which the straightening plate 10 rotates downward from the position P1 side toward the position P4 side in FIG. 1. The second rotation direction is a direction in which the straightening plate 10 rotates upward from the position P4 side toward the position P1 side in FIG. 1.

[0062] [Damper hinge] Fig. 5 is a perspective view showing the internal structure of the damper hinge 100. In Fig. 5, SC indicates the center line of the shaft portion 111. The center line SC is also the center line of the shaft body 110. The double-headed arrow in Fig. 5 indicates the width direction of the damper hinge 100.

[0063] As described above, the damper hinge 100 has the shaft body 110 and the bearing body 120. As shown in FIG. 5, the damper hinge 100 has a simple configuration without a viscous oil sealing mechanism or a clutch mechanism. Therefore, the damper hinge 100 is easier to assemble than conventional damper hinges. In the damper hinge 100, the shaft body 110 is configured to be connected integrally with the joint portion 9a. Note that in FIG. 5, the housing 124 of the bearing body 120 is omitted in order to show the internal structure of the damper hinge 100.

[0064] The shaft body 110 has a shaft portion 111, a disk portion 112, a tapered portion 113, a first recess 114, and a second recess 115. The shaft body 110 is connected to the joint portion 9a. The disk portion 112 and the tapered portion 113 are configured to protrude radially outward from the shaft portion 111. In the shaft body 110, the second recess 115 is formed at a position corresponding to the tapered portion 113 in the width direction of the damper hinge 100.

[0065] In the damper hinge 100, the shaft body 110 has two tapered portions 113, two first recesses 114, and two second recesses 115. More specifically, the shaft body 110 has a configuration in which the shaft portion 111, one tapered portion 113 (one second recess 115), one first recess 114, the disk portion 112, the other first recess 114, and the other tapered portion 113 (the other second recess 115) are arranged in this order from the shaft portion 111 with respect to the center line SC. That is, each of the two first recesses 114 is formed between the disk portion 112 and the tapered portion 113.

[0066] The bearing body 120 has a first elastic portion 121, a second elastic member 122, a plate portion 123, and a housing 124. The first elastic portion 121 and the plate portion 123 are disposed in the first recess 114. The first elastic portion 121 is disposed on the disk portion 112 side of the first recess 114 in the width direction of the damper hinge 100. The plate portion 123 is disposed on the tapered portion 113 side of the first recess 114 in the width direction of the damper hinge 100. The second elastic member 122 is disposed in the second recess 115.

[0067] Due to the rotation of the shaft portion 111, the plate portion 123 receives a pressing force from a tapered surface 113a (described later) of the tapered portion 113, which presses the plate portion 123 toward the disk portion 112. As a result, the first elastic portion 121 receives a pressing force from the plate portion 123, which presses the first elastic portion 121 toward the disk portion 112. As a result, the first elastic portion 121 comes into contact with the side surface 112a of the disk portion 112. This contact generates frictional resistance between the first elastic portion 121 and the side surface 112a, and the rotation of the shaft portion 111 is braked by the friction brake.

[0068] The plate portion 123 is made of a material that has a smaller friction resistance when it comes into contact with the tapered portion 113 than the first elastic portion 121. In the bearing body 120, the first elastic portion 121 and the second elastic member 122 are made of rubber. The plate portion 123 is made of metal or plastic.

[0069] The first recess 114 has a first braking surface 114a. The first braking surface 114a is disposed on the disk portion 112 side of the first recess 114 in the width direction of the damper hinge 100. A contact avoidance area CAA is provided on the tapered portion 113 side of the first braking surface 114a in the width direction of the damper hinge 100. The first braking surface 114a is disposed so that the bottom surface 121a of the first elastic portion 121 contacts the first braking surface 114a when the rectifying plate 10 is at position P3 in FIG. 1. This causes the rotation of the rectifying plate 10 from position P3 to position P4 to be braked by the contact brake.

[0070] In a state where the bottom surface 121a of the first elastic portion 121 is in contact with the first braking surface 114a, the plate portion 123 is prevented from contacting the first braking surface 114a due to the presence of the contact avoidance area CAA. That is, the first braking surface 114a is disposed at a position where it does not contact the plate portion 123 due to the downward rotation of the straightening vane 10. This makes it possible to prevent the plate portion 123 from colliding with the first braking surface 114a. As a result, damage and deformation of the plate portion 123 are suppressed.

[0071] The second recess 115 has a second braking surface 115a and a third braking surface 115b. The second braking surface 115a is disposed at a position where the bottom surface 122a of the second elastic portion 122 contacts the second braking surface 115a when the rectifying plate 10 is at the position P1 in FIG. 1. As a result, the rotation of the rectifying plate 10 from the position P1 to the upward side is braked by the contact brake. In addition, when the rectifying plate 10 rotates further upward from the position P1, the second elastic portion 122 is elastically deformed. Due to the elastic deformation of the second elastic portion 122, the rotation of the rectifying plate 10 from the position P1 to the upward side is braked by the elastic brake. This reduces the collision of the magnetic portion 11 with the lower panel 5. As a result, damage and deformation of the magnetic portion 11 and the lower panel 5 are suppressed.

[0072] The third braking surface 115b is disposed so that when the straightening plate 10 rotates from position P4 to the wall side with which the back surface of the range hood 1 contacts in FIG. 1, the bottom surface 122a of the second elastic portion 122 comes into contact with the third braking surface 115b. As a result, the rotation of the straightening plate 10 from position P4 to the wall with which the back surface of the range hood 1 contacts is braked by the contact brake. In addition, if the straightening plate 10 further rotates to the wall side with which the back surface of the range hood 1 contacts after the bottom surface 122a and the third braking surface 115b come into contact, the second elastic portion 122 is elastically deformed. Due to the elastic deformation of the second elastic portion 122, the rotation of the straightening plate 10 to the wall side with which the back surface of the range hood 1 contacts is braked by the elastic brake. As a result, the collision of the straightening plate 10 with the wall with which the back surface of the range hood 1 contacts is suppressed.

[0073] [Changes in state of shaft and bearing from position P1 to position P3] Fig. 6 is a perspective view for explaining the change in state of shaft body 110 and bearing body 120 due to rotation of shaft portion 111. Fig. 7 is a plan view for explaining the change in state of shaft body 110 and bearing body 120 in Fig. 6.

[0074] Figures 6(a) and 7(a) show the state of the shaft body 110 and the bearing body 120 when the straightening vane 10 is in position P1 in Figure 1. The double-headed arrows in Figures 6(a) and 7(a) indicate the rotation direction of the shaft portion 111. Figures 6(b) and 7(b) show the state of the shaft body 110 and the bearing body 120 when the straightening vane 10 is in position P3 in Figure 1. The double-headed arrows in Figures 6(b) and 7(b) indicate the rotation direction of the shaft portion 111. The arrow in Figure 7(b) indicates the pressing force applied to the first elastic portion 121.

[0075] As shown in Fig. 6(a), when the straightening vane 10 is in position P1, the bottom surface 122a of the second elastic portion 122 is in contact with the second braking surface 115a. As a result, further rotation of the shaft portion 111 in the second rotation direction is braked by a contact brake caused by the contact between the bottom surface 122a and the second braking surface 115a. Meanwhile, the bottom surface 121a of the first elastic portion 121 is not in contact with the first braking surface 114a. Also, the bottom surface 122a of the second elastic portion 122 is not in contact with the third braking surface 115b.

[0076] As shown in FIG. 7(a), the tapered portion 113 has a tapered surface 113a. The plate portion 123 is configured to cover the side surface 121b of the first elastic portion 121 on the tapered surface 113a side. That is, the plate portion 123 is arranged so that the side surface 121b of the first elastic portion 121 does not directly contact the tapered surface 113a. The tapered surface 113a is formed on the tapered portion 113 so that the distance between the side surface 112a of the disk portion 112 and the tapered surface 113a increases in the first rotation direction of the shaft portion 111. In other words, the tapered surface 113a is formed on the tapered portion 113 so that the distance between the side surface 112a of the disk portion 112 and the tapered surface 113a decreases in the second rotation direction of the shaft portion 111. In the first elastic portion 121, the side surface 121b is formed to follow the tapered surface 113a.

[0077] 7(a), when the straightening plate 10 is in position P1, the plate portion 123 is not in contact with the tapered surface 113a. That is, the first elastic portion 121 is not pressed by the tapered portion 113. Therefore, when the straightening plate 10 is in position P1, the braking force due to the contact friction brake caused by the contact between the first elastic portion 121 and the disk portion 112 against the rotation of the shaft portion 111 in the first rotation direction is small or not generated.

[0078] 6(b), when the straightening plate 10 is in position P3, the bottom surface 121a of the first elastic portion 121 is in contact with the first braking surface 114a. As a result, further rotation of the shaft portion 111 in the first rotation direction is braked by a contact brake caused by contact between the bottom surface 121a and the first braking surface 114a. On the other hand, when the straightening plate 10 is in position P3, the bottom surface 122a of the second elastic portion 122 is not in contact with either the second braking surface 115a or the third braking surface 115b.

[0079] As shown in FIG. 7(b), when the straightening vane 10 is at position P3, the tapered surface 113a of the tapered portion 113 is in contact with the plate portion 123. That is, the tapered surface 113a presses the first elastic portion 121 against the side surface 112a of the disk portion 112 via the plate portion 123. As a result, the side surface 121c of the first elastic portion 121 on the disk portion 112 side is in contact with the side surface 112a of the disk portion 112. As a result, friction is generated between the side surface 121c and the side surface 112a, and the rotation of the shaft portion 111 in the first rotation direction is braked by the friction brake.

[0080] As described above, plate portion 123 is made of a material that has a smaller friction resistance when it comes into contact with tapered portion 113 than first elastic portion 121. Therefore, plate portion 123 slides smoothly on tapered surface 113a, and can efficiently transmit the pressing force from tapered surface 113a to first elastic portion 121. As a result, the rotation of shaft portion 111 in the first rotation direction is efficiently braked by the friction brake.

[0081] As described above, the tapered surface 113a of the tapered portion 113 is formed in the tapered portion 113 so that the distance between the side surface 112a and the tapered surface 113a widens in the first rotation direction of the shaft portion 111 and narrows in the second rotation direction of the shaft portion 111. Therefore, as the rotation of the shaft portion 111 in the first rotation direction progresses, the pressure applied to the first elastic portion 121 increases. Therefore, as the rotation of the shaft portion 111 in the first rotation direction progresses, the braking force of the friction brake due to the contact between the side surface 121c and the side surface 112a increases. In other words, the braking force of the friction brake at the beginning of the rotation becomes smaller. This suppresses the collision of the straightening plate 10 with the wall that the back surface of the range hood 1 contacts, and enables the straightening plate 10 to rotate quickly at the beginning of the rotation.

[0082] [Changes in state of shaft and bearing from position P3 to position P4]

[0083] The range hood 1 is configured such that the normal rotation range of the baffle plate 10 is from position P1 to position P3 in FIG. 1. As described above, at position P1, further rotation of the shaft portion 111 in the second rotation direction is braked by a contact brake formed by the second elastic portion 122 and the second braking surface 115a. At position P2, rotation of the shaft portion 111 in the first rotation direction is braked by a friction brake formed by the first elastic portion 121 pressing against the disk portion 112. At position P3, further rotation of the shaft portion 111 in the first rotation direction is braked by a friction brake formed by the first elastic portion 121 pressing against the disk portion 112 and a contact brake formed by the first elastic portion 121 and the first braking surface 114a.

[0084] When the straightening plate 10 rotates forcefully in the first rotation direction, the straightening plate 10 may rotate further from position P3 toward position P4. In this case, there is a risk that the straightening plate 10 may collide with the wall that the back surface of the range hood 1 contacts. For this reason, the damper hinge 100 of the range hood 1 is configured to exert a strong braking force against the rotation of the straightening plate 10 from position P3 toward position P4.

[0085] Fig. 8 is a perspective view for explaining the change in state of shaft body 110 and bearing body 120 due to rotation of shaft portion 111 in the first rotation direction after contact braking between first elastic portion 121 and first braking surface 114a occurs. Fig. 9 is a side view for explaining the change in state of shaft body 110 and bearing body 120 in Fig. 8.

[0086] Figures 8(a) and 9(a) show the state of the shaft body 110 and the bearing body 120 when the straightening vane 10 is in position P3 in Figure 1. The double-headed arrows in Figures 8(a) and 9(a) indicate the rotation direction of the shaft portion 111. Figures 8(b) and 9(b) show the state of the shaft body 110 and the bearing body 120 when the straightening vane 10 is in position P4 in Figure 1. The double-headed arrows in Figures 8(b) and 9(b) indicate the rotation direction of the shaft portion 111.

[0087] The perspective view of the state of the shaft body 110 and the bearing body 120 shown in Fig. 8(a) is the same as the perspective view of the state of the shaft body 110 and the bearing body 120 shown in Fig. 6(b). The explanation of the state of the shaft body 110 and the bearing body 120 in Fig. 8(a) is omitted because it is the same as the explanation of Fig. 6(b) above.

[0088] FIG. 9(a) shows the positional relationship between the bottom surface 122a of the second elastic portion 122 and the second braking surface 115a and the third braking surface 115b of the second recess 115 when the straightening plate 10 is at position P3. As shown in FIG. 9(a), when the straightening plate 10 is at position P3, the bottom surface 122a of the second elastic portion 122 is in a state of not contacting either the second braking surface 115a or the third braking surface 115b. That is, when the straightening plate 10 is at position P3, no contact brake is generated due to contact between the bottom surface 122a of the second elastic portion 122 and the second braking surface 115a or the third braking surface 115b. Note that, as shown in FIG. 6(b), when the straightening plate 10 is at position P3, the bottom surface 121a of the first elastic portion 121 is in contact with the first braking surface 114a of the first recess 114.

[0089] As shown in FIG. 8(b), when the rectifying plate 10 is in position P4, the bottom surface 121a of the first elastic portion 121 is pressed against the first braking surface 114a and is in an elastically deformed state. As a result, further rotation of the shaft portion 111 in the first rotation direction is braked by an elastic brake due to the elastic deformation of the first elastic portion 121. That is, further rotation of the rectifying plate 10 in the first rotation direction from position P3 is braked by an elastic brake due to the elastic deformation of the first elastic portion 121. Note that when the rectifying plate 10 is in position P4, the plate portion 123 is located in the contact avoidance area CAA, and thus contact with the first braking surface 114a is avoided. As a result, damage and deformation of the plate portion 123 are suppressed.

[0090] As shown in Fig. 8(b) and Fig. 9(b), when the straightening plate 10 is in position P4, the bottom surface 122a of the second elastic portion 122 comes into contact with the third braking surface 115b. As a result, further rotation of the shaft portion 111 in the second rotation direction is braked by a contact brake caused by contact between the bottom surface 122a of the second elastic portion 122 and the third braking surface 115b of the second recess 115. In other words, further rotation of the straightening plate 10 in the first rotation direction from position P4 is braked by a contact brake caused by contact between the second elastic portion 122 and the third braking surface 115b. As a result, the collision of the straightening plate 10 with the wall that the back surface of the range hood 1 contacts is suppressed.

[0091] When the straightening plate 10 further rotates in the first rotation direction from the position P4, the bottom surface 122a of the second elastic portion 122 is pressed against the third braking surface 115b of the second recess 115, and the second elastic portion 122 is elastically deformed. Due to this elastic deformation of the second elastic portion 122, further rotation of the shaft portion 111 in the first rotation direction is braked by the elastic brake. This further suppresses the collision of the straightening plate 10 with the wall that the back surface of the range hood 1 contacts.

[0092] [Method of braking the rotation of the straightening plate in the first rotation direction] As described above, in the damper hinge 100, there are the following five braking means for braking the rotation of the shaft portion 111 in the first rotation direction.

[0093] First braking means: Friction brake by the first elastic portion 121 and the tapered portion 113 Second braking means: contact brake by the first elastic portion 121 and the first braking surface 114a Third braking means: Elastic brake by elastic deformation of the first elastic portion 121 Fourth braking means: contact brake between the second elastic portion 122 and the third braking surface 115b Fifth braking means: Elastic brake by elastic deformation of the second elastic portion 122

[0094] Table 1 shows the relationship between the rotational positions of the baffle plate 10 from position P1 to position P4 shown in FIG. 1 by the damper hinge 100 of the range hood 1, and the braking means and each braking step for the rotation of the baffle plate 10 in the first rotation direction.

[0095] [Table 1] * At position P1, the rotation of the straightening vane 10 in the second rotation direction is braked by a contact brake formed by the second elastic portion 122 and the second braking surface 115a.

[0096] As shown in Table 1, the damper hinge 100 is configured so that as the rotation of the straightening vane 10 in the first rotation direction progresses, the damper hinge 100 has an increased means for braking the rotation of the straightening vane 10 in the first rotation direction. In other words, the rotation of the straightening vane 10 in the first rotation direction is braked by the damper hinge 100 using a braking method including the following five steps.

[0097] First step: Friction braking by the first braking means Second step: friction braking by the first braking means and contact braking by the second braking means Third step: friction braking by the first braking means, contact braking by the second braking means, and elastic braking by the third braking means Fourth step: friction braking by the first braking means, contact braking by the second braking means, elastic braking by the third braking means, and contact braking by the fourth braking means. Fifth step: friction braking by the first braking means, contact braking by the second braking means, elastic braking by the third braking means, contact braking by the fourth braking means, and elastic braking by the fifth braking means.

[0098] In the method of braking the rotation of the straightening plate 10 in the first rotation direction by the damper hinge 100, the number of braking means increases as the rotation of the straightening plate 10 in the first rotation direction progresses. In addition, the friction brake by the first braking means, the elastic brake by the third braking means, and the elastic brake by the fifth braking means increase in braking force as the rotation of the straightening plate 10 in the first rotation direction progresses. That is, in the method of braking the rotation of the straightening plate 10 in the first rotation direction by the damper hinge 100, the braking force against the rotation of the straightening plate 10 in the first rotation direction increases with the transition from the first step to the fifth step. This suppresses the collision of the straightening plate 10 with the wall that the back surface of the range hood 1 contacts.

[0099] As described above, the method of braking the rotation of the straightening vane 10 in the first rotation direction by the damper hinge 100 provides a braking force that increases as the rotation of the straightening vane 10 in the first rotation direction progresses. Conversely, the method of braking the rotation of the straightening vane 10 in the first rotation direction by the damper hinge 100 provides a braking force that is small at the beginning of the rotation of the straightening vane 10 in the first rotation direction. Therefore, it is possible to quickly adjust the straightening vane 10 to a predetermined open state position.

[0100] [Variations] In the range hood 1 according to the present embodiment, the magnetic part 11 supports the straightening plate 10 on the lower panel 5, but the present invention is not limited to this. Instead of the magnetic part 11, a known mechanism for supporting the straightening plate in the open state in the closed state can be applied. Examples of the known mechanism include a latch mechanism and a screw mechanism.

[0101] In the range hood 1 according to the present embodiment, the baffle plate 10 is detachably engaged by the detachment mechanism 7, but the present invention is not limited to this. A known mechanism can be used as the baffle plate attachment mechanism. For example, the known mechanism includes a mechanism including a first attachment mechanism that engages the right side of the rear edge of the baffle plate and a second attachment mechanism that engages the left side.

[0102] In the damper hinge 100 according to this embodiment, the shaft body 110 has two tapered portions 113, two first recesses 114, and two second recesses 115, but the present invention is not limited to this. For example, the shaft body 110 may have one tapered portion 113, one first recess 114, and one second recess 115. From the viewpoint of the damping performance of the rotation of the shaft portion 111, it is preferable that the shaft body 110 has a plurality of tapered portions 113, first recesses 114, and second recesses 115.

[0103] In the damper hinge 100 according to this embodiment, the second recess 115 is formed at a position corresponding to the tapered portion 113, but the present invention is not limited to this. For example, the second recess 115 may be formed at a position corresponding to the disk portion 112.

[0104] In the damper hinge 100 according to this embodiment, the bearing body 120 has a plate portion 123 that covers the side surface 121b of the first elastic portion 121, but the present invention is not limited to this. For example, the bearing body 120 may have a configuration that does not have the plate portion 123. From the viewpoint of the efficiency of the friction brake by the first elastic portion 121, it is preferable that the bearing body 120 has the plate portion 123.

[0105] In the damper hinge 100 according to this embodiment, the bearing body 120 is configured to include the first elastic portion 121 and the second elastic portion 122, but the present invention is not limited to this. For example, the bearing body 120 may be configured not to include the second elastic portion 122. From the viewpoint of the damping performance of the rotation of the shaft portion 111, it is preferable that the bearing body 120 includes the first elastic portion 121 and the second elastic portion 122.

[0106] The damping means for the rotation of the shaft portion 111 in the first rotation direction by the damper hinge 100 according to this embodiment includes five damping means from the first damping means to the fifth damping means, but the present invention is not limited to this. The above damping means may include at least the first damping means. From the viewpoint of the damping performance of the rotation of the shaft portion 111, it is preferable that the above damping means include at least the first damping means and the second damping means.

[0107] [Additional Note] The embodiments disclosed herein are illustrative in all respects and are not restrictive. The scope of the present invention is defined by the claims rather than the above-described embodiments, and includes the meaning equivalent to the claims and all modifications within the scope thereof. [Industrial Applicability]

[0108] The damper hinge described above, which is capable of smoothly adjusting the rotation position, can be used not only as a range hood baffle plate, but also as a damper hinge for various opening and closing bodies such as toilet lids and toilet seats for Western-style toilets, and lids for electrical appliances and cabinets.

[0109] The above-described method of braking the rotation of the baffle plate, which enables smooth adjustment of the rotation position of the baffle plate and prevents the rear of the range hood from colliding with the wall in contact with it, can be applied to various range hoods equipped with a baffle plate. [Explanation of symbols]

[0110] 1. Range hood 2. Food 3. Blower box 4 Fans 5 Bottom Panel 5a opening 5b Magnetized part 6 Filters 7. Detachable mechanism 8 Fixed Hanger 8a Insertion part 8b Fixed part 9 Hinge unit 9a Joint 9b Arm 9c Fitting protrusion 10 Rectifier plate 10a Trailing edge 10b Leading edge 10c Right edge 10d left edge 11 Magnetized part 100 Damper Hinge 110 Shaft body 111 Shaft 112 Disk section 112a Side of the disk 113 Tapered section 113a Tapered surface 114 First recess 114a First braking surface 115 Second recess 115a Second braking surface 115b Third braking surface 120 Bearing body 121 First elastic part 121a: bottom surface of first elastic portion 121b: Side surface of the first elastic portion on the plate portion side 121c: a side surface of the first elastic portion on the disk portion side 122 Second elastic member 122a Bottom surface of second elastic member 123 Plate section 124 Housing BH bearing hole CAA contact avoidance area SC Center line of shaft

Claims

1. A shaft body having a shaft portion; a bearing body having a bearing hole into which the shaft portion is rotatably fitted; Equipped with The shaft body is A disk portion protruding radially outward from the shaft portion; a tapered portion that protrudes radially outward from the shaft portion and has a tapered surface that is inclined with respect to the rotation direction of the shaft portion on a surface that faces a side surface of the disk portion; a first recess formed between the disk portion and the tapered portion; having The tapered surface is formed on the tapered portion such that a distance between the side surface of the disk portion and the tapered surface increases in a first rotation direction of the shaft portion, the bearing body includes a first elastic portion disposed in the first recess, The tapered surface presses the first elastic portion against a side surface of the disk portion when the shaft portion rotates in a first rotation direction. Damper hinge.

2. The shaft body includes at least Two tapered portions disposed on both sides of the disk portion; two first recesses formed between the disk portion and the tapered portion; 2. The damper hinge of claim 1 having the following structure:

3. the bearing body has a plate portion disposed between the tapered surface and the first elastic portion of the first recess, The plate portion has a smaller friction resistance when in contact with the tapered surface than the first elastic portion, The tapered surface presses the first elastic portion against a side surface of the disk portion via the plate portion. The damper hinge of claim 2 .

4. the first recess has a first braking surface with which the first elastic portion comes into contact when the shaft portion rotates in the first rotation direction, The first braking surface brakes further rotation of the shaft portion in the first rotation direction by contacting the first elastic portion with the first braking surface. The damper hinge of claim 3.

5. The damper hinge according to claim 4 , wherein the first braking surface is disposed at a position not contacting the plate portion due to rotation of the shaft portion in the first rotation direction.

6. The shaft has a second recess, the bearing body has a second elastic portion disposed in the second recess, the second recess has a second braking surface with which the second elastic portion comes into contact when the shaft portion rotates in a second rotation direction opposite to the first rotation direction, The second braking surface brakes further rotation of the shaft portion in the second rotation direction by contacting the second elastic portion with the second braking surface.

6. The damper hinge of claim 5.

7. the second recess has a third braking surface with which the second elastic portion comes into contact when the shaft portion rotates in the first rotation direction, The third braking surface brakes further rotation of the shaft portion in the first rotation direction by contacting the second elastic portion with the third braking surface.

7. The damper hinge of claim 6.

8. The damper hinge according to claim 7, wherein the first braking surface is positioned at a position where the first elastic portion is pressed against the first braking surface and elastically deformed when the second elastic portion is in contact with the third braking surface.

9. A range hood comprising the damper hinge according to any one of claims 1 to 8 as a hinge for supporting a baffle plate so as to be rotatable in the vertical direction.

10. A method for damping the rotation of a straightening plate in a range hood having a damper hinge that supports the straightening plate so that the straightening plate can rotate in the vertical direction, comprising: The damper hinge comprises: A shaft body to which the flow straightening plate is fixed; a bearing body into which the shaft body is rotatably fitted and having an elastic portion that brakes the rotation of the shaft body; Equipped with In the rotation of the rectifying plate from the upper side to the lower side, a first step in which the rotation of the straightening plate is damped by frictional resistance between the shaft body and the elastic portion; a second step in which the rotation of the straightening plate is braked by frictional resistance and contact regulation between the shaft body and the elastic portion; A braking method having the following features.

11. The braking method according to claim 10, further comprising a third step of braking the rotation of the baffle plate by frictional resistance and contact regulation between the shaft body and the elastic portion, and elastic deformation of the elastic portion.

12. The elastic portion includes a first elastic portion and a second elastic portion, the first step in which the rotation of the straightening plate is damped by frictional resistance between the shaft body and the first elastic portion; the second step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion; the third step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion, and elastic deformation of the first elastic portion; a fourth step in which the rotation of the straightening plate is damped by frictional resistance and contact regulation between the shaft body and the first elastic portion, elastic deformation of the first elastic portion, and contact regulation between the shaft body and the second elastic portion; 12. The method of claim 11, comprising:

13. The braking method described in claim 12, further comprising a fifth step in which the rotation of the straightening plate is braked by frictional resistance and contact regulation between the shaft body and the first elastic portion, elastic deformation of the first elastic portion, contact regulation between the shaft body and the second elastic portion, and elastic deformation of the second elastic portion.

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