JP2009089942A - Reclining apparatus and manufacturing method of reclining apparatus - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve the calibration accuracy of a cylinder part and a circular hole formed at the center part of an external gear and an internal gear and to prevent play in a using state or the like in a taumel type reclining apparatus capable of stepless angle adjustment of a seat back. <P>SOLUTION: In the reclining apparatus wherein the external gear and the internal gear are provided on one and the other of a seat cushion and the seat back, the circular hole of a large diameter and the cylinder part of a small diameter provided with respective shafts as a center are formed on one and the other of the external gear and the internal gear, and the external gear and the internal gear are relatively swung and rotated while changing an engaging part by imparting rotating force to a pair of wedge-like members inserted between the inner surface of the circular hole and the outer surface of the cylinder part, at least one of the inner surface of the circular hole and the outer surface of the cylinder part is calibrated with a shaft determined by three or more different external gear engaging positions in a peripheral direction in the external gear or a shaft determined by three or more internal gear engaging positions in the peripheral direction in the internal gear as a reference. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a reclining device used in a vehicle or the like and a manufacturing method thereof, and more particularly to a taumel type reclining device that adjusts a tilt angle of a seat back steplessly and a manufacturing method thereof.

  A so-called taumel type reclining device has an external gear on one side and the other side of the pivot portion of the lower arm fixed to the seat cushion and the upper arm fixed to the seat back, and has more teeth than the external teeth of the external gear. An internal gear having internal teeth is fixed, and a rotating shaft coaxially and rotatably fitted to the external gear or the internal gear is used to connect either the external gear or the internal gear to the other shaft. By rotating and rotating relatively while changing the meshing portion to the center, the stepless angle adjustment of the seat back is made possible.

  More specifically, a circular hole is formed in one of the shaft portions of the external gear and the internal gear, and a cylindrical portion having an outer surface smaller in diameter than the circular hole is provided in the other shaft portion. In the state where the external gear and the internal gear mesh with each other, the center of the cylindrical portion is positioned eccentric to the center of the circular hole. Then, a pair of wedge members are inserted into the eccentric shaft space between the circular hole and the cylindrical portion. The pair of wedge-shaped members are biased in a direction in which the wedge is driven between the circular hole and the cylindrical portion, and the relative movement between the external gear and the internal gear is normally prohibited. On the other hand, when the wedge-shaped member is moved in the direction in which the wedge is pulled out against the urging force, relative movement between the external gear and the internal gear is allowed, and the angle of the upper arm relative to the lower arm can be changed.

As described above, in the external gear and the internal gear, the inner surface of the circular hole constituting the eccentric bearing surface for the wedge-shaped member and the outer surface of the cylindrical portion greatly affect the reclining operation and stability accuracy. It is required to form the part outer surface with high accuracy. In Patent Document 1, a cylindrical collar is provided at the center of the internal gear, and accuracy is obtained by concentrically calibrating the peripheral surface of the collar with reference to the tip circle of the internal tooth. .
JP-A-7-284422

  It is not the tooth tips but the side surfaces of the teeth that contact the internal gear and the external gear in contact with each other in the meshing state. Therefore, in the calibration based on the tip circle as in Patent Document 1, the accuracy of the eccentric bearing surface in the actual use state in which the inner teeth and the outer teeth mesh with each other is not guaranteed, and there is a possibility that rattling occurs. .

  Accordingly, the present invention provides a reclining device that improves the calibration accuracy of the cylindrical portion and the circular hole formed in the central portion of the external gear and the internal gear, and is less prone to error such as rattling in use, and a method of manufacturing the reclining device. The purpose is to provide.

  The present invention has been made paying attention to calibrating the outer surface of the cylindrical portion and the inner surface of the circular hole with reference to the external teeth and the internal teeth, which are actual meshing portions of the external gear and the internal gear. That is, according to the aspect of the reclining device, the external gear that is fixed to one of the seat cushion and the seat back at the center of tilting of the seat back and the external teeth of the external gear mesh with the external gear. Internal teeth having a larger number of teeth than the external teeth are formed, an internal gear fixed to the other of the seat cushion and the seat back, and one of the external gear and the internal gear are provided around the respective axes. It is inserted between the large-diameter circular hole and the cylindrical part having a smaller diameter than the circular hole, and the inner surface of the circular hole and the outer surface of the cylindrical part, and normally controls the relative movement of the external gear and the internal gear. In the reclining device comprising a pair of wedge-shaped members that relatively rotate and rotates the external gear and the internal gear while changing the meshing portion by applying a forward and reverse rotational force, Little external surface of cylindrical part Either of them is based on an axis determined by three or more meshing positions in the circumferential direction of the external teeth of the external gear or an axis determined by three or more meshing positions in the circumferential direction of the internal teeth of the internal gear. It is characterized by being calibrated.

  In the aspect of the manufacturing method of the reclining device having the external gear, the internal gear, the circular hole, the cylindrical portion, and the pair of wedge members, the external teeth of the external gear and the internal teeth of the internal gear are also provided. Engaging at least three positions different in the circumferential direction and holding the gears held around the axis determined by the three or more different engagement positions in the circumferential direction with respect to the cutting blade And rotating at least one of the inner surface of the circular hole and the outer surface of the cylindrical portion.

  In the step of holding at least one of the external teeth of the external gear and the internal teeth of the internal gear, the external gear provided with at least three divided portions that can be expanded and contracted in the rotational radial direction and at least one divided portion. Preferably, the external gear or the internal gear is held by a holding means having a holding tooth that can mesh with the external teeth of the external gear or the internal teeth of the internal gear.

  In the manufacturing method of the reclining device of the present invention, as a preparatory step of processing the inner surface of the circular hole and the outer surface of the cylindrical portion, the shape of the contact area between the inner surface of the circular hole and the outer surface of the cylindrical portion in the pair of wedge members is assembled. It is preferable to have a step of measuring before and a step of determining a diameter size of at least one of the outer surface of the cylindrical portion and the inner surface of the circular hole based on the measured value. Thereby, it is possible to save the trouble of preparing a plurality of wedge-shaped members of different sizes in advance and selecting and attaching a wedge-shaped member of an appropriate size at the time of assembly.

  According to the above reclining device and the manufacturing method thereof of the present invention, in the external gear and the internal gear, the outer surface of the cylindrical portion and the inner surface of the circular hole are finished on the basis of the external teeth and the internal teeth that are the meshing sites after assembly ( Calibration), the accuracy is high, and it is possible to prevent inconveniences such as looseness in use after assembly.

  With reference to FIGS. 1 to 5, a schematic configuration of a both Taumel type reclining device as an object of the present invention will be described. 1 is fixed to a frame (not shown) of a seat cushion by a bolt or the like. In the lower arm 10, there are six fitting holes 11 (two of which appear in FIG. 1) around the position of the seat back tilt center (the portion intersecting the seat back tilt center axis). It is drilled to be located on the same circumference.

  The upper arm 20 is fixed to a seat back frame (not shown) by bolts or the like. In the upper arm 20, there are six fitting holes 21 (two of which appear in FIG. 1) around the seat back tilt center position (a portion intersecting the seat back tilt center axis). It is drilled so as to be located on the same circumference.

  The gear mechanism 30 is mounted between the lower arm 10 and the upper arm 20 and adjusts the inclination angle of the upper arm 20. The lower arm 10 is fitted to the external gear 31 and the internal gear 32 in the gear mechanism 30. A plurality of fixing protrusions 31 a and 32 a that are fitted into the hole 11 and the fitting hole 21 of the upper arm 20 are provided.

  As shown in FIG. 4, the external gear 31 has a substantially disk shape, and an external tooth 31 b is formed on the outer peripheral surface, and a cylindrical portion 31 c is formed in the center. An annular recess 31d is formed around the cylindrical portion 31c. The external gear 31 is positioned by fitting six fixing protrusions 31 a formed on the side surface into the fitting hole 11 of the lower arm 10, and is welded to the lower arm 10 after this positioning.

  The internal gear 32 also has a substantially disk shape as shown in FIG. The internal gear 32 is engraved with internal teeth 32b that are inscribed with the external teeth 31b and that have at least one more tooth than the external teeth 31b of the external gear 31. A circular through hole (circular hole) 32 c is formed in the center of the internal gear 32. The through hole 32c is formed inside the cylindrical rib-shaped portion 32f, and an annular recess 32d is formed in a region between the cylindrical rib-shaped portion 32f and the internal teeth 32b. The internal gear 32 is positioned by fitting the six fixed protrusions 32 a on the side surface into the fitting holes 21 of the upper arm 20, and is welded to the upper arm 20 after this positioning.

  A cylindrical portion 33a of a cylindrical rotary shaft 33 with a flange shown in FIG. 3 is rotatably fitted in the cylindrical portion 31c of the external gear 31. An arcuate notch 33c is formed in the flange 33b of the rotating shaft 33. A connecting serration 33g is cut on the inner cylindrical surface of the cylindrical portion 33a.

  Between the inner surface (inner cylinder surface) of the through hole 32c of the internal gear 32 and the outer surface (outer cylinder surface) of the cylindrical portion 31c of the external gear 31, a pair of wedge members 35, 36 is inserted.

  The wedge-shaped members 35 and 36 have a plane-symmetric shape, and the inner cylindrical surfaces 35a and 36a of the wedge-shaped members 35 and 36 have inner diameters substantially the same as the outer diameter of the cylindrical portion 31c of the external gear 31, The outer cylindrical surfaces 35b and 36b of the wedge-shaped members 35 and 36 have outer diameters substantially the same as the inner diameter of the through hole 32c. The inner cylindrical surface 35a and the outer cylindrical surface 35b of the wedge-shaped member 35 are changed in a wedge shape because the center axes thereof do not coincide with each other. Similarly, the inner cylindrical surface 36a and the outer cylindrical surface 36b of the wedge-shaped member 36 are changed in a wedge shape because the center axes thereof do not coincide with each other.

  Stepped recesses 35c and 36c are formed on the end surfaces of the thin-walled areas of the wedge-shaped members 35 and 36, and the flange portion 33b of the rotary shaft 33 projects into this space. Therefore, when the rotating shaft 33 rotates counterclockwise in FIG. 2, the side wall 33e of the notch 33c of the rotating shaft 33 comes into contact with the side wall 35e of the recess 35c of the wedge-shaped member 35. When rotating clockwise in FIG. 2, the side wall 33f of the notch 33c of the rotating shaft 33 contacts the side wall 36e of the recess 36c of the wedge-shaped member 36 on the opposite side.

  The wedge-shaped members 35, 36 are arranged between the inner surface of the through hole 32 c of the internal gear 32 and the outer surface of the cylindrical portion 31 c of the external gear 31 so that the thick side faces each other. The internal gear 32 is eccentric, and the internal teeth 32b are engaged with the external teeth 31b. By the wedge-shaped members 35 and 36, the rotary shaft 33 can mesh the internal teeth 32b and the external teeth 31b, and can relatively rotate and rotate the external gear 31 and the internal gear 32 while changing the meshing portion. The wedge-shaped members 35 and 36 receive a biasing force in a direction away from each other from a spring 37 as an elastic member.

  The spring 37 includes a one-turn annular portion 37a and spring ends 37b and 37c rising from the annular portion 37a. The annular portion 37a is an annular step formed by the cylindrical rib-like portion 32f of the internal gear 32. Supported within the department. The spring end portions 37b and 37c protrude from the annular portion 37a toward the lower arm 10 (the right direction in FIG. 1), and the spring end portion 37b is formed on the side end surface of the wedge-shaped member 35 on the thick side. The spring end portion 37 c is locked to the groove portion 36 d formed on the side end surface on the thick side of the wedge-shaped member 36.

  The cylindrical pressing member 38 is fitted to the outer peripheral surface of the internal gear 32, and both end portions thereof protrude toward the central axis, and sandwich the external gear 31 and the internal gear 32 (see FIG. 1). Thereby, it can control that the external gear 31 and the internal gear 32 leave | separate in an axial direction. An annular groove 33d is cut at the tip of the rotary shaft 33, and a retaining ring 39 is locked there.

  In the above reclining device, a pair is symmetrically arranged on both sides of each seat, and the left and right rotary shafts 33 are connected via a connecting shaft 13 (FIG. 1) inserted and fixed between serrations 33g of the cylindrical part 33a. Are connected. The connecting shaft 13 and the rotating shaft 33 are rotationally driven when adjusting the inclination angle of the seat back.

  In the above reclining device, the spring 37 biases the wedge-shaped members 35 and 36 away from each other in a state in which no rotational operation force is applied to the connecting shaft 13 (the rotating shaft 33) from the outside, and both the wedge-shaped members 35 and 36 are urged. Is given the force in the direction of driving the wedge. Therefore, relative movement between the internal gear 32 and the rotary shaft 33 is prohibited, the gear mechanism 30 is in a locked state, and the seat back is locked at that position.

  In this locked state, when the rotary shaft 33 is rotated, for example, counterclockwise in FIG. 2, a force in the direction of pulling the wedge-shaped member 35 from the gap from the side wall 33 e of the rotary shaft 33 to the side wall 35 e of the wedge-shaped member 35 acts. The wedge-shaped member 35 rotates counterclockwise with respect to the internal gear 32. As a result, a gap is generated between the wedge-shaped member 35 and the peripheral member, and the internal gear 32 can be moved. Then, the wedge-shaped member 36 receiving the urging force of the spring 37 rotates counterclockwise so as to fill this gap.

  By this interlocking operation, the wedge-shaped members 35 and 36 rotate counterclockwise together with the rotating shaft 33. The same applies to the clockwise rotation. Therefore, the internal gear 32 is supported by the rotary shaft 33 at an eccentric position where the internal teeth 32b mesh with the external teeth 31b, and the external gear 31, the internal gear 32, and the rotary shaft 33 constitute a gear mechanism. Will be. Thus, by rotating the rotary shaft 33, the gear mechanism 30 is changed from the locked state to the unlocked state, and the internal gear 32 is relatively swung while changing the meshing portion around the axis of the external gear 31. By rotating, the upper arm 20 can be tilted with respect to the lower arm 10, and the inclination angle of the seat back can be adjusted.

  In the gear mechanism 30, stopper protrusions 31 e and 32 e are provided on the external gear 31 and the internal gear 32 in order to regulate the maximum tilt angle of the upper arm 20 with respect to the lower arm 10. The stopper projection 31e of the external gear 31 protrudes into the recess 31d from the inner peripheral portion of the external tooth 31b toward the cylindrical portion 31c, and the stopper projection 32e of the internal gear 32 is formed on the cylindrical rib-shaped portion 32f. It protrudes in the recessed part 32d toward the internal tooth 32b side from an outer peripheral part. When a predetermined amount of relative rotation occurs between the external gear 31 and the internal gear 32, the side surfaces of the stopper protrusions 31e and 32e come into contact with each other to restrict the rotational operation and limit the further angle change of the seat back. Is done.

  In the reclining device configured as described above, the outer surface of the cylindrical portion 31c of the external gear 31 and the inner surface of the through hole 32c of the internal gear 32 are respectively connected to the inner cylindrical surfaces 35a, 36a of the wedge-shaped members 35, 36. It functions as a bearing surface in contact with the outer cylindrical surfaces 35b and 36b. Therefore, the outer surface of the cylindrical portion 31c and the inner surface of the through hole 32c are highly accurate in order to prevent rattling and loosening between the wedge-shaped members 35 and 36 when the outer teeth 31b and the inner teeth 32b are engaged. It needs to be formed. The external gear 31 and the internal gear 32 of the present embodiment are not the tip circles of the external teeth 31b and the internal teeth 32b, but the side surfaces of the external teeth 31b and the internal teeth 32b that are actual contact portions when the gears are engaged. High accuracy is obtained by calibrating the cylindrical portion 31c and the through hole 32c with reference to the portion.

  Specifically, when calibrating the outer surface of the cylindrical portion 31c of the external gear 31, a clamp jig 40 shown in FIG. 6 is used. The clamp jig 40 has a cylindrical chuck 42 protruding from the main body 41. The chuck 42 is rotatable about a rotation axis 42 x and is composed of three partial annular body expansion / contraction portions (divided portions) 43 divided in the rotation direction by a gap 45, and a circle communicating with the gap 45 at the center. A central opening 44 having a shape is formed. Each expansion / contraction portion 43 is supported in such a manner as to increase or decrease the interval of the gap 45 so as to be movable in the rotational radius direction around the central opening 44, and 3 by an actuator (not shown) provided in the main body portion 41. The two expansion / contraction portions 43 are expanded / contracted in the rotational radius direction. Each of the three expansion / contraction portions 43 has an annular flange 43a located on the same circumference centering on the rotation shaft 42x, and an annular recess 43b is formed inside the annular flange 43a. Holding teeth 43c project from the inner peripheral surface of each annular flange 43a facing the recess 43b toward the center opening 44 side. Each of the expanding / contracting portions 43 is provided with one holding tooth 43c, and the total three holding teeth 43c are arranged at approximately equal intervals in the circumferential direction around the central opening 44. The holding teeth 43 c are formed in the same shape as one of the internal teeth 32 b of the internal gear 32 and can mesh with the external teeth 31 b of the external gear 31.

  When machining the outer surface of the cylindrical portion 31c, the external gear 31 with the external teeth 31b formed is fitted into the concave portion 43b of the chuck 42 so that the concave portion 31d faces outward (opposite the chuck 42) ( (See FIG. 6) The three expansion / contraction portions 43 are moved in the diameter reduction direction. Then, as shown in FIG. 8, the three holding teeth 43 c provided in the expansion / contraction part 43 are engaged with the external teeth 31 b, respectively, and the external gear 31 is in engagement with the chuck 42 at three positions different in the circumferential direction. Held in. In this way, with the external gear 31 set in the clamp jig 40, the chuck 42 is driven to rotate about the rotation shaft 42x, and the outer surface of the cylindrical portion 31c is calibrated by cutting with a cutter (cutting blade) 46.

  As can be seen from FIG. 9 in which the holding state of the external gear 31 by the chuck 42 is enlarged, both side surfaces of the holding teeth 43c are in contact with the side surfaces of the two adjacent external teeth 31b, while the holding teeth 43c The tip portion is not in contact with the valley portion of the external tooth 31b, and the inner peripheral surface of the annular flange 43a is also separated from the tooth tip of the external tooth 31b. That is, the chuck 42 holds the external gear 31 with the side meshing surface of the external tooth 31b as a position reference surface. Since the external teeth 31b are held by the holding teeth 43c at three different positions in the circumferential direction, the axial position of the external gear 31 with respect to the chuck 42 is determined. At this time, unlike the case of using the tip circle of the outer teeth 31b as a reference, the same axial position as the actual use state when the outer teeth 31b mesh with the inner teeth 32b is obtained. By rotating the external gear 31 around the center and cutting, the outer surface of the cylindrical portion 31c can be calibrated with high accuracy without causing play or looseness when the gear mechanism 30 is assembled.

  When the calibration work of the through hole 32c of the internal gear 32 is performed, a clamp jig 50 shown in FIG. 7 is used. The clamp jig 50 has a cylindrical chuck 52 protruding from the main body 51. The chuck 52 is rotatable about a rotation shaft 52 x and is composed of three expansion / contraction portions (divided portions) 53 divided in the rotation direction by the gap 55, and a circular central opening communicating with the gap 55 at the center. A portion 54 is formed. Each of the expansion / contraction portions 53 is supported so as to be movable in the direction of the rotation radius around the central opening 54 in such a manner as to increase or decrease the interval of the gap 55, and 3 by an actuator (not shown) provided in the main body 51. The two expansion / contraction portions 53 are expanded / contracted in the rotational radius direction. Each of the three expansion / contraction portions 53 is formed of a partial annular body located on the same circumference with the rotation axis 52x as the center, and the outer peripheral surface of each expansion / contraction portion 53 is in the outer diameter direction opposite to the central opening 54. Holding teeth 53a are provided so as to project. One holding tooth 53a is provided in each expansion / contraction part 53, and the three holding teeth 53a in total are arranged at substantially equal intervals in the circumferential direction centering on the central opening 54. The holding teeth 53 a are formed in the same shape as one of the external teeth 31 b of the external gear 31 and can mesh with the internal teeth 32 b of the internal gear 32.

  When machining the inner surface of the through hole 32c, the internal gear 32 with the internal teeth 32b formed is fitted into the chuck 52 so that the recess 32d faces the end face side of the expansion / contraction part 53 (see FIG. 7). The two expansion / contraction portions 53 are moved in the diameter expansion direction. Then, as shown in FIG. 10, the three holding teeth 53 a provided in the expansion / contraction part 53 mesh with the internal teeth 32 b, respectively, and the internal gear 32 engages with the chuck 52 at three positions in the circumferential direction. Supported by In this way, with the internal gear 32 set in the clamp jig 50, the chuck 52 is driven to rotate about the rotation shaft 52x, and the inner surface of the through hole 32c is calibrated by cutting with a cutter (cutting blade) 56.

  As can be seen from FIG. 11 in which the holding state of the internal gear 32 by the chuck 52 is enlarged, both side surfaces of the holding teeth 53a are in contact with the side surfaces of the two adjacent internal teeth 32b, while the holding teeth 53a The tip portion is not in contact with the valley portion of the internal tooth 32b, and the outer peripheral surface of the expansion / contraction portion 53 is also separated from the tooth tip of the internal tooth 32b. That is, the chuck 52 holds the internal gear 32 with the side meshing surface of the internal tooth 32b as a position reference surface. Since the holding of the internal teeth 32b by the holding teeth 53a is performed at three different positions in the circumferential direction, the axial position of the internal gear 32 with respect to the chuck 52 is determined. At this time, unlike the case where the tip circle of the internal tooth 32b is used as a reference, the same axial position as the actual use state when the internal tooth 32b meshes with the external tooth 31b is obtained. By rotating the internal gear 32 around the center and cutting, it is possible to calibrate the inner surface of the through hole 32c with high accuracy that does not cause looseness or looseness when the gear mechanism 30 is assembled.

  Theoretically, as long as the external teeth 31b and the internal teeth 32b are held at at least three positions in the circumferential direction (rotation direction), the two-dimensional of the external gear 31 and the internal gear 32 that are the holding targets. Therefore, both the clamp jig 40 and the clamp jig 50 of the illustrated embodiment are provided with three holding teeth 43c and 53a with different positions in the circumferential direction. However, when the accuracy error of each holding tooth or gear tooth is taken into account, the more the holding position in the circumferential direction, the higher the accuracy of the shaft position in terms of the greatest common divisor. The tool 50 may be provided with any number of four or more holding teeth 43c and 53a having different circumferential positions.

  The cylindrical portion 31c of the external gear 31 has a rough shape formed by burring, and finishes (calibrates) the outer surface by cutting using the clamp jig 40 and the cutter 46 as described above. Moreover, in the internal gear 32, the finishing process of the inner surface of the through hole 32c is performed on the through hole 32c formed in the central portion of the cylindrical rib-shaped portion 32f by cutting using the clamp jig 50 and the cutter 56 described above. Perform (calibration). At this time, an appropriate fitting clearance can be obtained between the wedge-shaped members 35 and 36 so that the wedge-shaped members 35 and 36 inserted between the cylindrical portion 31c and the through hole 32c can properly function as wedges. Thus, the shape of the wedge-shaped members 35, 36 (the width between the inner cylindrical surfaces 35a, 36a and the outer cylindrical surfaces 35b, 36b, the diameter size and the curvature of the inner cylindrical surfaces 35a, 36a and the outer cylindrical surfaces 35b, 36b) ), The outer diameter size (cutting amount) of the cylindrical portion 31c and the inner diameter size (cutting amount) of the through-hole 32c are adjusted.

  FIG. 12 shows the concept of adjusting the amount of cutting in the through hole 32c. The through hole 32c has an inner diameter size indicated by a one-dot chain line N1 in FIG. 12 in an initial stage where the cutting process is not performed. The designed inner diameter size of the through hole 32c is defined as a solid line N2 in FIG. If the shape of the wedge-shaped members 35, 36, particularly the outer diameter size and curvature of the outer cylindrical surfaces 35b, 36b are as designed, the wedge-shaped members 35, 36 are assembled by cutting the inner surface of the through hole 32c to the N2 position. In this state, the outer cylinder surfaces 35b and 36b and the inner surface of the through hole 32c can be fitted without play.

  FIG. 14 shows a comparative example in which the wedge-shaped member fitting clearance is larger than the design value. In FIG. 14, the outer surface of the cylindrical portion 31c ′ and the inner surface of the through hole 32c ′ are not processed for adjusting the engagement accuracy with the wedge, and the respective diameter sizes are constant. The rotating shaft 33 'indicated by a two-dot chain line has side walls 33e' and 33f 'for transmitting a rotational force to one and the other of the pair of wedge members 35' and 36 '. In the wedge-shaped member 36 ', the clearance of the inner cylindrical surface 36a' with respect to the outer surface of the cylindrical portion 31c 'and the clearance of the outer cylindrical surface 36b' with respect to the inner surface of the through hole 32c 'are formed as designed values. By pressing the groove 36d 'in the rotational direction, the wedge is held in the illustrated position. At this time, the wedge-shaped member 36 ′ has one side end wall 36 e ′ in the circumferential direction opposed to the side wall 33 f ′ of the rotating shaft 33 ′, but is not in contact with the side wall 33 f ′, but the cylindrical portion 31 c. 'And the inner cylindrical surface 36a' and the outer cylindrical surface 36b 'are held in contact with the inner surface of the through hole 32c'. On the other hand, in the wedge-shaped member 35 ′, the clearance between the outer surface of the cylindrical portion 31c ′ and the inner cylindrical surface 35a ′ and between the inner surface of the through hole 32c ′ and the outer cylindrical surface 35b ′ is larger than the design value. When the groove portion 35d 'is pressed in the rotational direction by a spring (not shown), as shown in FIG. 14, it tends to move further in the wedge driving direction than the proper press-fitting position. That is, in FIG. 14, the rotary shaft 33 'is virtually shown. However, when the rotary shaft 33' is actually attached, the wedge-shaped member 35 'has an outer surface of the cylindrical portion 31c' and an inner surface of the through hole 32c '. One side end wall 35e 'in the circumferential direction is brought into contact with the side wall 33e' of the rotary shaft 33 'without being fully press-fitted in between. Then, the wedge-shaped member 35 ′ does not serve as a wedge that restricts the relative rotation of the external gear 31 and the internal gear 32. On the contrary, the wedge-shaped members 35 ′ and 36 ′ are not fitted into the cylindrical portion 31 c ′ and the through-hole 32 c ′ because the fitting clearance is too small, and it becomes difficult to insert the wedge-shaped members 35 ′ and 36 ′. It may be impossible to do it.

  In the present embodiment, when the wedge-shaped member 35 or the wedge-shaped member 36 has a shape that causes the fitting clearance to be larger than the design value, like the wedge-shaped member 35 'of FIG. 14, the two-dot chain line N3 of FIG. As described above, the amount of cutting from the initial opening diameter N1 is reduced to make the inner diameter size of the through hole 32c smaller than the design value N2, thereby narrowing the space between the inner surface of the through hole 32c and the outer surface of the cylindrical portion 31c. To obtain an appropriate mating clearance. On the contrary, when the wedge-shaped members 35 and 36 have a shape that makes the fitting clearance smaller than the design value, the cutting amount is increased as shown by a two-dot chain line N4 in FIG. 12, and the inner diameter of the through hole 32c is increased. By making the size larger than the design value N2, the space between the inner surface of the through hole 32c and the outer surface of the cylindrical portion 31c is widened to obtain an appropriate fitting clearance.

  FIG. 13 shows a mode in which the amount of cutting process based on the same concept is adjusted on the outer surface of the cylindrical portion 31 c of the external gear 31. The cylindrical portion 31c has an outer diameter size indicated by a one-dot chain line M1 in FIG. 13 at a stage immediately after burring. The designed outside diameter size of the cylindrical portion 31c is assumed to be a solid line M2 in FIG. If the wedge-shaped members 35 and 36 (particularly the inner cylindrical surfaces 35a and 36a) have a shape corresponding to the fitting clearance as designed, the wedge-shaped members 35 and 36 are cut by cutting the outer surface of the cylindrical portion 31c to the M2 position. In the assembled state, the inner cylindrical surfaces 35a and 36a and the outer surface of the cylindrical portion 31c can be fitted without play. If the wedge-shaped members 35 and 36 have a shape in which the fitting clearance is larger than the design value, the amount of cutting on the outer surface of the cylindrical portion 31c from the initial outer diameter M1 is reduced as shown by a two-dot chain line M3 in FIG. By making the outer diameter size of the portion 31c larger than the design value M2, the space between the inner surface of the through hole 32c and the outer surface of the cylindrical portion 31c is narrowed to obtain an appropriate fitting clearance. On the contrary, if the wedge-shaped members 35 and 36 have a shape that makes the fitting clearance smaller than the design value, the cutting amount of the outer surface of the cylindrical portion 31c from the initial outer diameter M1 is increased as indicated by a two-dot chain line M4 in FIG. Then, by making the outer diameter size of the cylindrical portion 31c smaller than the design value M2, the space between the inner surface of the through hole 32c and the outer surface of the cylindrical portion 31c is widened, and an appropriate fitting clearance is obtained.

  That is, in any case, the diameter size is adjusted by cutting on the cylindrical portion 31c or the through hole 32c side so as to correspond to the actual shape of the wedge-shaped members 35 and 36. As a specific work process, first, the shape of the wedge-shaped members 35 and 36, strictly speaking, the contact area between the inner cylindrical surfaces 35a and 36a with the inner surface of the cylindrical portion 31c and the inner surface of the through holes 32c with the outer cylindrical surfaces 35b and 36b. The width dimension of the area, the diameter size and the curvature in the contact area on the inner cylinder surfaces 35a and 36a and the outer cylinder surfaces 35b and 36b are measured. And according to the obtained measured value, the outer diameter size of the cylindrical part 31c and the inner diameter size of the through hole 32c, that is, the cutting amount is determined. Then, the cutting process using the cutters 46 and 56 described above is performed, and the determined diameter size is adjusted. Ideally, it is desirable to measure the shape of each wedge-shaped member 35, 36 for each individual product, and to set the cutting amount of the cylindrical portion 31c and the through hole 32c corresponding to the shape. Therefore, it is practical to set the shape measurement and the cutting amount for each production lot from the viewpoint of labor and cost.

  The adjustment of the cutting amount considering the shape of the wedge-shaped members 35 and 36 as described above can improve accuracy when performed on both the cylindrical portion 31c side and the through hole 32c side. If only one of the cylindrical portion 31c and the through hole 32c can be adjusted, it may be adjusted. In addition, about the cylindrical part 31c, since the inner surface side functions as a bearing part of the rotating shaft 33, it is preferable to leave moderate thickness without making cutting amount very large.

  Thus, by adjusting the bearing surface position with respect to the wedge-shaped members 35 and 36 by changing the diameter size (cutting amount) of the cylindrical portion 31c or the through hole 32c, a plurality of types of wedge-shaped members 35 having different sizes and shapes, It is unnecessary to prepare 36 in advance and to replace the wedge-shaped members 35 and 36 with appropriate sizes each time the individual gear mechanism 30 is assembled. As a result, the manufacturing cost can be reduced, and the management of parts becomes easy.

  As mentioned above, although demonstrated based on illustration embodiment, this invention is not limited to this embodiment, It is possible to set it as a different structure unless it deviates from the main point of invention. For example, in the embodiment, the external gear 31 is provided with the cylindrical portion 31c, and the through-hole 32c into which the cylindrical portion 31c is inserted is formed in the internal gear 32. However, this relationship can be reversed.

It is a longitudinal cross-sectional view which shows an example of the Taumel type reclining apparatus provided with the external gear and the internal gear by this invention. It is the left view which showed the reclining apparatus of FIG. 1 except the upper arm and the lower arm. It is a disassembled perspective view of the principal part of the reclining apparatus of FIG. It is a figure which shows an external gear, (a) is a front view, (b) is AA sectional drawing of (a). It is a figure which shows an internal gear, (a) is a front view, (b) is BB sectional drawing of (a). It is a perspective view which shows the clamp jig | tool which hold | maintains an external gear, and the cutter which cuts the cylindrical part outer surface of an external gear. It is a perspective view which shows the clamp jig | tool which hold | maintains an internal gear, and the cutter which cuts the through-hole inner surface of an internal gear. It is the figure which looked at the state holding an external gear with a clamp jig from the expansion / contraction part tip side of a chuck. It is the figure which expanded and showed the meshing part of the holding tooth by the side of a clamp jig | tool in the holding state of FIG. 8, and the external tooth of an external gear. It is the figure which looked at the state which held the internal gear with the clamp jig from the main-body part side of a clamp jig by making the expansion / contraction part of a chuck into a section. It is the figure which expanded and showed the meshing part of the holding tooth by the side of a clamp jig | tool in the holding state of FIG. 10, and the internal tooth of an internal gear. It is the figure which showed the change of the cutting amount with respect to the inner surface of the through-hole of an internal gear. It is the figure which showed the change of the cutting amount with respect to the outer surface of the center cylindrical part of an external gear. It is a comparison figure which shows the axial part vicinity of the external gear and internal gear in case the fitting clearance of a wedge-shaped member is larger than a design value.

Explanation of symbols

DESCRIPTION OF SYMBOLS 10 Lower arm 11 Fitting hole 13 Connecting shaft 20 Upper arm 21 Fitting hole 30 Gear mechanism 31 External gear 31a Fixed protrusion 31b External tooth 31c Cylindrical part 31d Recessed protrusion 31 Internal gear 32a Fixed protrusion 32b Internal tooth 32c Through hole ( Round hole)
32d Recess 32e Stopper projection 32f Cylindrical rib-shaped portion 33 Rotating shaft 35 36 Wedge-shaped member 35a 36a Inner cylindrical surface 35b 36b Outer cylindrical surface 37 Spring 38 Pressing member 40 Clamp jig (holding means)
41 Main unit 42 Chuck 43 Enlarging / contracting part (dividing part)
43a annular flange 43b recess 43c holding tooth 44 central opening 45 gap 46 cutter (cutting blade)
50 Clamp jig (holding means)
51 Body 52 Chuck 53 Enlarging / Reducing (Dividing)
53a Holding tooth 54 Central opening 55 Cavity 56 Cutter (cutting blade)

Claims (4)

An external gear fixed to one of the seat cushion and the seat back so as to be positioned at the center of tilting of the seat back;
An internal gear formed with internal teeth having a larger number of teeth than the external teeth meshing with the external teeth of the external gear and fixed to the other of the seat cushion and the seat back;
A large-diameter circular hole provided on one and the other of the external gear and the internal gear with the respective axes as centers, and a cylindrical portion having a smaller diameter than the circular hole; and between the inner surface of the circular hole and the outer surface of the cylindrical portion It is inserted, and the relative movement of the external gear and the internal gear is restricted and the rotational force in the forward / reverse direction is applied, so that the external gear and the internal gear are relatively swung while changing the meshing part. A pair of wedge-shaped members to be rotated;
In a reclining device comprising
At least one of the inner surface of the circular hole and the outer surface of the cylindrical portion is determined by three or more meshing positions in the circumferential direction of the external teeth of the external gear and three or more in the circumferential direction of the internal teeth of the internal gear A reclining device that is calibrated with reference to an axis determined by the meshing position. An external gear fixed to one of the seat cushion and the seat back so as to be positioned at the center of tilting of the seat back;
An internal gear formed with internal teeth having a larger number of teeth than the external teeth meshing with the external teeth of the external gear and fixed to the other of the seat cushion and the seat back;
A large-diameter circular hole provided on one and the other of the external gear and the internal gear with the respective axes as centers, and a cylindrical portion having a smaller diameter than the circular hole; and between the inner surface of the circular hole and the outer surface of the cylindrical portion It is inserted, and the relative movement of the external gear and the internal gear is restricted and the rotational force in the forward / reverse direction is applied, so that the external gear and the internal gear are relatively swung while changing the meshing part. A pair of wedge-shaped members to be rotated;
In a reclining device comprising
Engaging and holding at least one of the external teeth of the external gear and the internal teeth of the internal gear at three or more positions in the circumferential direction; and
Centering on an axis determined at three or more meshing positions different from each other in the circumferential direction, rotating a held gear relative to a cutting blade and machining at least one of the circular hole inner surface and the cylindrical portion outer surface;
The manufacturing method of the reclining apparatus characterized by having. In the manufacturing method of the reclining device according to claim 2, in the step of holding at least one of the external teeth of the external gear and the internal teeth of the internal gear, at least three divided portions that can be expanded and contracted in the rotational radial direction; Reclining for holding the external gear or the internal gear by a holding means provided with at least one external tooth of the external gear or a holding tooth meshable with the internal tooth of the internal gear provided in each divided portion Device manufacturing method. In the manufacturing method of the reclining apparatus of Claim 2 or 3, Furthermore,
Measuring the shape of the contact area between the inner surface of the circular hole and the outer surface of the cylindrical portion in the pair of wedge-shaped members before assembly;
Determining a diameter size of at least one of the outer surface of the cylindrical portion and the inner surface of the circular hole based on the measured value;
The manufacturing method of the reclining apparatus which has this.

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