JP2005249020A - Positioning mechanism and rotary support mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a rotary support mechanism, keeping the relative angular displacement of two member rotatably coupled to each other without a hook, securing the relative angular displacement of two members 180° or more, and having excellent durability. <P>SOLUTION: Although first to third projecting parts 71, 73, 75 of a driving cam 33 are received by first to third recessed parts 51, 53, 55 of a fixed cam 31 to be positioned when the relative angle between the driving cam 33 and the fixed cam 31 is a reference angle, they are abutted on a first reference surface 65 of the fixed cam extending over 180°or more when the relative angle is any angle other than that. In that case, a rotating shaft 19 is included in the inside of a polygon M obtained by connecting three or more points belonging to the abutting part. Accordingly, the fixed cam 31 and the driving cam 33 can be prevented from being tilted by energizing force of a disc spring during the relative rotation. Thus, it is possible to decrease uneven abrasion of the fixed cam 31 and the driving cam 33 and abrasion of a shaft supporting the cams. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a positioning mechanism and a rotation support mechanism using the same.

  A notebook personal computer (hereinafter sometimes abbreviated as “notebook personal computer”) is known as an information processing apparatus or information terminal apparatus. In general, a notebook personal computer has a configuration in which a main body on which a computer unit or the like is mounted and a lid on which a liquid crystal display unit or the like is mounted are rotatably coupled using a hinge. In many of such devices, a hook is provided between the lid and the main body in order to maintain the closed state (see, for example, FIG. 1 of Patent Document 1).

  However, in order to open the lid of such a notebook computer, an operation of opening the lid while removing the hook by operating a slide type operation unit or the like is necessary, but this operation is complicated. Also, many notebook computers are required to be able to open the lid about 180 ° with respect to the main body. Of course, sufficient durability is required to withstand repeated opening and closing many times.

The present invention hooks the relative angular displacement of two members, such as a lid of a laptop computer, which can be rotated, in order to solve the problems of the conventional laptop computer and satisfy various requirements. A rotation support mechanism with excellent durability capable of maintaining a relative angular displacement of 180 ° or more that can be maintained without being used, and a positioning mechanism that can be used therefor are provided. For the purpose.
JP 2004-3594 A

  The present invention relates to a positioning mechanism, a first cam having a first cam surface supported so as to be relatively rotatable around a predetermined rotation axis and to be relatively movable in the direction of the rotation axis, and a second cam facing the first cam surface. A second cam having a cam surface, and biasing means for biasing the first and second cams in the direction of the rotation axis so that the first cam surface and the second cam surface are in contact with each other. The cam surface has a first reference surface and a recess formed in a direction away from the first reference surface to the second cam. The second cam surface is formed from the second reference surface and the second reference surface. And a convex portion formed in a direction approaching the first cam. The first cam surface and the second cam surface are second when the relative angular displacement of the first and second cams is a predetermined reference angle. The convex portion of the cam surface is received in the concave portion of the first cam surface, and the relative angular displacement has changed by 180 ° or more in the first direction from the substantially reference angle. Until the predetermined limit angle is reached, the convex portion of the second cam surface is not always received in the concave portion of the first cam surface, and the convex portion of the first reference surface of the first cam surface and the convex portion of the second cam surface. The rotation axis is included in a polygon obtained by connecting any three or more points belonging to the contact portion.

  The features of the present invention can be broadly shown as described above, but the configuration and contents thereof, together with the objects and features, will be further clarified by the following disclosure in view of the drawings.

  The positioning mechanism according to claim 1 includes a first cam having a first cam surface supported so as to be relatively rotatable about a predetermined rotation axis and to be relatively movable in the direction of the rotation axis, and a second cam facing the first cam surface. A second cam having a cam surface; and biasing means for biasing the first and second cams in the direction of the rotation axis so that the first cam surface and the second cam surface are in contact with each other. The first cam surface has a first reference surface and a recess formed in a direction away from the first reference surface to the second cam. The second cam surface has a second reference surface and a convex portion formed in a direction approaching the first cam from the second reference surface.

  The first cam surface and the second cam surface are configured such that the convex portion of the second cam surface is received in the concave portion of the first cam surface when the relative angular displacement of the first and second cams is a predetermined reference angle. ing. Further, the first cam surface and the second cam surface are always in contact with each other until the relative angular displacement of the first and second cams reaches a predetermined limit angle that is changed by approximately 180 ° or more in the first direction from the substantially reference angle. The convex portion of the two cam surfaces is not received in the concave portion of the first cam surface and belongs to a contact portion between the first reference surface of the first cam surface and the convex portion of the second cam surface. The rotation axis is included inside a polygon obtained by connecting points.

  According to this positioning mechanism, the first and second cams are positioned by receiving the convex portion of the second cam surface in the concave portion of the first cam surface when their relative angular displacement is a predetermined reference angle. Is done. The convex portion of the second cam surface is constituted by a top portion and an inclined surface that follows the top portion, and the concave portion of the first cam surface is constituted by a bottom portion and an inclined surface that follows the bottom portion. The relative rotation of the second cam is restrained by the rotation restraining force generated between the two inclined surfaces due to the biasing force of the biasing means.

  The positioning state can be released by applying a rotational force larger than the rotation suppression force to the first and second cams. After leaving the positioning state, the positioning is not performed until the relative angular displacement reaches a predetermined limit angle. That is, the first and second cams can be positioned only at one end point of the relative angular displacement while ensuring a relative angular displacement of 180 ° or more. By performing positioning only at one end point of the relative angular displacement, it is possible to halve the wear of the first and second cams caused by the positioning operation while securing the positioning at a necessary location.

  Further, while the first and second cams rotate relative to each other between the reference angle and the limit angle, any one of the three belonging to the contact portion between the first reference surface of the first cam surface and the convex portion of the second cam surface. The rotation axis is configured to be included in a polygon obtained by connecting points greater than or equal to the points. Therefore, it is possible to suppress the first and second cams from being inclined by the urging force of the urging means during the relative rotation. For this reason, it becomes easy to keep the rotation resistance by the friction obtained by contact | abutting with the 1st reference surface of a 1st cam surface, and the convex part of a 2nd cam surface constant. Further, since the uneven wear of the first reference surface of the first cam surface and the convex portion of the second cam surface and the wear of the first or second cam and the shaft or the like supporting the wear can be suppressed, the positioning mechanism Can further extend the service life.

  That is, it is possible to realize a positioning mechanism with excellent reliability and durability that can secure the relative angular displacement of two cams by 180 ° or more and can perform positioning only at one end point of the relative angular displacement. It becomes possible.

  In the positioning mechanism of the second aspect, the concave portion of the first cam surface is constituted by first to third concave portions having different shapes arranged at intervals of about 120 ° around the rotation axis. The convex portions of the second cam surface are first to third convex portions having different shapes arranged at approximately 120 ° intervals around the rotation axis, and the relative angular displacement of the first and second cams is The first to third convex portions are respectively received in the first to third concave portions at the reference angle.

  With this configuration, while the first and second cams rotate relative to each other between the reference angle and the limit angle, the first reference surface of the first cam surface and the convex portion of the second cam surface are all around the circumference. Since the first and second cams are in contact with each other at an angle that divides substantially in three equal parts, it is possible to further reliably prevent the first and second cams from being inclined by the urging force of the urging means. For this reason, it becomes easier to keep the rotational resistance due to the friction of the first and second cams constant, and the life of the positioning mechanism can be further extended.

  According to a third aspect of the present invention, there is provided a rotary support mechanism that supports the first and second members so that they can be positioned relative to each other around the rotation axis and can be rotated relative to each other using any one of the positioning mechanisms described above. . The first cam is supported so as not to rotate about the rotation axis with respect to the first member. The second cam is supported so as not to rotate about the rotation axis with respect to the second member.

  Further, the rotation support mechanism is configured such that when the relative angular displacement of the first and second cams exceeds the reference angle and reaches a first stop angle equal to or less than a limit angle, the first and second members are relatively moved in the first direction. First rotation blocking means for blocking rotation, and relative rotation in the second direction opposite to the first direction of the first and second members when the relative angular displacement of the first and second cams is substantially a reference angle Second rotation preventing means.

  Therefore, the first and second members whose relative rotation is allowed only within a certain angle range by the first and second rotation preventing means can be positioned only at one end of the allowable relative rotation range. A rotation support mechanism with excellent durability can be realized.

  According to a fourth aspect of the present invention, when the relative angular displacement of the first and second cams becomes the second stop angle between the invasion start angle and the reference angle, the first and second rotation preventing means causes the first and The relative rotation of the second member in the second direction is prevented. However, the invasion start angle is the first and second cams at the start of intrusion into the concave portion of the first cam surface by the convex portion of the second cam surface when the first and second cams rotate relative to each other in the second direction. The relative angular displacement of.

  When the relative angular displacement of the first and second cams reaches the second stop angle, the inclined surface that forms the convex portion of the second cam surface and the inclined surface that forms the concave portion of the first cam surface come into contact with each other. The first and second cams receive a relative rotational force in the second direction through these inclined surfaces in contact with each other. Therefore, the first and second members also receive a relative rotational force in the second direction. On the other hand, at this time, the relative rotation of the first and second members in the second direction is blocked by the second rotation blocking means. That is, at this time, the first and second members are in a state in which the relative rotation in the second direction is prevented while receiving the relative rotational force in the second direction. Accordingly, the first and second members can be more reliably positioned without any play between them.

  According to a fifth aspect of the present invention, the rotary support mechanism includes a shaft member having the rotary shaft as an axis. The shaft member is supported by one of the first and second members so as to be rotatable and the other non-rotatable. The first cam, the second cam, and the urging means are each inserted through the shaft member.

  Therefore, it is possible to realize a compact rotation support mechanism capable of positioning both the first and second members via the shaft member while being rotatably supported.

  In the rotation support mechanism according to the sixth aspect, one of the first member and the second member is a main body of the notebook personal computer and the other is a lid thereof. The first rotation preventing means includes a first stopper portion of the main body and a second stopper portion of the lid that come into contact with each other when the lid is fully opened. The second rotation preventing means is constituted by a third stopper portion of the main body that contacts each other when the lid is closed and a fourth stopper portion of the lid.

  Therefore, the lid can be kept closed without using a hook or the like, and the lid can be opened about 180 ° with respect to the main body, and has sufficient durability to withstand repeated opening and closing many times. A notebook personal computer can be realized.

  FIG. 1 is a perspective view showing a normal use state of a notebook computer 1 using a rotation support mechanism using a positioning mechanism according to an embodiment of the present invention. The notebook computer 1 has a configuration in which a main body 3 on which a computer unit or the like is mounted and a lid 5 on which a liquid crystal display unit or the like is mounted are rotatably coupled using a pair of right and left hinge devices 7 and 9.

  FIG. 2 is a side view (left side view) of the notebook computer 1 viewed from the direction II in FIG. However, for convenience of explanation, only the right hinge device 7 is shown, and the left hinge device 9 is not shown. The hinge device 9 on the left side has a mirror object configuration with the hinge device 7 on the right side. P1, P2, and P3 in FIG. 2 represent the maximum opening position (indicated by a one-dot chain line), the closed position (indicated by a two-dot chain line), and the normal use position (indicated by a solid line) with respect to the main body 3, respectively. The turning angle of the lid 5 from the closing position P2 to the maximum opening position P1 is about 180 °.

  When the lid 5 rotates about the rotation shaft 19 from the normal use position P3 in the R1 direction (counterclockwise in the figure) and reaches the maximum opening position P1, the stopper 11 which is the first stopper portion of the main body 3 And the stopper 13 which is the second stopper portion of the lid 5 are in contact with each other so that the lid 5 does not rotate further in the R1 direction. On the other hand, when the lid 5 rotates in the R2 direction (clockwise in the figure) from the normal use position P3 about the rotation shaft 19 to reach the closed position P2, a stopper 15 which is a third stopper portion of the main body 3 is provided. And the stopper 17 which is the fourth stopper portion of the lid 5 are in contact with each other so that the lid 5 does not rotate further in the R2 direction.

  FIG. 3 is a view of the hinge device 7 on the right side as viewed from the III direction in FIGS. 1 and 2. FIG. 4 is a view of the hinge device 7 as viewed from the II direction in FIGS. 1 and 3. As shown in FIG. 3, the hinge device 7 includes a shaft 21 that is a shaft member having the rotating shaft 19 as an axis.

  The shaft 21 includes a lid connecting part 41, a flange part 43, a fixed cam support part 45, and a drive cam support part 47. The lid connecting portion 41 is formed on one end side of the shaft 21, and a connecting groove 41 a for connecting to the lid 5 so as not to rotate relative to the lid 5 is provided at the foremost end thereof. When the lid 5 is assembled to the main body 3, the coupling groove 41 a and a coupling fitting (not shown) fixed to the lid 5 are fitted so as not to be relatively rotatable.

  The flange portion 43 is formed adjacent to the lid connecting portion 41. The fixed cam support portion 45 is formed in a columnar shape adjacent to the flange portion 43 and having a diameter smaller than that of the flange portion 43. The first sliding washer 23, the second sliding washer 25, the bracket 27, and the fixed cam 31 as the first cam are rotatably fitted in the fixed cam support portion 45 in this order.

  However, since the protrusion 23a provided on the first sliding washer 23 is fitted into the notch 43a provided on the flange 43, the first sliding washer 23 is supported by the shaft 21 so as not to rotate. Become. Further, since the protrusion 25a provided on the second sliding washer 25 is fitted into the notch 27c provided on the bracket 27, the second sliding washer 25 is supported by the bracket 27 so as not to rotate. .

  Further, the fixed cam 31 is fixed to the bracket 27 by passing the bolt 39 through the through hole 31 c (see FIG. 5A) provided in the fixed cam 31 and screwing it into the bracket 27. The bracket 27 includes a rising portion 27a provided with a through hole through which the shaft 21 is passed, and a base portion 27b orthogonal thereto. A pin 29 is fixed to the base 27 and a through hole (not shown) is provided. The pin 29 is inserted into an insertion hole (not shown) provided in the main body 3, and a bolt (not shown) is screwed into the main body 3 through the through hole, whereby the bracket 27 is fixed to the main body 3. Is done.

  The drive cam support 47 of the shaft 21 is formed in a columnar shape adjacent to the fixed cam support 45 and having a deformed cross section having a maximum passing dimension equal to or smaller than the diameter of the fixed cam support 45. In this embodiment, a substantially D-shaped cross section is adopted as the irregular cross section (see FIG. 4). The substantially D-shaped cross section includes a flat portion 47a obtained by cutting a part of a circle having a diameter slightly smaller than the diameter of the fixed cam support portion 45. A screw 47 b is formed in the vicinity of the end portion of the drive cam support portion 47 (that is, the other end side of the shaft 21).

  The drive cam support 47 is fitted with a drive cam 33 as a second cam and a plurality of disc springs 35 as biasing means in this order, and finally a nut 37 is screwed into the screw 47b. The biasing force by the spring 35 can be adjusted according to the screwing amount of the nut 37.

  The drive cam 33 is provided with a through hole 33a having substantially the same shape as the modified cross section of the drive cam support 47 (see FIG. 6A), and the drive cam support 47 is inserted into the through hole 33a. In this embodiment, a through hole (not shown) having substantially the same shape as the through hole 33a of the drive cam 33 is also provided at the approximate center of the disc spring 35, and the drive cam is supported in the through hole. Part 47 is inserted. Therefore, both the drive cam 33 and the disc spring 35 are supported so as not to rotate with respect to the shaft 21 and to be movable in the direction of the rotation shaft 19.

  Eventually, the first sliding washer 23, the drive cam 33, the disc spring 35, and the nut 37 are supported so as not to rotate with respect to the shaft 21, while the second sliding washer 25, the bracket 27, and the fixed cam 31 are attached to the shaft 21. On the other hand, it is supported rotatably. Further, all the members between the flange portion 43 of the shaft 21 and the nut 37 receive a biasing force in the direction of the rotating shaft 19 by the disc spring 35.

  Therefore, when the lid 5 rotates with respect to the main body 3, the first sliding washer 23, the drive cam 33, the disc spring 35, and the nut 37 are rotated around the rotation shaft 19 together with the shaft 21 fixed to the lid 5. While rotating, the second sliding washer 25 and the fixed cam 31 together with the bracket 27 fixed to the main body 3 do not rotate around the rotation shaft 19. For this reason, when the lid 5 rotates with respect to the main body 3, relative rotation occurs between the first sliding washer 23 and the second sliding washer 25 and between the fixed cam 31 and the drive cam 33.

  5A is a view of the fixed cam 31 as viewed from the II direction in FIG. 5B is a partial view of the fixed cam 31 as viewed from the VB direction of FIG. 5A. As shown in FIG. 5A, the fixed cam 31 includes a first cam surface 31b having a substantially hollow disk shape formed on the outer side of the through hole 31a centering on the rotary shaft 19, and a first cam surface 31b. A fixing portion 31d extending from a part is provided. The through hole 31a is a through hole for rotatably passing through the fixed cam support 45 of the shaft 21 described above. As described above, the fixing portion 31d is provided with a through hole (baka hole) 31c through which the screw portion of the bolt 39 is passed.

  The first cam surface 31b includes a first reference surface 65 (see FIG. 5B) and first recesses 51 formed in a direction away from the first reference surface 65 to the drive cam 33 (direction II in FIG. 3). A second recess 53 and a third recess 55 are provided. A second recess 53 and a third recess 55 are formed at positions rotated counterclockwise by 120 ° and 240 ° from the first recess 51, respectively. As shown in FIG. 5B, the first recess 51 has a substantially V-shaped or substantially inverted trapezoidal cross-section, and a pair of a predetermined angle connecting the bottom 67, the bottom 67, and the first reference surface 65. Inclined surfaces 69a and 69b (sometimes referred to as “inclined surface 69”). In this embodiment, the opening angles of the inclined surfaces 69a and 69b are substantially the same, and each is about 50 °, for a total of about 100 °. In addition, the depth of the 1st recessed part 51 is about 0.5 millimeters. The second concave portion 53 and the third concave portion 55 have the same configuration.

  More specifically, the first recess 51 is formed from the inner peripheral limit radius 57 centering on the rotation shaft 19 of the first cam surface 31 b to the outer peripheral limit radius 59. The second recess 53 is formed from the inner peripheral limit radius 57 to the first intermediate radius 61 between the inner peripheral limit radius 57 and the outer peripheral limit radius 59. The third recess 55 is formed from the second intermediate radius 63 that is substantially the same as the first intermediate radius 61 (that is, a radius that is the same as or slightly smaller than the first intermediate radius 61) to the outer peripheral limit radius 59.

  Here, the inner peripheral limit radius 57 represents the minimum limit position where the concave portion can be formed on the first cam surface 31b by a radius around the rotation shaft 19, and in this embodiment, a through hole is formed. The radius of 31a corresponds to this. The outer peripheral limit radius 59 is the maximum limit position where a recess can be formed on the first cam surface 31b, expressed by a radius centered on the rotary shaft 19. In this embodiment, the first cam surface The outer radius of 31b corresponds to this. In this embodiment, the first intermediate radius 61 and the second intermediate radius 63 are set to approximately ½ of the sum of the inner peripheral limit radius 57 and the outer peripheral limit radius 59.

  Moreover, what expressed the inner end and the outer end by the radius centering on the rotating shaft 19 about each recessed part which comprises the 1st cam surface 31b is defined as the minimum radius and the maximum radius of each recessed part. Under such a definition, for example, for the second recess 53, the minimum radius is the inner peripheral limit radius 57 and the maximum radius is the first intermediate radius 61.

  In this embodiment, the opening angles of the first recess 51 and the second recess 53 are set to approximately the same 20 °. Further, the opening angle of the third recess 55 is set to an angle larger than the opening angle of the first recess 51 and the second recess 53 (for example, about 60 times about 3 times). Here, the opening angle of the first recess 51 is an angle formed by boundary lines 67a and 67b between the bottom 67 of the first recess 51 and the inclined surfaces 69a and 69b. In this example, the boundary lines 67 a and 67 b are configured to pass through the rotation shaft 19. The opening angles of the second recess 53 and the third recess 55 are also defined in the same manner as in the case of the first recess 51.

  6A is a view of the drive cam 33 as seen from the direction opposite to the direction II in FIG. 6B is a partial view of the drive cam 33 as seen from the VIB direction of FIG. 6A. As shown in FIG. 6A, the drive cam 33 includes a substantially cam plate-shaped second cam surface 33 b formed outside the through hole 33 a centering on the rotary shaft 19 described above. As described above, the through-hole 33a is an irregular (non-circular) through-hole that is inserted into the drive cam support 47 of the shaft 21 so as not to rotate.

  The second cam surface 33b is a first convex portion 71 formed toward the second reference surface 85 (see FIG. 6B) and the direction approaching the fixed cam 31 from the second reference surface 85 (II direction in FIG. 3). , Second convex portion 73 and third convex portion 75. A second convex portion 73 and a third convex portion 75 are formed at positions rotated clockwise from the first convex portion 71 by 120 ° and 240 °, respectively. As shown in FIG. 6B, the first convex portion 71 has a substantially inverted V-shaped or substantially trapezoidal cross-sectional shape, and has a predetermined angle connecting the top portion 87, the top portion 87 and the second reference surface 85. A pair of inclined surfaces 89a and 89b (sometimes referred to as “inclined surface 89”) is provided.

  In this embodiment, the inclination angles of the inclined surfaces 89a and 89b are set to be substantially the same as the inclination angles of the inclined surfaces 69a and 69b of the corresponding first recess 51 of the fixed cam 31. That is, the inclination angles of the inclined surfaces 89a and 89b are about 50 °, and the angle formed between the inclined surfaces 89a and 89b is about 100 °. The height of the first convex portion 71 is also substantially the same as the depth of the first concave portion 51, that is, about 0.5 millimeters. The 2nd convex part 73 and the 3rd convex part 75 are the same structures.

  More specifically, the first convex portion 71 is formed from the inner peripheral limit radius 77 centering on the rotation shaft 19 of the second cam surface 33b to the outer peripheral limit radius 79. The second convex portion 73 is formed from the inner peripheral limit radius 77 to the first intermediate radius 81 between the inner peripheral limit radius 77 and the outer peripheral limit radius 79. The third convex portion 75 is formed from the second intermediate radius 83 that is substantially the same as the first intermediate radius 81 (that is, a radius that is the same as or slightly larger than the first intermediate radius 81) to the outer peripheral limit radius 79.

  Here, the inner peripheral limit radius 77 represents the minimum limit position at which the convex portion can be formed on the first cam surface 33b by the radius around the rotation shaft 19, and the inner peripheral limit radius of the fixed cam 31. It is set to be substantially the same as the radius 57 (that is, a radius that is the same as or slightly larger than the inner peripheral limit radius 57). Further, the outer peripheral limit radius 79 represents the maximum limit position where the convex portion can be formed on the second cam surface 33b by a radius around the rotation shaft 19, and the outer peripheral limit radius 59 of the fixed cam 31 is It is set to be substantially the same (that is, a radius that is the same as or slightly smaller than the outer peripheral limit radius 59). In this embodiment, the outer peripheral limit radius 79 corresponds to the radius of the second cam surface 33b. The first intermediate radius 81 and the second intermediate radius 83 are substantially the same as the first intermediate radius 61 of the fixed cam 31 (that is, the same radius as the first intermediate radius 61 or slightly smaller), and the fixed cam 31. Is set to be substantially the same as the second intermediate radius 63 (that is, a radius that is the same as or slightly larger than the second intermediate radius 63). In this embodiment, the first intermediate radius 81 and the second intermediate radius 83 are set to approximately ½ of the sum of the inner peripheral limit radius 77 and the outer peripheral limit radius 79.

  In addition, for the individual convex portions constituting the second cam surface 33b, the inner end and the outer end expressed by radii around the rotation shaft 19 are defined as the minimum radius and the maximum radius of each convex portion. . Under such a definition, for example, for the second protrusion 73, the minimum radius is the inner peripheral limit radius 77 and the maximum radius is the first intermediate radius 81.

  In this embodiment, the opening angles of the first to third convex portions 71, 73, 75 are substantially the same as the opening angles of the first to third concave portions 51, 53, 55 of the fixed cam 31. Here, the opening angle of the first convex portion 71 is an angle formed by the boundary lines 87a and 87b between the top portion 87 of the first convex portion 71 and the inclined surfaces 89a and 89b. In this example, the boundary lines 87 a and 87 b are configured to pass through the rotation shaft 19. The opening angle of the second convex part 73 and the third convex part 75 is also defined similarly to the case of the first convex part 71.

  As can be seen from FIGS. 5A and 6A, the first cam surface 31b of the fixed cam 31 and the second cam surface 33b of the drive cam 33 face each other (that is, with FIG. 6A facing down). The angle center line F of the first recess 51 centered on the rotation shaft 19 of the fixed cam 31 and the angle center line D of the first projection 71 centered on the rotation shaft 19 of the drive cam are overlapped. The first to third convex portions 71, 73, and 75 of the drive cam 33 are configured to be received in the first to third concave portions 51, 53, and 55 of the fixed cam 31, respectively. The relative angular displacement DA between the fixed cam 31 and the drive cam 33 in this state is called a reference angle. The relative angular displacement DA between the fixed cam 31 and the drive cam 33 is expressed by a line F indicating the angle center of the first concave portion 51 of the fixed cam 31 and a line D indicating the angle center of the first convex portion 71 of the drive cam. If it is expressed by an angle difference, the reference angle is “0 °”. FIG. 10A shows a state where the relative angular displacement DA of the fixed cam 31 and the drive cam 33 is the reference angle.

  As will be described later, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is substantially the reference angle in the first direction (the direction corresponding to the direction in which the lid 5 is opened with respect to the main body 3; the R1 direction in FIG. 2). The first to third concave portions 51, 53 of the fixed cam 31 are always in the first to third convex portions 71, 73, 75 of the drive cam 33 until reaching a predetermined limit angle changed by 180 ° or more. , 55 and any three or more points belonging to the contact portion between the first reference surface 65 of the fixed cam 31 and the first to third convex portions 71, 73, 75 of the drive cam 33. The rotary shaft 19 is included inside the polygon obtained by tying. FIG. 10B shows a state when the relative angular displacement DA of the fixed cam 31 and the drive cam 33 is the limit angle.

  Further, as can be seen from FIGS. 5A and 6A, the effective minimum angle A <b> 2 of the third protrusion 75 centered on the rotation shaft 19 of the drive cam 33 is the first recess 51 centered on the rotation shaft 19 of the fixed cam 31. This is configured to be larger than the effective maximum angle A1. The relative angular displacement DA between the fixed cam 31 and the drive cam 33 changes in the first direction from the reference angle (see FIG. 10A) toward the limit angle (see FIG. 10B). The 3rd convex part 75 is comprised so that the 1st recessed part 51 of the fixed cam 31 may be opposed (refer FIG. 7B).

  The effective minimum angle A2 of the third convex portion 75 centered on the rotation shaft 19 of the drive cam 33 is the portion of the third convex portion 75 of the drive cam 33 that overlaps the movement locus of the first concave portion 51 of the fixed cam 31. Among these, the range in which the top portion of the fixed cam 31 that can come into contact with the first reference surface 65 is indicated by an angle around the rotation axis 19 is indicated. The effective maximum angle A1 of the first recess 51 around the rotation shaft 19 of the fixed cam 31 is the portion of the first recess 51 of the fixed cam 31 that overlaps the movement locus of the third protrusion 75 of the drive cam 33. The range in which the third cam 75 of the drive cam 33 cannot be contacted is indicated by an angle around the rotation shaft 19.

  7A to 9B are diagrams for explaining the rotational positional relationship between the fixed cam 31 and the drive cam 33 during the operation of the hinge device 7. In each figure, the fixed cam 31 is represented by a solid line, and the drive cam 33 is represented by a two-dot chain line. The drive cam 33 is represented as a view of FIG. 6A viewed from the back. 7A, FIG. 7B, FIG. 8A, FIG. 8B, FIG. 9A, and FIG. 9B respectively show a state in which the lid 5 is opened to the maximum (180 °) with respect to the main body 3 (corresponding to the maximum opening position P1 in FIG. 2) Corresponds to the 120 ° open state (corresponding to the normal use position P3 in FIG. 2), 60 ° open state, 10 ° open state, 5 ° open state, and closed state (corresponding to the close position P2 in FIG. 2). doing.

  11A, 11B, and 11C respectively show a schematic diagram viewed from the XIA direction of FIG. 8B, a schematic diagram viewed from the XIB direction of FIG. 9A, and a schematic diagram viewed from the XIC direction of FIG. 9B.

  The operation of the hinge device 7 will be described based on FIGS. 7A to 9B and FIGS. 11A to 11C. As shown in FIG. 7A, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 185 ° when the lid 5 is opened to the maximum extent (180 °) with respect to the main body 3. The relative angular displacement DA (185 °) at this time corresponds to the first stop angle. The relative angular displacement DA when the lid 5 is opened 180 ° is set to 185 ° when the lid 5 is closed with respect to the main body 3 (the opening angle of the lid 5 is 0 °) as shown in FIG. 9B. This is because the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is set to 5 °. The reason for this will be described later.

  As shown in FIG. 7B, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 125 ° when the lid 5 is opened 120 ° relative to the main body 3. As shown in FIG. 8A, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 65 ° when the lid 5 is opened 60 ° relative to the main body 3. As shown in FIG. 8B, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 15 ° when the lid 5 is opened 10 ° with respect to the main body 3.

  7A to 8B, the first to third convex portions 71, 73, and 75 of the drive cam 33 are received in the first to third concave portions 51, 53, and 55 of the fixed cam 31, respectively. Obtained by connecting any three or more points belonging to the contact portion between the first reference surface 65 of the fixed cam 31 and the first to third convex portions 71, 73, 75 of the drive cam 33. A rotation axis 19 is included inside a polygon M (indicated by a thick broken line).

  Therefore, it is possible to prevent the fixed cam 31 and the drive cam 33 from being tilted by the biasing force of the disc spring 35 from the fully opened state where the lid 5 is opened 180 ° to the main body 3 to the state where the lid is opened 10 °. can do. For this reason, it is easy to keep the rotational resistance due to friction obtained by the contact between the first reference surface 65 of the fixed cam 31 and the first to third convex portions 71, 73, 75 of the drive cam 33 constant. For this reason, it becomes easy to stop and hold the lid 5 at an arbitrary position with respect to the main body 3 by using this frictional force. Further, uneven wear of the first reference surface 65 of the fixed cam 31 or the first to third convex portions 71, 73, 75 of the drive cam 33, the fixed cam 31 or the drive cam 33 and the shaft 21 supporting the same, etc. Since wear can be suppressed, the life of the hinge device 7 can be further extended.

  The state shown in FIG. 8B connects any three or more points belonging to the contact portion between the first reference surface 65 of the fixed cam 31 and the first to third convex portions 71, 73, 75 of the drive cam 33. This is a limit that the rotation axis 19 is included in the obtained polygon M. The positional relationship between the first concave portion 51 of the fixed cam 31 and the first convex portion 71 of the drive cam 33 in this state is shown in FIG. 11A. The top portion 87 of the first convex portion 71 of the drive cam 33 is slightly in contact with the end of the first reference surface 65 of the fixed cam 31.

  When the lid 5 is further closed from this state and the opening angle of the main body 3 and the lid 5 becomes 5 ° (that is, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 10 °), the fixed cam 31 and the drive are driven. The rotational position relationship with the cam 33 is as shown in FIG. 9A. At this point, the contact between the first to third protrusions 71, 73, 75 of the drive cam 33 and the first reference surface 65 of the fixed cam 31 is completed, and the first to third protrusions of the drive cam 33 are completed. 71, 73, and 75 start to enter the first to third recesses 51, 53, and 55 of the fixed cam 31, respectively. The relative angular displacement DA (10 °) at this time corresponds to the invasion start angle. The positional relationship between the first concave portion 51 of the fixed cam 31 and the first convex portion 71 of the drive cam 33 in this state is shown in FIG. 11B. The inclined surface 89 a of the first convex portion 71 of the drive cam 33 starts to contact the inclined surface 69 a of the first concave portion 51 of the fixed cam 31.

  In this state, for example, the inclined surface 89 a of the first convex portion 71 of the drive cam 33 is inclined by the biasing force of the disc spring 35 without applying much force to the lid 5. The surface 69a slides down and stops in a state where the lid 5 is completely closed, that is, in a state where the stopper 15 of the main body 3 and the stopper 17 of the lid 5 in FIG. FIG. 9B shows the rotational positional relationship between the fixed cam 31 and the drive cam 33 when the lid 5 is completely closed. At this time, the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is 5 °. The relative angular displacement DA (5 °) at this time corresponds to the second stop angle.

  The positional relationship between the first concave portion 51 of the fixed cam 31 and the first convex portion 71 of the drive cam 33 in this state is shown in FIG. 11C. While the inclined surface 89a of the first convex portion 71 of the drive cam 33 is in contact with the inclined surface 69a of the first concave portion 51 of the fixed cam 31, the top portion 87 of the first convex portion 71 of the drive cam 33 and the fixed cam 31 It can be seen that the bottom 67 of the first recess 51 is not in contact, and the second reference surface 85 of the drive cam 33 and the first reference surface 65 of the fixed cam 31 are not in contact.

  For this reason, the fixed cam 31 and the drive cam 33 are connected to each other via the inclined surface 89a of the first convex portion 71 of the drive cam 33 and the inclined surface 69a of the first concave portion 51 of the fixed cam 31 that are in contact with each other. Due to the urging force of 35, a relative rotational force in the second direction (that is, a direction corresponding to the R2 direction in FIG. 2) is received. Therefore, the main body 3 and the lid 5 also receive a relative rotational force in the second direction. On the other hand, as described above, the relative rotation of the main body 5 and the lid 3 in the second direction is prevented by the contact between the stopper 15 and the stopper 17. That is, at this time, the main body 3 and the lid 5 are in a state in which the relative rotation in the second direction is prevented while receiving the relative rotational force in the second direction. Therefore, the main body 3 and the lid 5 can be more reliably positioned without any play between them.

  10A and 10B, as described above, the fixed cam 31 and the drive cam 33 when the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is the reference angle (0 °) and the limit angle (225 °), respectively. FIG. In the hinge device 7, the range of the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is limited to 5 ° to 185 ° by two pairs of stoppers provided on the main body 3 and the lid 5. . However, since the limit angle of the fixed cam 31 and the drive cam 33 is 225 °, the setting is made with a considerable margin. If the position of the stopper is changed, the lid 5 can be opened (that is, rotated in the R1 direction) by about 40 ° from the position P1 in FIG. 2 while maintaining various effects of the present invention. It is also possible.

  The hinge device 7 in this embodiment corresponds to a positioning mechanism, and the configuration in which the stopper 11 of the main body 3 and the stopper 13 of the lid 5 and the stopper 15 of the main body 3 and the stopper 17 of the lid 5 are added to the hinge device 7 is a rotation support mechanism. Corresponding to

  In the above-described embodiment, the case where the fixed cam 31 and the drive cam 33 are provided with three concave portions and three convex portions having different shapes arranged at intervals of 120 ° has been described as an example. The present invention is not limited to this. For example, the interval between the three concave portions and the three convex portions of the fixed cam and the drive cam may be other than 120 °. Also, the number of concave and convex portions of the fixed cam and the drive cam may be two or less, for example, or four or more.

  12A to 14 are views showing examples of a fixed cam according to another embodiment of the present invention. Both are examples in which the number of concave and convex portions of the fixed cam and the drive cam is two. For convenience of explanation, only the concave portion of the fixed cam will be illustrated and described. When the relative angular displacement between the fixed cam and the drive cam is a reference angle, the drive cam has convex portions that are received in the concave portions of these fixed cams without excess or deficiency.

  The fixed cam 101 shown in FIG. 12A is provided at a position where the first concave portion 103 having the same size and shape as the third concave portion 55 of the fixed cam 31 of FIG. And a second recess 105. The second concave portion 105 has substantially the same opening angle as the first concave portion 103 and has the same inner peripheral limit radius 57 and first intermediate radius 61 as the second concave portion 53 of the fixed cam 31 of FIG.

  A fixed cam 111 shown in FIG. 12B is provided at a position where the first recess 113 having the same dimensions as the third recess 55 of the fixed cam 31 of FIG. And a second recess 115. The second recess 115 has the same size and shape as the first recess 51 of the fixed cam 31 of FIG.

  The fixed cam 121 shown in FIG. 13A is provided at a position where the second concave portion 125 having the same size and shape as the third concave portion 55 of the fixed cam 31 of FIG. 1st recessed part 123 provided. The first recess 123 is a recess formed obliquely from the inner peripheral limit radius 57 to the outer peripheral limit radius 59 as in the fixed cam 31 of FIG. When forming the oblique concave portion, it may be formed in an arc shape or a spiral shape as shown in the figure, but may be formed in a straight line shape.

  A fixed cam 131 shown in FIG. 13B is provided at a position where the second concave portion 135 having the same size and shape as the first concave portion 51 of the fixed cam 31 of FIG. The first recess 133 is provided. The 1st recessed part 133 is the same dimension shape as the 1st recessed part 123 of the fixed cam 121 of FIG. 13A.

  A fixed cam 141 shown in FIG. 14 is provided at a position where the first concave portion 143 having the same size and shape as the first concave portion 123 of the fixed cam 121 of FIG. 13A and the first concave portion 143 rotated by 180 ° with respect to the rotation shaft 19. And a second recess 145. The 2nd recessed part 145 has the 1st recessed part 143 and the dimension shape of a mirror surface object.

  Note that the number of the concave portions and the convex portions of the fixed cam and the driving cam may be one. Although not shown, for example, the concave portion of the fixed cam is formed in a single spiral shape around 360 °, and the convex portion of the drive cam is also formed in a helical shape that can be received without excess or shortage. .

  In the above-described embodiments, various dimensions including the opening angle of each concave portion in the fixed cam and the opening angle of each convex portion in the drive cam are illustrated, but these are merely examples. Of course, the present invention is not limited to those of these dimensions, and can take various values as required.

  In each of the above-described embodiments, the first cam is a fixed cam and the second cam is a drive cam. Conversely, the first cam may be a drive cam and the second cam may be a fixed cam.

  Further, in each of the above-described embodiments, when the relative angular displacement of the first and second cams becomes the second stop angle between the intrusion start angle and the reference angle, the first and second rotation preventing means cause the first and Although the second member is configured to be prevented from relative rotation in the second direction, the present invention is not limited to this. For example, when the relative angular displacement of the first and second cams becomes the reference angle, the second rotation preventing means may be configured to prevent the relative rotation of the first and second members in the second direction. it can.

  In each of the above-described embodiments, the hinge device used in the notebook computer has been described as an example. However, the present invention is not limited to this. The present invention can be applied to an information processing apparatus other than a notebook personal computer and a hinge apparatus for use in an information terminal. Furthermore, the hinge device according to the present invention is not limited to application to an information processing device or an information terminal. For example, the hinge device can be relatively swung within a predetermined angle, such as a main body, a lid, and a door. It can be used to rotatably support one member. Further, the positioning mechanism according to the present invention is applied to, for example, two members capable of continuously rotating in one direction or both directions, for example, positioning of a rotary switch, in addition to the two members relatively swingable within a predetermined angle. You can also Furthermore, this invention can also be grasped as follows.

(1) A first cam having a first cam surface supported so as to be relatively rotatable around a predetermined rotation axis and to be relatively movable in the direction of the rotation axis, and a second cam surface opposite to the first cam surface. Two cams, and biasing means for biasing the first and second cams in the direction of the rotation axis so that the first cam surface and the second cam surface are in contact with each other. A first reference surface, and a recess formed in a direction away from the first reference surface to the second cam. The second cam surface approaches the first reference cam from the second reference surface. The first cam surface and the second cam surface are convex portions of the second cam surface when the relative angular displacement of the first and second cams is a predetermined reference angle. Is received in the recess of the first cam surface, and the relative angular displacement reaches a predetermined limit angle that is changed by approximately 180 ° or more in the first direction from the reference angle. Until the convex portion of the second cam surface is always received in the concave portion of the first cam surface and at the contact portion between the first reference surface of the first cam surface and the convex portion of the second cam surface. A positioning mechanism configured to include the rotation shaft inside a polygon obtained by connecting any three or more points belonging to the above, (2) the concave portion of the first cam surface is centered on the rotation shaft A plurality of recesses having at least one of a minimum radius and a maximum radius centered on the rotation axis arranged at a predetermined angle are provided, and the convex portions of the second cam surface are arranged at a predetermined angle around the rotation axis. A plurality of convex portions having at least one of a minimum radius and a maximum radius centered on the rotation axis, wherein the relative angular displacement of the first and second cams corresponds to the first cam surface corresponding to the reference angle. A plurality of convex portions respectively received in the concave portions; In the process in which the relative angular displacement of the second cam changes from the reference angle toward the limit angle in the first direction, the specific convex portion has a minimum radius or a maximum radius smaller than that of the convex portion. A positioning mechanism, characterized in that the positioning mechanism is configured to oppose the concave portion.

(3) The positioning mechanism having the configuration of (1) above, wherein the concave portions of the first cam surface are a plurality of different effective maximum angles centered on the rotating shaft and arranged at a predetermined angle with respect to the rotating shaft. The convex portions of the second cam surface are a plurality of convex portions having different effective minimum angles centered on the rotational axis and spaced apart from each other by a predetermined angle with respect to the rotational axis. A plurality of convex portions respectively received in the concave portions of the first cam surface corresponding to the relative angular displacement of the two cams being the reference angle, with the rotation axis of the specific convex portion of the second cam surface as the center The effective minimum angle to be formed is larger than the effective maximum angle centered on the rotation axis of the specific recess of the first cam surface, and the relative angular displacement of the first and second cams is limited from the reference angle to the limit. In the process of changing in the first direction towards the angle Positioning mechanism, characterized in, that the specific convex portion is configured to face the specific recess.

(4) In the positioning mechanism having the configuration of (1) above, the recesses of the first cam surface are formed by first to third recesses having different shapes arranged at intervals of about 120 ° about the rotation axis. The convex portions of the second cam surface are first to third convex portions having different shapes and arranged at an interval of about 120 ° around the rotation axis, and the relative angles of the first and second cams. (5) the first recess is centered on the rotation axis of the first cam surface. The first to third projections are respectively received in the first to third recesses when the displacement is the reference angle. The second recess is formed from the inner periphery limit radius to the outer periphery limit radius, and is formed from the inner periphery limit radius to an intermediate radius between the inner periphery limit radius and the outer periphery limit radius. Is formed substantially from the intermediate radius to the outer peripheral radius limit, The first convex portion is formed from substantially the inner peripheral limit radius centered on the rotation axis of the second cam surface to the outer peripheral limit radius, and the second convex portion is approximately from the inner peripheral limit radius to approximately the The third convex portion is formed from substantially the intermediate radius to the outer peripheral limit radius, and the effective minimum angle about the rotation axis of the third convex portion is defined by the first concave portion. A relative angular displacement of the first and second cams is changed from the reference angle toward the limit angle in the first direction. A positioning mechanism, wherein the third convex portion is configured to face the first concave portion.

  Although the present invention has been described above as a preferred embodiment, the terminology has been used for description rather than limitation and departs from the scope and spirit of the present invention. Without departing from the scope of the appended claims.

It is a perspective view which shows the normal use state of the notebook personal computer 1 using the rotation support mechanism using the positioning mechanism by one Embodiment of this invention. It is the side view (left side view) which looked at the notebook personal computer 1 from the II direction of FIG. It is the figure which looked at the hinge apparatus 7 of the right side from the III direction of FIG. 1 and FIG. It is drawing which looked at the hinge apparatus 7 from the II direction of FIG. 1 and FIG. 5A is a view of the fixed cam 31 as viewed from the II direction in FIG. 5B is a partial view of the fixed cam 31 as viewed from the VB direction of FIG. 5A. 6A is a view of the drive cam 33 as seen from the direction opposite to the direction II in FIG. 6B is a partial view of the drive cam 33 as seen from the VIB direction of FIG. 6A. 7A and 7B are diagrams for explaining the rotational positional relationship between the fixed cam 31 and the drive cam 33 during the operation of the hinge device 7. 8A and 8B are diagrams for explaining the rotational positional relationship between the fixed cam 31 and the drive cam 33 during the operation of the hinge device 7. 9A and 9B are diagrams for explaining the rotational positional relationship between the fixed cam 31 and the drive cam 33 during the operation of the hinge device 7. FIG. 10A is a drawing showing the rotational positional relationship between the fixed cam 31 and the drive cam 33 when the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is a reference angle. FIG. 10B is a drawing showing the rotational positional relationship between the fixed cam 31 and the drive cam 33 when the relative angular displacement DA between the fixed cam 31 and the drive cam 33 is the limit angle. 11A, 11B, and 11C respectively show a schematic diagram viewed from the XIA direction of FIG. 8B, a schematic diagram viewed from the XIB direction of FIG. 9A, and a schematic diagram viewed from the XIC direction of FIG. 9B. FIG. 12A is a view showing an example of a fixed cam 101 according to another embodiment of the present invention. FIG. 12B is a view showing an example of a fixed cam 111 according to still another embodiment of the present invention. FIG. 13A is a view showing an example of a fixed cam 121 according to still another embodiment of the present invention. FIG. 13B is a view showing an example of a fixed cam 131 according to still another embodiment of the present invention. It is drawing which shows the example of the fixed cam 141 by other embodiment of this invention.

Explanation of symbols

19: Rotating shaft 31: Fixed cam 33: Drive cam 51: First concave portion 53: Second concave portion 55: Third concave portion 65: First reference surface 71: First convex portion 73: Second convex portion 75: Third convex portion M: Polygon Patent Applicant Hirokazu Sangyo Co., Ltd. Applicant Agent Patent Attorney Koichi Tagawa

Claims (6)

A first cam having a first cam surface supported so as to be relatively rotatable around a predetermined rotation axis and to be relatively movable in the direction of the rotation axis; and a second cam having a second cam surface opposed to the first cam surface; Urging means for urging the first and second cams in the direction of the rotation axis so that the first cam surface and the second cam surface are in contact with each other;
The first cam surface has a first reference surface and a recess formed in a direction away from the first reference surface to the second cam,
The second cam surface has a second reference surface and a convex portion formed in a direction approaching the first cam from the second reference surface,
In the first cam surface and the second cam surface, when the relative angular displacement of the first and second cams is a predetermined reference angle, the convex portion of the second cam surface is received in the concave portion of the first cam surface, and the relative angle The convex portion of the second cam surface is always not received in the concave portion of the first cam surface and the first displacement until the displacement reaches a predetermined limit angle that is changed from the reference angle by 180 ° or more in the first direction. The rotating shaft is configured to be included in a polygon obtained by connecting any three or more points belonging to the contact portion between the first reference surface of one cam surface and the convex portion of the second cam surface. ,
A positioning mechanism characterized by. The positioning mechanism of claim 1,
The concave portion of the first cam surface is composed of first to third concave portions having different shapes arranged at intervals of about 120 ° around the rotation axis,
The convex portions of the second cam surface are first to third convex portions having mutually different shapes arranged at approximately 120 ° intervals around the rotation axis, and the relative angular displacement of the first and second cams is The first to third protrusions respectively received in the first to third recesses at the reference angle;
It is characterized by. A rotation support mechanism that uses the positioning mechanism according to claim 1 to support the first and second members so that the first and second members can be positioned relative to each other around the rotation axis and can rotate relative to each other.
The first cam is supported so as not to rotate about the rotation axis with respect to the first member,
The second cam is supported so as not to rotate about the rotation axis with respect to the second member,
The first and second members prevent relative rotation of the first and second members in the first direction when the relative angular displacement of the first and second cams exceeds the reference angle and reaches a first stop angle equal to or less than the limit angle. One rotation prevention means,
Second rotation blocking means for blocking relative rotation of the first and second members in a second direction opposite to the first direction when the relative angular displacement of the first and second cams is substantially the reference angle;
Rotation support mechanism with In the rotation support mechanism of Claim 3,
When the first and second cams rotate relative to each other in the second direction, the relative angular displacement of the first and second cams at the start of the intrusion into the concave portion of the first cam surface by the convex portion of the second cam surface starts to enter. When the angle is defined, when the relative angular displacement of the first and second cams becomes a second stop angle between the entry start angle and the reference angle, the first and second members are rotated by the second rotation preventing means. That relative rotation in the second direction is prevented.
It is characterized by. The rotation support mechanism according to any one of claims 3 to 4,
A shaft member having the rotation axis as an axis, the shaft member including a shaft member that is rotatably supported on one of the first and second members and non-rotatably supported on the other,
The first cam, the second cam, and the urging means are each inserted through the shaft member;
It is characterized by. The rotation support mechanism according to any one of claims 3 to 5,
One of the first member and the second member is the main body of the notebook personal computer and the other is the lid,
The first rotation preventing means is constituted by a first stopper portion of the main body and a second stopper portion of the lid that come into contact with each other when the lid is fully opened,
The second rotation preventing means is constituted by the third stopper portion of the main body and the fourth stopper portion of the lid that contact each other when the lid is closed;
It is characterized by.

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