JP2018192183A - Recliner - Google Patents

Abstract

To enhance structural strength of a ring member for coming-off stop of two disk-shaped connection members forming a recliner in an axial direction.SOLUTION: A recliner 4 comprises: two disk-shaped gears, namely a lower gear 10 and an upper gear 20 which are assembled in an axial direction so as to rotate relatively mutually; a rotation stop mechanism for stopping relative rotation thereof; and a ring member 70 which is attached over outer peripheries 11, 24 of the lower gear 10 and the upper gear 20, and maintains a state in which the lower and upper gears are assembled in the axial direction. The ring member 70 comprises: a coupling part 71 coupled to an outer peripheral part 24 of the upper gear 20; a surrounding part 72 extended from the coupling part 71 in an axial direction and surrounds an outer peripheral part 11 of the lower gear 10 from an outer peripheral side; and a pressing part 73 which is folded to inside of a radial direction from an end part of a tip extended in an axial direction of the surrounding part 72 and is put to the outer peripheral part 11 of the lower gear 10 from outside of the axial direction. A protrusion portion 73A which protrudes and is bent outward in an axial direction is formed on the pressing part 73.SELECTED DRAWING: Figure 7

Description

  The present invention relates to a recliner. In detail, it is related with the recliner which bears the reclining adjustment mechanism of a vehicle seat.

  2. Description of the Related Art Conventionally, in a vehicle seat, a configuration is known in which a seat back is connected to a seat cushion so that a backrest angle can be adjusted via a recliner (Patent Document 1). The recliner is assembled so that the disk-shaped internal gear and the external gear can be rotated relative to each other while changing their meshing positions. The internal gear and the external gear are pressed so as to be strongly meshed with each other by an anti-rotation mechanism assembled therebetween, or are rotated in a direction to change the mutual meshing position. It has a configuration.

  The external gear and the internal gear described above are assembled in a state in which they are prevented from coming off in the axial direction by a cylindrical ring member mounted across the outer peripheral portions. Specifically, the ring member described above includes a coupling portion that is fitted and integrally coupled to the outer peripheral portion of the internal gear, and an enclosure that extends from the coupling portion in the axial direction and surrounds the outer peripheral portion of the external gear from the outer peripheral side. And a pressing portion that is bent inward in the radial direction from the tip end portion extending in the axial direction of the surrounding portion and applies a surface from the outer side in the axial direction to the outer peripheral portion of the external gear. .

JP 2013-94375 A

  In the prior art, there is a problem that the pressing portion of the ring member tends to be bent outward in the axial direction based on the bending point with the surrounding portion due to the pressing force to the outer side in the axial direction received from the external gear. The present invention was devised as a solution to the above-described problem, and the problem to be solved by the present invention is to prevent axial detachment between the two disk-shaped connecting members constituting the recliner. This is to increase the structural strength of the ring member.

  In order to solve the above problems, the recliner of the present invention takes the following means.

  1st invention is a recliner which bears the reclining adjustment mechanism of a vehicle seat, Comprising: Two disk-shaped connection members assembled | attached to the axial direction in the state which can mutually be rotated, and two connection members An anti-rotation mechanism that is provided between them and stops relative rotation, and a ring member that is mounted between the outer peripheral portions of the two connecting members and holds them in an axially assembled state. is there. A coupling part that is coupled to the outer peripheral part of the connecting member on one side, an enclosure that extends in the axial direction from the coupling part and surrounds the outer peripheral part of the other connecting member from the outer peripheral side, and an axial direction of the enclosing part And a pressing portion that is bent inward in the radial direction from the end portion extending inward and applied to the outer peripheral portion of the coupling member on the other side from the outer side in the axial direction. An overhanging portion that bends and protrudes outward in the axial direction is formed in the pressing portion.

  According to the first aspect of the present invention, the projecting portion formed in the pressing portion of the ring member increases the second moment of the section around the bending point with the surrounding portion of the pressing portion, and the pressing portion is connected to the other side. It becomes difficult to be deformed against a force pressed outward from the member in the axial direction. With the above configuration, it is possible to increase the structural strength of the ring member that prevents the axial connection between the two disk-shaped connecting members.

  The second invention is the following configuration in the first invention described above. The overhang portion is formed at the inner edge of the pressing portion in the radial direction.

  According to the second aspect of the present invention, the cross-sectional secondary moment around the bending point with the surrounding portion of the pressing portion can be optimally increased by the projecting portion, and the structural strength of the ring member can be appropriately increased. The overhang site can be easily molded.

  The third invention is the following configuration in the second invention described above. The overhanging portion is bent obliquely inward in the radial direction from the pressing portion toward the outside in the axial direction.

  According to the third aspect of the present invention, the shape of the projecting portion projecting obliquely inwardly can ensure a long projecting length inward in the radial direction as the entire pressing unit, and the other side connection by the pressing unit. The pressing of the member in the axial direction can be appropriately performed over a wider range.

  According to a fourth invention, in any one of the first to third inventions described above, the following configuration is adopted. The overhanging portion has an annular shape connected endlessly in the circumferential direction.

  According to the fourth invention, since the extension of the inner circumferential length of the pressing portion can be appropriately suppressed by the overhanging portion, it is possible to more appropriately suppress the deformation that is pressed outward in the axial direction of the pressing portion. it can.

It is a schematic perspective view of the vehicle seat to which the recliner of Example 1 is applied. It is the perspective view which expanded the connection part of a seat back and a seat cushion. It is a disassembled perspective view of the connection part. It is the disassembled perspective view which looked at the connection part from the different direction. It is a disassembled perspective view of a recliner. It is the disassembled perspective view which looked at the recliner from a different direction. It is the VII-VII sectional view taken on the line of FIG. It is a side view showing the rotation stop state of the recliner. It is a side view which shows the state by which the recliner was rotated by one side. It is a principal part enlarged view of FIG. 7 showing a mode that a recliner is welded to the side frame of a seat back. It is the XI-XI sectional view taken on the line of FIG. It is the XII section enlarged view of FIG. It is an expansion perspective view of a hinge bush single-piece | unit. It is the XIV part enlarged view of FIG. It is a schematic perspective view of the vehicle seat to which the recliner of Example 2 was applied. It is the disassembled perspective view which looked at the assembly part of a recliner from the one side. It is the disassembled perspective view which looked at the assembly part of a recliner from the other side. It is the disassembled perspective view which looked at the recliner from one side. It is the disassembled perspective view which looked at the recliner from the other side. It is the front view which looked at the recliner from the ratchet side. It is the XXI-XXI sectional view taken on the line of FIG. FIG. 22 is a cross-sectional view taken along the line XXII-XXII in FIG. 21 showing a locked state of the recliner. It is sectional drawing showing the unlocked state of the recliner. It is the schematic diagram which emphasized and represented each fulcrum when making a recliner into a locked state. It is the schematic diagram showing the state which the recliner deform | transformed by the input of heavy load. It is the XXVI part enlarged view of FIG.

  EMBODIMENT OF THE INVENTION Below, the form for implementing this invention is demonstrated using drawing.

<< Basic structure of sheet 1 >>
First, the configuration of the recliner 4 according to the first embodiment will be described with reference to FIGS. As shown in FIG. 1, the recliner 4 of the present embodiment is applied to a seat 1 configured as a left seat of an automobile, and a seat back 2 serving as a backrest portion of a seated occupant is used as a seat cushion serving as a seating portion. 3 is configured to function as a rotation shaft device (joint device) capable of stopping rotation that is coupled to a state where the backrest angle can be adjusted. The recliner 4 described above is provided at the lower end of each side frame 2F that forms the inner skeleton of the left and right sides of the seat back 2, and the rear end of each side frame (not shown) that forms the inner skeleton of the left and right sides of the seat cushion 3. Each of the coupled reclining plates 3F is provided so as to be interposed between them, and these are connected to each other so as to be rotated relative to each other. Each of the side frames 2F of the seat back 2 described above is disposed at an inner position in the seat width direction of each of the above reclining plates 3F, and each of the above described recliners 4 is interposed therebetween. It is assumed that

  Each reclining plate 3F described above has a larger thickness than each side frame 2F of the seat back 2 described above. The reason is that each reclining plate 3F is configured to strongly receive the load in the front-rear direction applied to the seat back 2 as a bending moment load via each recliner 4 that supports the seat back 2. The structure is provided with high structural strength by increasing the thickness. Each side frame 2F of the seat back 2 described above is configured to be appropriately reduced in weight by being made thinner than each reclining plate 3F.

  Each of the recliners 4 described above has an electric configuration, and is normally held in a rotation-stopped state in which the backrest angle of the seat back 2 is fixed. Each of the recliners 4 is operated by rotating an electric switch (not shown) provided on the left side of the seat cushion 3 so that they are simultaneously rotated around the same axis so that the backrest angle of the seat back 2 is increased or decreased. It is designed to change in the direction. In addition, the recliners 4 are configured such that their rotation operations are stopped all at once by stopping the operation of the electric switch (not shown) described above.

  Specifically, each recliner 4 described above incorporates a hinge bush 60 for performing each rotation operation at the center thereof. The hinge bushes 60 are integrally connected to each other via a connecting rod 5R, and each of the hinge bushes 60R is rotated all at once as the connecting rod 5R is pivotally operated. Yes. Then, as the hinge bush 60 is turned, the recliner 4 on each side is turned so as to change the backrest angle of the seat back 2. The connecting rod 5 </ b> R described above is inserted into the drive unit 5 attached to the inner side surface portion of the left side frame 2 </ b> F of the seat back 2 and is connected so as to receive power transmission, and is transmitted from the drive unit 5. The shaft is rotated or stopped in both forward and reverse directions by rotational force and braking force.

<< Specific Configuration of Recliner 4 >>
Hereinafter, a specific configuration of each recliner 4 described above will be described in detail. In addition, although each recliner 4 is arrange | positioned mutually symmetrically, the substantial structure of each other is the same. Therefore, in the following, the configuration of the recliner 4 disposed on the left side of the seat 1 shown in FIGS. That is, as shown in FIG. 5 to FIG. 6, the recliner 4 includes a substantially disc-shaped lower gear 10 and an upper gear 20 that are assembled so as to overlap each other in the axial direction, and these rotation stoppers are assembled between them. A pair of wedges 40, a lock spring 50 that moves and urges each wedge 40 in the circumferential direction, a hinge bush 60 that is pivotally attached to the center of the upper gear 20 and moves each wedge 40 in the circumferential direction, And a ring member 70 that is assembled across the outer peripheral portions of both the gears 10 and 20 to prevent these axial detachments.

  Both the gears 10 and 20, the pair of wedges 40, and the hinge bush 60 described above are each formed of a hardened steel plate material that has been quenched. Here, the above-described lower gear 10 corresponds to the “other-side connecting member” of the present invention, and the upper gear 20 corresponds to the “one-side connecting member” of the present invention, and includes a wedge 40 and a lock spring 50. Corresponds to the “rotation stop mechanism” of the present invention. Hereinafter, the specific configuration of each component of the recliner 4 will be described in detail in order.

<< Configuration of Lower Gear 10 >>
First, the configuration of the lower gear 10 will be described. The lower gear 10 is formed of a substantially disk-shaped member having a surface directed in the sheet width direction. The lower gear 10 described above is formed with an internal gear 11 that protrudes in a substantially cylindrical shape toward an axial direction that is an assembling direction to the upper gear 20 at an outer peripheral edge portion that leaves the central portion. The internal gear 11 described above is formed by partially punching a part of the lower gear 10 in the plate thickness direction. On the inner peripheral surface of the internal gear 11, there is an internal tooth row 11 </ b> A that can be engaged by pressing an external tooth row 21 </ b> A of an external gear 21 that protrudes from the center of the upper gear 20 described later from the inside in the radial direction. Are formed side by side in the circumferential direction. The internal tooth row 11 </ b> A is formed continuously along the entire peripheral area on the inner peripheral surface of the internal gear 11.

  In addition, a circular hole 12 is formed in the center portion of the lower gear 10 so as to penetrate in a circular shape in the plate thickness direction. The circular hole 12 has a shape having a hole diameter larger than that of a cylindrical portion 22 formed so as to protrude from the center portion of the upper gear 20 described later, and the cylindrical portion 22 described above has a radial gap ( An annular gap S) can be received in an open state (see FIGS. 7 to 8). As shown in FIG. 8, a pair of wedges 40 are assembled in a gap (annular gap S) between the inner peripheral surface of the assembled circular hole 12 and the outer peripheral surface of the cylindrical portion 22. .

  These wedges 40 are normally squeezed to the respective sides in the circumferential direction with respect to the above-described gap (annular gap S) by the urging force of the lock spring 50 hooked between them. It functions to keep the relative rotation between the two gears 10 and 20 stopped. As shown in FIG. 9, these wedges 40 are rotated by a hinge bush 60 (described later) in either the forward or reverse direction. ) Is pushed in the circumferential direction (clockwise direction in the figure) opposite to the biasing direction by the lock spring 50 to release the state in which the relative rotation between the gears 10 and 20 is stopped. It is like that. Each wedge 40 is further pushed in the circumferential direction (clockwise direction in the drawing) as the hinge bush 60 further rotates, and the inner circumferential surface of the circular hole 12 is moved. And the outer peripheral surface of the cylindrical portion 22 (annular gap S) are gradually pushed and expanded in the circumferential direction (clockwise direction in the drawing) so that both gears 10 and 20 are relatively rotated. It is like that. These specific movements will be described in detail later.

  Further, as shown in FIG. 5, three arcs projecting side by side along the same circumference on the outer side surface in the axial direction opposite to the assembly direction of the lower gear 10 to the upper gear 20 described above. A dowel 13 having a shape is formed. These dowels 13 are formed by partially punching a part of the lower gear 10 in the plate thickness direction. As shown in FIGS. 3 and 7, these dowels 13 correspond to the corresponding three formed on the reclining plate 3 </ b> F when the axially outer side surface portion of the lower gear 10 is brought into contact with the inner side surface portion of the reclining plate 3 </ b> F. Each of the dowel holes 3Fb is fitted into the dowel hole 3Fb and integrally joined by welding. The reclining plate 3F described above is further formed with a fitting hole 3Fa that penetrates substantially in a perfect circle so as to communicate the hole shape across the three dowel holes 3Fb.

<< Configuration of Upper Gear 20 >>
As shown in FIGS. 5 to 6, the upper gear 20 is also formed of a substantially disk-shaped member that faces in the sheet width direction. The upper gear 20 has a shape having an outer diameter that is slightly larger than that of the lower gear 10 described above. The upper gear 20 is formed with an external gear 21 that protrudes in a substantially cylindrical shape toward the axial direction, which is an assembling direction to the lower gear 10, at the central portion where the outer peripheral edge portion is left. The external gear 21 is formed by partially punching a part of the upper gear 20 in the plate thickness direction. On the outer peripheral surface of the outer gear 21, an outer tooth row 21A that can mesh with the inner tooth row 11A formed on the inner peripheral surface of the inner gear 11 of the lower gear 10 from the inside in the radial direction is provided in the circumferential direction. It is formed side by side. The external tooth row 21 </ b> A is formed side by side continuously over the entire peripheral area on the outer peripheral surface of the external gear 21.

  The above-described external gear 21 is configured to have an outer diameter smaller than the internal gear 11 of the above-described lower gear 10 and one tooth number. Specifically, the number of teeth of the external gear row 21A of the external gear 21 is 33, whereas the number of teeth of the internal gear row 11A of the internal gear 11 is 34. The above-described upper gear 20 is assembled to the above-described lower gear 10 so that the external gear 21 is engaged with the internal gear 11 by being pressed from the inside in the radial direction.

  Here, a cylindrical portion 22 that protrudes in a cylindrical shape toward the axial direction that is an assembly direction to the lower gear 10 is formed by burring in the plate thickness direction at the center portion of the external gear 21 of the upper gear 20 described above. Yes. The cylindrical portion 22 is formed in a cylindrical shape having a smaller outer diameter than the circular hole 12 formed in the central portion of the lower gear 10 described above, and penetrates in a circular shape in the axial direction in the cylinder. A through hole 22A is formed. The cylindrical portion 22 described above is received in the circular hole 12 of the lower gear 10 by assembling the external gear 21 of the upper gear 20 described above in the axial direction to mesh with the internal gear 11 of the lower gear 10. By the above assembly, an annular gap S is formed between the outer peripheral surface of the cylindrical portion 22 and the inner peripheral surface of the circular hole 12 (see FIGS. 7 to 8).

  As shown in FIG. 8, the above-described annular gap S is in a state where the external gear 21 of the upper gear 20 is pressed against the internal gear 11 of the lower gear 10 from the inside in the radial direction. The relationship between the center positions 20R and 10R is in an eccentric state, so that a region having a wide radial interval and a region having a narrow radial direction are formed. Specifically, the annular clearance S is the narrowest in the radial direction in the circumferential region where the external gear 21 and the internal gear 11 are engaged, and in the opposite circumferential region passing through the axial center thereof, It is formed so as to have the largest radial spacing. A pair of wedges 40 are fitted and assembled in the annular gap S in the axial direction. An open ring-shaped lock spring 50 is applied between the wedges 40 to urge them so as to separate them in the opposite circumferential directions.

  With the above-described configuration, each wedge 40 is normally applied with an urging force so as to be pushed in a sandwiched manner in the circumferential direction from a region having a large radial interval toward a narrow region in the annular gap S described above. It is supposed to have received it. Then, with these pushing forces, the wedges 40 are always in a state in which the upper gear 20 is pressed against the lower gear 10 in a specific radial direction (downward in the drawing) with the pressing points P1 and P2 as fulcrums. The gears 21 and 11 are pressed against each other in a meshing state without backlash and are held in a state of being stopped from rotating.

  Each of the wedges 40 is rotated from the state in which the upper gear 20 is prevented from rotating with respect to the lower gear 10, and a hinge bush 60 described later is pivoted in either the forward or reverse direction. As shown in the figure, the hinge bush 60 is arranged in a circumferential direction (clockwise direction in the figure) on the opposite side to the biasing direction by the lock spring 50, one of which is located on the rotated side (left side in FIG. 9). The state where the relative rotation between the two gears 10 and 20 is stopped by being pushed is released. Each wedge 40 is further pushed in the circumferential direction (clockwise in the figure) as the hinge bush 60 further rotates, and is pushed in accordance with this movement. The two gears 10 are gradually pushed and expanded in the circumferential direction (clockwise direction in the drawing) in the gap (annular gap S) between the inner circumferential surface of the circular hole 12 and the outer circumferential surface of the cylindrical portion 22 by the other moved. , 20 is changed in the circumferential direction (clockwise direction in the figure). By the above operation, the external gear 21 rotates while changing the meshing position of each other along the inner peripheral surface of the internal gear 11 so that the relative rotational positional relationship changes according to the difference in the number of teeth. The upper gear 20 is rotated relative to the lower gear 10 by being moved.

  As shown in FIG. 6, on the outer side surface in the axial direction of the upper gear 20 described above, there are formed three arc-shaped dowels 23 that protrude side by side so as to draw the same circumference. These dowels 23 are formed by partially punching a part of the upper gear 20 in the plate thickness direction. 4 and 7, the dowels 23 are formed on the side frame 2F when the outer side surface portion in the axial direction of the upper gear 20 is brought into contact with the inner side surface portion of the side frame 2F of the seat back 2 and coupled. Each of the three dowel holes 2Fb is fitted and integrated with each other by welding. The side frame 2F of the seat back 2 described above is further penetrated in a circular shape so that the connecting rod 5R can be passed in the axial direction in the center of the region surrounded by the three dowel holes 2Fb. The through hole 2Fa is formed.

  As shown in FIG. 6, the outer peripheral portion of the above-described upper gear 20 has a concave portion 24 recessed inward in the radial direction and a convex portion 25 projecting outward in the radial direction from the concave portion 24 in the circumferential direction. 3 are alternately arranged side by side. Each of the recess positions 24 described above is formed in three circumferential regions (in the region between the three dowels 23 arranged in the circumferential direction) that are out of the circumferential region where the three dowels 23 are formed. ing. Each recessed portion 24 has a shape having an outer peripheral surface serving as a bottom surface of the recess at the same radial position as the outer peripheral surfaces of the three dowels 23 described above.

  In addition, each of the convex portions 25 described above has a shape having a meat portion protruding outward in the radial direction from each dowel 23 at a position on each circumferential region where the three dowels 23 described above are formed. It is formed. Each of these convex portions 25 has a shape with a circumferential length that extends longer in both directions in the circumferential direction than the individual dowels 23 located on the inner side in the radial direction. Each of the convex portions 25 and the concave portions 24 described above has the same thickness and the same thickness as the general surface portion that faces in the axial direction, which is the shape portion on the outer peripheral side of the external gear 21 of the upper gear 20. Is formed.

  Each of the recess positions 24 described above is formed on one end portion in the axial direction of a cylindrical shape of the ring member 70 described later, and each of the coupling portions 71 protruding in the axial direction from three regions in the circumferential direction is respectively axised. It functions as a part that is set in a state of being received in the direction and fitted on the outer peripheral surface. Each of the coupling portions 71 of the ring member 70 set on the outer peripheral surface of each recess position 24 is arced on the outer peripheral surface of each recess position 24 with the respective end portions inserted in the axial direction thereof. They are welded and joined together.

  On the other hand, each convex portion 25 is inserted into a region between the circumferential positions of each coupling portion 71 by fitting each coupling portion 71 of the ring member 70 described above at a position on the outer circumferential surface of each concave portion 24. Each of the formed recessed portions 71A is brought into contact with each other in the axial direction, and functions as a portion for positioning the insertion position of the ring member 70 in the axial direction. Further, as shown in FIG. 10, each convex portion 25 is formed by fitting each dowel 23 described above into each dowel hole 2 </ b> Fb formed in the side frame 2 </ b> F of the seat back 2, so that the outer side in the axial direction of the upper gear 20. When the surface portion is brought into surface contact with the inner side surface portion of the side frame 2F, the surface portion is set to be in surface contact with the inner side surface portion of the side frame 2F. With the above-described configuration, each convex portion 25 has a contact portion between the outer peripheral surface of each dowel 23 and the inner peripheral surface of each dowel hole 2Fb of the side frame 2F from the outside in the axial direction of the side frame 2F. When arc welding is performed, it is in a state of being applied to the welding portion We of the side frame 2F from the back side, thereby increasing the substantial thickness of the welded portion area to which the welding heat is applied, thereby preventing the side frame 2F from being burned out. It works to prevent.

<< Configuration of each wedge 40 >>
Next, the configuration of the wedge 40 will be described. As shown in FIG. 5, each wedge 40 has a curved shape that is symmetrical to each other in the circumferential direction. Each wedge 40 is set and provided in an annular gap S formed between the circular hole 12 of the lower gear 10 and the cylindrical portion 22 of the upper gear 20 (see FIG. 8). Each of the wedges 40 is curved in a tapered shape in which the radial thickness gradually decreases from one end side to the other end side in the circumferential direction so as to follow the shape of the annular gap S described above. It is made into a shape.

  A hook 41 having a partially cut-out shape is formed at each end of the wedge 40 on the thick side. Between these hooks 41, each end 51 of the open ring-shaped lock spring 50 is hooked and fixed from both inner sides. Each end portion 51 of the lock spring 50 is bent in a shape protruding in the axial direction, and is inserted between the hanging portions 41 of each wedge 40 while being squeezed so as to be attracted to each other. It is assembled in a state where it is hooked on each hook 41 by the resilience accompanying the restoration.

  As a result of the assembly of the lock spring 50, the wedges 40 are always subjected to a biasing force in a direction in which they are separated from the lock spring 50 in the circumferential direction. Then, by the above urging force, each wedge 40 receives a force so as to be pushed in a circumferential direction opposite to each other from a wide region in the radial direction in the annular gap S to a narrow region. It is in a state. Then, by the above pushing force, each wedge 40 applies a force to constantly push the upper gear 20 against the lower gear 10 in a specific radial direction (downward in the drawing) with the pressing points P1 and P2 as fulcrums. As a state, the gears 21 and 11 are pressed against each other in a meshing state without backlash and held in a state of being stopped from rotating.

  Each of the wedges 40 is rotated from the state in which the upper gear 20 is prevented from rotating with respect to the lower gear 10, and a hinge bush 60 described later is pivoted in either the forward or reverse direction. As shown in the figure, the hinge bush 60 is arranged in a circumferential direction (clockwise direction in the figure) on the opposite side to the biasing direction by the lock spring 50, one of which is located on the rotated side (left side in FIG. 9). The state where the relative rotation between the two gears 10 and 20 is stopped by being pushed is released.

<< Configuration of Hinge Bush 60 >>
Next, the configuration of the hinge bush 60 will be described. As shown in FIGS. 6 and 13, the hinge bush 60 includes a substantially disc-shaped cover portion 61 that faces in the axial direction, and a shaft portion 62 that protrudes from the center of the cover portion 61 in a cylindrical shape in the axial direction. An operation projection 63 protruding in an arc shape in the same axial direction as the shaft portion 62 described above from the outer peripheral edge portion of the cover portion 61, and a small cylindrical shape formed on the outer peripheral portion on the base side of the shaft portion 62 And a projecting portion 64 that protrudes. The hinge bush 60 is formed into a shape having the above shape by former forming of a steel plate material.

  A hexagonal hole 60 </ b> A that penetrates in the axial direction through the central portion of the shaft portion 62 described above is formed in the central portion of the hinge bush 60 described above. In the hexagonal hole 60A, as shown in FIG. 6, the above-described connecting rod 5R having a hexagonal bar shape that can be fitted into the hexagonal hole 60A is inserted in the axial direction so as to be integrated in the rotational direction. It is connected to. The cover part 61 mentioned above is made into the shape where the partial area | region of the circumferential direction of the outer peripheral part was notched. With the above-described configuration, each end surface hooked to each wedge 40 of the lock spring 50 described above is formed on each end surface formed in a shape in which the surface is directed in the rotation direction by the notch of the cover portion 61 described above. A spring pressing portion 61 </ b> A that is set in a shape opposed to the circumferential direction 51 is formed.

  As shown in FIGS. 5, 7 and 8, the hinge bush 60 described above has an axial portion 62 whose axial portion 62 protrudes from the cylindrical portion 22 of the upper gear 20 described above. It is assembled | attached as the state inserted so that the shaft could be rotated. As a result of the above assembly, the hinge bush 60 has the operation protrusion 63 protruding in the axial direction described above inserted into the gap between the tapered ends of the wedges 40 (annular gap S). Set as state. Each spring pressing portion 61 </ b> A is set in a state of being disposed at a position that is in a circumferentially facing relationship with each end portion 51 of the lock spring 50. Moreover, as shown in FIGS. 11-12, the cover part 61 mentioned above is set to the state which covered each wedge 40 from the outer side of the axial direction. 8 to 9, the cover 61 of the hinge bush 60 and a part of the lock spring 50 are shown in a shape that is transmitted through phantom lines in order to show the internal structure of the recliner 4 in an easy-to-understand manner.

  The hinge bush 60 assembled as described above is pivotally operated by receiving the driving force from the drive unit 5 described above by connecting the connecting rod 5R described above to the center of the hinge bush 60. It is like that. For example, when the hinge bush 60 is rotated in the clockwise direction as shown in FIG. 9 by the above-described pivoting operation, the lock spring 50 is illustrated by the spring pressing portion 61A on the left side of the covering portion 61 in the drawing. The end 51 that is hooked on the left wedge 40 is pressed in the circumferential direction so as to be removed from the hooked state with the hook 41 of the wedge 40. Further, the hinge bush 60 pushes the wedge 40 on the left side of the figure in the circumferential direction by the operation projection 63 by the above-mentioned rotation operation, and the wedge 40 is radially spaced within the annular gap S described above. It pushes from a narrow area to a wide area.

  By the above operation, the urging force of the lock spring 50 applied to the wedge 40 on the left side of the figure is released, and the state of being pushed in the annular gap S of the wedge 40 is released, and both gears are released. The rotation stopping state between 10 and 20 is released. When the hinge bush 60 is further rotated in the clockwise direction from the above state, the left wedge 40 is further pushed in the same direction, and the right wedge 40 is also moved to the lock spring. By the urging force of 50, the left wedge 40 is pushed so as to further bite in the circumferential direction toward the narrow space in the annular gap S that can move with the movement of the left wedge 40. It is like that.

  By the above movement, the right wedge 40 gradually pushes and widens the gap (annular gap S) between the inner circumferential surface of the circular hole 12 and the outer circumferential surface of the cylindrical portion 22 in the circumferential direction (clockwise direction in the drawing). The meshing position of the external gear 21 with respect to the internal gear 11 changes in the circumferential direction (clockwise direction in the figure). When the right wedge 40 is not easily slid in the circumferential direction only by the urging force of the lock spring 50 due to an external load action or the like, the left wedge 40 pushed by the hinge bush 60 is rotated. The head hits the head of the right wedge 40 and the right wedge 40 is directly pushed in the same circumferential direction.

  By the above movement, the external gear 21 and the internal gear 11 are pushed and moved relative to each other due to the difference in the number of teeth, so that the upper gear 20 rotates relative to the lower gear 10. The relative rotation is stopped by stopping the turning operation of the hinge bush 60. Specifically, when the rotation operation of the hinge bush 60 is stopped, each wedge 40 is again pushed into the region where the gap in the annular gap S is narrowed by the urging force of the lock spring 50, The relative rotation between the two gears 10 and 20 is returned to the stopped state. When the hinge bush 60 is rotated in the opposite direction, the upper gear 20 rotates relative to the lower gear 10 by the movement in the opposite direction.

<< Configuration of Ring Member 70 >>
Next, the configuration of the ring member 70 will be described. As shown in FIG. 5 to FIG. 6, the ring member 70 is formed by punching a thin steel plate into a hollow disc shape and further drawing the punched outer peripheral side portion in the plate thickness direction. The whole is formed in a substantially cylindrical shape having a hollow disk-like seat. Specifically, the ring member 70 includes a hollow disk-shaped pressing portion 73 that faces in the axial direction, a surrounding portion 72 that extends from the outer peripheral edge of the pressing portion 73 in a cylindrical shape in the axial direction, and a surrounding portion. The coupling portion 71 further extends in a cylindrical shape having projections and depressions in the axial direction from 72.

  In the ring member 70 described above, the lower gear 10 and the upper gear 20 described above are sequentially incorporated in the cylinder in the axial direction, so that the pressing portion 73 is disposed on the outer periphery of the lower gear 10 in the axial direction as shown in FIG. And the enclosure 72 is set in a state in which the outer peripheral portion of the lower gear 10 is enclosed from the outer peripheral side, and the coupling portion 71 is fitted in the outer peripheral portion of the upper gear 20. . Then, after the assembly, the ring member 70 is integrally coupled to the upper gear 20 by arc welding the coupling portion 71 fitted to the outer circumferential portion of the upper gear 20 to the outer circumferential portion of the upper gear 20. . With the above configuration, the lower gear 10 and the upper gear 20 are held in a state where they are prevented from coming off in the axial direction via the ring member 70.

  Specifically, as shown in FIG. 5 to FIG. 6, the coupling portion 71 described above has recess portions 71 </ b> A that are recessed in the axial direction at the three circumferential portions extending in the cylindrical shape. As a result, three portions in the circumferential direction, which are regions between the arrangement of the recessed portions 71A, are formed in an uneven shape having a shape partially protruding in the axial direction. The coupling portion 71 is formed so that the shape portions partially projecting in the axial direction are inserted in the axial direction into the respective recessed positions 24 formed on the outer peripheral portion of the upper gear 20 described above, and are joined by welding. It has become. Each recessed portion 71A is abutted in the axial direction against each convex portion 25 formed on the outer peripheral portion of the upper gear 20 described above, and a portion that restricts the insertion position of the upper gear 20 into the ring member 70 in the axial direction. (See FIG. 7).

  As shown in FIGS. 7 and 14, the pressing portion 73 is applied to the outer peripheral portion (internal gear 11) of the lower gear 10 described above from the outside in the axial direction, and the lower gear 10 is dropped in the axial direction with respect to the upper gear 20. It is designed to be held so as not to let it. As shown in FIG. 14, the above-described pressing portion 73 protrudes from the radially inner peripheral edge so as to be bent obliquely inward in the radial direction toward the outer side in the axial direction. The part 73A is bent and formed into an endlessly connected shape over the entire circumference.

  As shown in FIG. 7, the above-described overhanging portion 73 </ b> A is formed by the above-described internal gear 11 when the external gear 21 of the above-described upper gear 20 rotates to change the meshing position with respect to the internal gear 11 of the lower gear 10. Even if the outer peripheral surface 11B of the central disc portion half-extracted from the axial direction to the inner peripheral surface is moved so as to approach the inner peripheral surface from the inner side in the radial direction, there is a slight gap between the outer peripheral surface 11B and the outer peripheral surface 11B. It has T3 (refer FIG. 14), and is formed in the shape which protrudes diagonally inward in the radial direction so that it may not contact with the outer peripheral surface 11B.

  Specifically, as shown in FIG. 14, the above-described overhanging portion 73 </ b> A is an inclination formed on an angular surface on the inner side in the axial direction of the above-described outer peripheral surface 11 </ b> B formed along with the above-described half-punching of the internal gear 11. The surface is obliquely projected so as to be substantially parallel to the sag surface 11C that rises in a shape, and extends long and obliquely inward in the radial direction to the position where the sag surface 11C and the radial arrangement overlap. The shape is made. With the above-described configuration, the holding portion 73 has a cross-sectional secondary moment around the bending point 73B with the surrounding portion 72 as the above-described overhanging portion 73A is overhanging. It becomes difficult to bend and deform with respect to the pressed force.

  Specifically, the pressing portion 73 is hard to be bent and deformed because its hardness is increased by the bending work hardening of the protruding portion 73A. More specifically, the pressing portion 73 is formed in an endlessly connected ring shape, and the above-described overhanging portion 73A is formed endlessly over the entire inner peripheral edge. The peripheral length of the inner peripheral edge is thickened and reinforced in such a way that it is difficult to extend, and this also makes it difficult to bend and deform outward in the axial direction.

<< About the structure of the projection part 64 of the hinge bush 60 >>
By the way, as shown in FIGS. 2 to 3, 7, and 11, the connecting rod 5 </ b> R that is inserted and connected to the center portion of the hinge bush 60 of the recliner 4 from the inner side to the outer side in the axial direction includes: A stopper washer 5Ra is attached to the inserted portion. With the above configuration, the connecting rod 5 </ b> R is restricted from moving in the axial direction until the above-described washer 5 </ b> Ra comes into contact with the hinge bush 60. Specifically, the connecting rod 5R described above is similarly attached to the end of the other end inserted into the recliner 4 on the other side described above with reference to FIG. The washer 5Ra is restricted so as to be displaced in the axial direction only until the washer 5Ra contacts the hinge bush 60 of the recliner 4 on each side.

  As shown in FIGS. 2 to 3, 7, and 11, the fitting hole 3 </ b> Fa of the reclining plate 3 </ b> F coupled to the lower gear 10 of the recliner 4 described above is located on the back side of the fitting hole 3 </ b> Fa. A cylindrical container-shaped cap 80 that covers the lock spring 50 and the hinge bush 60 of the recliner 4 positioned from the outside in the axial direction is fitted and welded. After the cap 80 is set in the fitting hole 3Fa of the reclining plate 3F from the outside in the axial direction, the outer peripheral part thereof is the outer peripheral part of the fitting hole 3Fa (the shape part of the region between the arrangement of the dowel holes 3Fb). ) And are integrally joined together. The cap 80 restricts the movement of the lock spring 50 and the hinge bush 60 of the recliner 4 to the outside in the axial direction. That is, even if the connecting rod 5R described above is displaced in the axial direction, the movement of the hinge bush 60 to move outward in the axial direction is restricted by the cap 80 described above. . Further, the cap 80 restricts the movement of the lock spring 50 described above from the hooked state with each wedge 40 to the outside in the axial direction.

  As shown in FIG. 12, the cap 80 described above is in a state of being provided with a clearance T1 that allows the cover portion 61 of the hinge bush 60 described above to be slightly displaced axially outward. . However, even if the above-described gap T1 is opened, the gap T1 described above is caused by the effects of overload received from the outside during use, in addition to manufacturing variations of the components and peripheral parts of the recliner 4 including the hinge bush 60. May be stuffed. As a result, when the hinge bush 60 presses each wedge 40 in the axial direction, each wedge 40 is pushed or moved in the circumferential direction as described above with reference to FIG. The slidability when the position is returned by the force is deteriorated.

  Therefore, even if the above-described hinge bush 60 is filled with the gap T1 between the cap 80 as described above, the wedges 40 always come into contact with the cylindrical portion 22 of the upper gear 20 at all times. A projection 64 that functions to ensure an axial gap T2 is formed between the projection 64 and the projection 64. As shown in FIG. 13, the protrusion 64 has an outer peripheral portion on the base side of the shaft portion 62 of the hinge bush 60 described above, that is, the shaft portion 62 and a cover portion 61 that projects radially outward from the shaft portion 62. The inner corner portion is formed so as to project into an endless cylindrical shape that is slightly larger than the shaft portion 62. The protrusion 64 is formed in a shape protruding uniformly over the entire outer peripheral portion of the shaft portion 62.

  As shown in FIG. 12, when the covering portion 61 of the hinge bush 60 is subjected to a force to be pushed toward the wedges 40 when the gap is filled, the protruding portion 64 has the covering portion 61. Prior to being applied to the wedge 40 in the axial direction, the tip end surface of the cylindrical portion 22 of the upper gear 20 is brought into contact with the wedge 40, and the movement of the hinge bush 60 pushed in the axial direction is restricted. With the above-described configuration, the axial gap T <b> 2 associated with the tip of the protrusion 64 described above is always ensured between the cover 61 of the hinge bush 60 and each wedge 40. Therefore, even when the hinge bush 60 is capped in the axial direction as described above, the wedges 40 can always be slid smoothly.

  Here, the cylindrical portion 22 of the upper gear 20 described above is configured so that the axially protruding position of the upper gear 20 is kept at a low protruding position that does not reach the axially outer surface of each wedge 40 described above. Yes. The reason for this is that the area where the cylindrical portion 22 of the upper gear 20 can be pushed in at the time of burring is narrowed with the downsizing of the recliner 4. Therefore, the cover portion 61 of the hinge bush 60 described above is to the position where the cylindrical portion 22 of the upper gear 20 is retracted to the inside of the outer side surface in the axial direction of each wedge 40 if the protrusion 64 is not formed. Since it is only overhanging, it is configured to hit each wedge 40 before the cylindrical portion 22 when the gap is filled in the axial direction. However, since the projections 64 are formed on the hinge bush 60, the cover 61 of the hinge bush 60 is applied to each wedge 40 even if the cylindrical portion 22 of the upper gear 20 has a short overhang as described above. The projecting portion 64 can be applied to the cylindrical portion 22 of the upper gear 20 earlier than that.

<Summary>
In summary, the recliner 4 of this embodiment is configured as follows. That is, a recliner (4) that bears a reclining adjustment mechanism for a vehicle seat (1), and two disk-like connecting members (10, 20) assembled in an axial direction so as to be relatively rotatable with each other; An anti-rotation mechanism (40, 50) that is provided between the two connecting members (10, 20) and stops the relative rotation thereof, and an outer peripheral portion (11, 24) of the two connecting members (10, 20). ) And a ring member (70) that is mounted between them and holds them assembled in the axial direction. The ring member (70) is coupled to the outer peripheral portion (24) of the connection member (20) on one side, and the coupling member (10) on the other side extends in the axial direction from the coupling portion (71). ) That surrounds the outer peripheral portion (11) from the outer peripheral side, and the other end connecting member (10) that is bent inward in the radial direction from the end portion extending in the axial direction of the surrounding portion (72). A pressing portion (73) applied to the outer peripheral portion (11) of the outer peripheral portion from the outside in the axial direction. An overhanging portion (73A) is formed on the pressing portion (73) so as to bend and protrude outward in the axial direction.

  With such a configuration, the protruding portion (73A) formed in the pressing portion (73) of the ring member (70) is bent at the folding point (72) with the surrounding portion (72) of the pressing portion (73) ( 73B) The moment of inertia of the cross section around is increased, and the pressing portion (73) is less likely to be deformed by the force pressed outward in the axial direction from the connecting member (10) on the other side. With the above configuration, it is possible to increase the structural strength of the ring member (70) for preventing the axial detachment between the two disk-shaped connecting members (10, 20).

  Moreover, the overhang | projection site | part (73A) is formed in the edge part inside the radial direction of a holding | suppressing part (73). By adopting such a configuration, the secondary moment of the section around the bending point (73B) with the surrounding part (72) of the pressing part (73) is optimally increased by the overhanging part (73A), and the ring The structural strength of the member (70) can be increased appropriately, and the overhang portion (73A) can be easily formed.

  Further, the projecting portion (73A) projects from the pressing portion (73) obliquely inward in the radial direction toward the outer side in the axial direction. With such a configuration, a long projecting length inward in the radial direction as the entire pressing portion (73) can be ensured by the shape projecting obliquely inside the projecting portion (73A). The pressing of the other connecting member (10) by the pressing portion (73) can be appropriately performed over a wider range.

  Further, the projecting portion (73A) has an annular shape connected endlessly in the circumferential direction. With such a configuration, since the extension of the inner circumferential length of the pressing portion (73) can be appropriately suppressed by the overhanging portion (73A), the outer side in the axial direction of the pressing portion (73). The pressed deformation can be suppressed more appropriately.

<< Basic structure of sheet 101 >>
First, the configuration of the recliner 104 according to the first embodiment will be described with reference to FIGS. As shown in FIG. 15, the recliner 104 of this embodiment is applied to a seat 101 that constitutes a passenger seat of a small car, and a seat back 102 that serves as a backrest for a seated occupant is replaced with a seat cushion 103 that serves as a seating portion. On the other hand, it is configured to function as a rotation shaft device (joint device) that can be rotated and connected in a state in which the backrest angle can be adjusted. The recliner 104 described above includes a lower end portion of the left and right side frames 102Fa of the back frame 102F constituting the skeleton of the seat back 102, and a rear end portion of the left and right side frames 103Fa of the cushion frame 103F constituting the skeleton of the seat cushion 103. Between the two, and are connected to each other (see FIGS. 16 to 17). Specifically, each side frame 102Fa of the seat back 102 described above is provided so as to be positioned inside each side frame 103Fa of the seat cushion 103, and a recliner 104 is provided between each of them. It is in a state.

  As shown in FIG. 15, each recliner 104 described above is normally held in a locked state in which the backrest angle of the seat back 102 is fixed. Each recliner 104 is unlocked by releasing the lock state of the seat back 102 simultaneously by pulling up a reclining lever 105 provided on a side of the seat cushion 103 outside the vehicle, thereby changing the backrest angle of the seat back 102. It can be switched to the state. Each recliner 104 is returned to the locked state in which the backrest angle of the seat back 102 is fixed again by the urging by returning the operation state where the reclining lever 105 is lifted.

  A biasing force is always applied to the seat back 102 in the direction of forward tilt rotation between the side frames 102Fa on the left and right sides of the seat back 102 and the side frames 103Fa on the left and right sides of the seat cushion 103. A return spring 106 is hooked. These return springs 106 are respectively constituted by spiral springs, and their inner ends are hooked to brackets 103Fc coupled to the outer surfaces of the side frames 103Fa of the seat cushion 103, and the outer sides thereof are The end portion is in a state of being hooked and provided on a bracket 102Fc coupled to the outer surface of each side frame 102Fa of the seat back 102 (see FIG. 21).

  By the rotational biasing force of the return spring 106, the seat back 102 is lifted up to a position corresponding to the back of the seated occupant by releasing the fixed state of the backrest angle by each of the recliners 104 described above, and the seat The backrest angle is freely adjusted back and forth according to the movement of tilting the back and forth. By providing such an urging structure, the backrest angle of the seat back 102 can be easily adjusted.

  The seat back 102 described above rotates in a rotation region of about 180 degrees from the forward tilt position in which the seat back 102 is folded into the upper surface portion of the seat cushion 103 to the rear tilt position in which the seat back 102 is folded backward. Be able to. Of these, the rotation region of about 90 degrees from the position where the backrest angle of the seat back 102 stands straight up to the above-described rearward tilt position is stopped by stopping the lifting operation of the reclining lever 105. It is set as a rotation region of a “lock zone” where the tilt angle is returned to a fixed state. In addition, the backrest angle of the seat back 102 is fixed at about 90 degrees from the position where the backrest angle exceeds the lock zone to the forward tilt position described above even if the lifting operation of the reclining lever 105 is stopped. It is set as a “free zone” rotation area that is not returned to the set state.

  The rotation zones of the lock zone and the free zone are formed by the rotation zones of the lock zone and the free zone set for each recliner 104 described later. Since the above-described free zone rotation area is provided, the seat back 102 is pushed down to the position where the seat 101 enters the free zone by operating the reclining lever 105 while no person is sitting on the seat 101. Then, even if the operation of the reclining lever 105 is not continued, it is automatically moved forward to the position where it is folded into the upper surface of the seat cushion 103.

<< Specific Configuration of Recliner 104 >>
As shown in FIGS. 16 to 17, each recliner 104 described above includes a ratchet 110 integrally coupled to the outer side surface of each side frame 102 Fa of the seat back 102 described above, and each side frame 103 Fa of the seat cushion 103. A guide 120 integrally coupled to the inner side surface, and the relative rotation between the ratchet 110 and the guide 120 is locked or released to fix or release the backrest angle of the seat back 102 It has a configuration to do.

  Hereinafter, a specific configuration of each recliner 104 described above will be described in detail. Note that the recliners 104 are arranged symmetrically with respect to each other, but the substantial configuration is the same. Therefore, in the following, the configuration of the recliner 104 disposed outside the vehicle shown in FIGS. 16 to 17 will be described on behalf of these. As shown in FIGS. 18 to 19, the recliner 104 includes a disc-shaped ratchet 110 and a guide 120 assembled in the axial direction, three poles 130 (130 </ b> A to 130 </ b> C) assembled between them, and a rotating cam. 140, a hinge cam 150, a lock spring 160 assembled to the outer surface of the guide 120, and a ring member 170 formed in a cylindrical shape with a seat assembled between the ratchet 110 and the guide 120. Configured. The ratchet 110, the guide 120, the three poles 130, the rotating cam 140, and the hinge cam 150 described above are each formed of a hardened steel plate that has been quenched. Here, the ratchet 110 described above corresponds to the “other-side connecting member” of the present invention, and the guide 120 corresponds to the “one-side connecting member” of the present invention, and each of the poles 130, the rotating cam 140, the hinge cam 150, and The anti-rotation structure including the lock spring 160 corresponds to the “anti-rotation mechanism” of the present invention.

<About the structure of the ratchet 110>
As shown in FIG. 18, the ratchet 110 is formed in a substantially disk shape, and a cylinder that protrudes in a cylindrical shape in the axial direction that is an assembly direction to the guide 120 at the outer peripheral edge of the disk main body 111. The portion 112 is formed. The cylindrical portion 112 is formed in a shape in which the outer peripheral edge of the disc body 111 is extruded in a cylindrical shape in the same direction by being half-punched in the thickness direction. On the inner peripheral surface of the cylindrical portion 112, an inner tooth row 112 </ b> A that can press and engage each external tooth row 131 formed on the outer peripheral surface of each pole 130 described later from the inside in the radial direction is formed. Yes. The internal tooth row 112A is formed over substantially the entire circumference of the inner peripheral surface region of the cylindrical portion 112, and has a configuration in which a plurality of internal teeth are arranged at a pitch of 2 in the circumferential direction. . In addition, in one area in the circumferential direction of the cylindrical portion 112 where the internal tooth row 112A is not formed, a riding portion 112B that protrudes in a smooth circular arc shape toward the inside in the radial direction is formed. Yes. The riding-up portion 112B is formed so as to protrude inward in the radial direction from the inner tooth row 112A.

  In addition, a through hole 111A penetrating in a round hole shape is formed at the center of the disc body 111 of the ratchet 110 described above. In the through hole 111A, an operation pin 105A to be inserted and attached to a hinge cam 150 described later is inserted from the outside in the axial direction. Further, as shown in FIGS. 19 to 20, four dowels 111 </ b> B projecting in an oval shape are formed on the outer surface of the disc main body 111 of the ratchet 110, arranged at equal intervals in the circumferential direction. It is said that it was in the state. These dowels 111B are formed by half-cutting a part of the disc body 111 of the ratchet 110 in the plate thickness direction. 16 and 21, these dowels 111B are formed on the side frame 102Fa when the outer side surface of the disc body 111 of the ratchet 110 is connected to the outer side surface of the side frame 102Fa of the seat back 102. Each of the four dowel holes 102Fa1 is fitted into each of the four dowel holes 102Fa1 so as to function as a coupling portion integrally coupled by welding. The side frame 102Fa of the seat back 102 is further formed with a circular hole 102Fa2 for allowing the operation pin 105A described above to pass in the axial direction.

<< Configuration of Guide 120 >>
As shown in FIGS. 18 to 19, the guide 120 is formed in a substantially disc shape having an outer diameter that is slightly larger than the ratchet 110 described above, and the ratchet is formed on the outer peripheral edge of the disc body 121. The cylindrical part 122 which protrudes cylindrically in the axial direction used as the assembly direction to 110 is formed. The cylindrical portion 122 is formed in such a size that the cylindrical portion 112 of the ratchet 110 can be gently fitted into the cylinder. The guide 120 is in a state in which the cylindrical portion 112 of the ratchet 110 is fitted into and assembled with the cylindrical portion 122 in the above-described cylindrical portion 122, so that the guide 120 is gradually fitted into the inside and outside of the ratchet 110. It can be assembled in a state where it is supported inside and outside. The guide 120 slides on the ratchet 110 with respect to the ratchet 110 by a ring member 170 (described later) that is mounted between the cylindrical portion 122 and the cylindrical portion 112 of the ratchet 110 from the outer peripheral side. It is set in a state assembled so as to be prevented from coming off in the axial direction so as to be able to rotate relative to each other (see FIGS. 16 to 17 and FIG. 21).

  A through hole 121A penetrating in a round hole shape is formed at the center of the disc main body 121 of the guide 120 described above. Inside the through hole 121A, a shaft portion 152 of a hinge cam 150, which will be described later, is inserted from the inside in the axial direction to the outside and is pivotally attached so as to be rotatable. Further, as shown in FIG. 18, three dowels 121B protruding in an oval shape are formed on the outer surface of the disc main body 121 of the guide 120 described above at intervals of 90 degrees in the circumferential direction. It is said that it was in the state. Specifically, each of the dowels 121B is formed on the outer surface of the disc main body 121 of the guide 120 on a circumferential area where three cam housing grooves 124B described later are formed. Each of the dowels 121B described above is formed by half-cutting a part of the disc body 121 of the guide 120 in the thickness direction. 17 and 21, these dowels 121B are formed on the side frame 103Fa when the outer surface of the disc body 121 of the guide 120 is applied to the outer surface of the side frame 103Fa of the seat cushion 103 and joined. Each of the three dowel holes 103Fa1 is fitted into each of the dowel holes 103Fa1 so as to function as a coupling portion integrally coupled by welding. The side frame 103Fa of the seat cushion 103 is further provided with a through hole 103Fa2 through which the operation pin 105A and the lock spring 160, which will be described later, mounted on the outer surface of the disc body 121 of the guide 120 can be passed in the axial direction. Is also formed.

  Further, as shown in FIGS. 18 to 19, the guide 120 described above has a fan in the axial direction that is the assembly direction to the ratchet 110 at four positions in the circumferential direction of the inner surface of the disk body 121. A guide wall 123 protruding in a mold shape is formed. These guide walls 123 are formed by extruding a part of the disc body 121 of the guide 120 into a fan shape that expands in the radial direction in the same direction by half-cutting in the plate thickness direction. It is said that it was in the state. Then, as shown in FIG. 19, by forming the guide walls 123 described above, concave areas that can accommodate three poles 130 to be described later in the circumferentially arranged regions of the respective guide walls 123. The pole housing groove 124A is formed. Each guide wall 123 described above is configured to support each pole 130 set in each pole receiving groove 124A described above from both sides in the circumferential direction so as to be moved only inward and outward in the radial direction. ing. In addition, due to the formation of the guide walls 123 described above, a concave cam housing capable of housing a rotating cam 140 (described later) in a state in which the rotating cam 140 can be axially rotated in the central region of the guide 120 surrounded by the guide walls 123. A groove 124B is formed.

  Of the four guide walls 123 described above, the upper two guide walls 123 in the figure, in which the poles 130 are not disposed, are respectively provided with the rotating cams 140 set in the cam housing grooves 124B on the outer peripheral side. An extending portion 123A that can be applied and supported is formed. Due to the support by the extending portions 123A, the rotating cam 140 supports the pole 130, which will be described later, at three positions offset in the circumferential direction from the inside in the radial direction, thereby acting on the reaction force deflected upward in the figure. Even if it receives, it will be kept as the state where the balance of power was taken (refer to Drawing 22).

  The three pole housing grooves 124A formed in the circumferentially arranged region of each guide wall 123 and the cam housing groove 124B formed in the central portion of the guide 120 are respectively pushed out of the guide walls 123 described above. As a part of the guide groove 124 that is formed in a relatively concave shape by molding, the guide groove 124 is formed in a shape that is indented flush with each other. As described above, the above-described guide 120 is in a state where the three poles 130, the rotary cam 140, and the hinge cam 150 that are assembled with the ratchet 110 are supported.

  Further, as shown in FIG. 19, a spring hooking portion 125 for hooking an outer end of a lock spring 160 described later is formed on the outer surface of the disc main body 121 of the guide 120 described above. Yes. The spring hook 125 is formed by half-cutting a part of the disc body 121 of the guide 120 in the plate thickness direction. The spring hooks 125 are arranged at positions (two adjacent to each other) at equal intervals with the three dowels 121B formed on the outer surface of the disk main body 121 at intervals of 90 degrees in the circumferential direction. The two dowels 121B are formed at positions spaced 90 degrees apart in the circumferential direction. The spring hook portion 125 has a shape having a constriction at an intermediate portion so that an outer end portion of a lock spring 160 described later can be hooked.

<< Configuration of pole 130 >>
As shown in FIGS. 19 and 22, the three poles 130 are housed and assembled in respective pole housing grooves 124 </ b> A formed on the inner surface of the disc main body 121 of the guide 120. With the above assembly, each pole 130 is supported in the circumferential direction so that it can move only inward and outward in the radial direction along the shape of each pole receiving groove 124A with respect to the guide 120. Yes. As shown in FIG. 21, each pole 130 is accommodated in each of the above-described pole accommodation grooves 124A, and the inner periphery of the cylindrical portion 112 of the ratchet 110 is located at a position where the pole 130 moves outward in the radial direction. An internal tooth row 112A formed on the surface is exposed.

  As shown in FIGS. 18 to 19, external tooth rows 131 that can mesh with the internal tooth row 112 </ b> A of the ratchet 110 described above are formed on the outer peripheral surface of each pole 130 described above. Each external tooth row 131 is formed in a shape in which a plurality of external teeth are arranged at a pitch of 2 degrees in the circumferential direction on the outer peripheral surface of each pole 130 curved in a circular arc surface shape. Each of the above-described poles 130 is pushed outward in the radial direction by the rotating cam 140 when the rotating cam 140 set at the center of the guide 120 is axially rotated as shown in FIGS. (Refer to FIG. 22) or to be pulled back (refer to FIG. 23).

  As shown in FIG. 22, each pole 130 is pushed outward in the radial direction by the rotation of the rotary cam 140, so that the external tooth row 131 formed on the outer peripheral surface of each pole 130 becomes the internal tooth row 112 </ b> A of the ratchet 110. Pressed and meshed. As a result, the respective poles 130 are integrally coupled to the ratchet 110 in the rotational direction, and the relative rotation between the ratchet 110 and the guide 120 is locked via the respective poles 130. That is, in the relationship with the guide 120, each pole 130 can move only inward and outward in the radial direction by the circumferential support by the above-described guide walls 123. Therefore, the ratchet 110 This is because it functions so as to lock the rotation of the ratchet 110 relative to the guide 120 by being integrated with each other.

  Further, as shown in FIG. 23, each pole 130 is pulled back inward in the radial direction by the rotation of the rotating cam 140, so that each pole 130 is released from the meshing state with the internal tooth row 112 </ b> A of the ratchet 110. Thereby, the state in which the relative rotation between the ratchet 110 and the guide 120 is locked is released, and the ratchet 110 and the guide 120 are switched to a state in which the ratchet 110 and the guide 120 can rotate relative to each other. Each of the poles 130 described above is formed in a U-shape having two legs 132 extending inward in the radial direction, and one leg leg 132 is formed inside each U-shape. The hook part 133 which protrudes from is formed.

  As shown in FIG. 22, each of the poles 130 is pushed outward in the radial direction by the leg 132 being pressed from the inside in the radial direction by the rotation cam 140 by the rotation of the rotating cam 140. Yes. Further, as shown in FIG. 23, the pawls 130 are pulled inward in the radial direction by the hooks 144 of the rotating cam 140 when the rotating cam 140 rotates in the direction opposite to the above. It is designed to be pulled back inward in the radial direction.

<< Configuration of Rotating Cam 140 >>
As described above with reference to FIG. 22, the rotating cam 140 is housed and assembled in a cam housing groove 124 </ b> B formed on the inner surface of the disc main body 121 of the guide 120. The above-described rotating cam 140 is in a state of being supported so as to be rotatable with respect to the guide 120 by a hinge cam 150 to be described later, which is inserted into the central portion and assembled. As shown in FIG. 21, the rotating cam 140 is formed in a shape having the same thickness as each of the above-described poles 130. When the rotating cam 140 is housed in the above-described cam housing groove 124B, each of the poles 130 is formed. And arranged in the same position in the axial direction.

  As shown in FIGS. 22 to 23, the rotating cam 140 described above can have the leg portions 132 of the poles 130 inserted on the left and right sides of the figure facing the poles 130 and on the lower surface portions, respectively. Recesses 142, shoulders 143 on which the legs 132 of the respective poles 130 that have entered the recesses 142 are pushed up so as to be pushed outward in the radial direction by the rotation operation of the rotation cams 140, and the rotation cams 140 in the opposite direction. A hook 144 is formed which is hooked to the hooking portion 133 of each pole 130 by the rotation operation and pulls each pole 130 inward.

  The rotating cam 140 is set in a state that an operating portion 153 of a hinge cam 150 (described later) is assembled in an axial direction so as to be integrated in a rotating direction in a through hole 141 formed in the center portion thereof. Yes. Specifically, the through-hole 141 is formed in a hole shape, and the operation part 153 formed in a hook shape of the hinge cam 150 is assembled to be integrated with the operation part 153 in the rotation direction. It can be assembled to become. As a result of the assembly, the rotary cam 140 is rotated integrally with the hinge cam 150 by a movement in which the hinge cam 150 is axially rotated to one side or the other side in the rotational direction.

  As shown in FIG. 22, the rotary cam 140 is normally pushed in the same direction because the hinge cam 150 described above is rotated and biased clockwise by a lock spring 160 described later. It is set as the state hold | maintained in the state which was carried out. As a result, the rotating cam 140 pushes out the legs 132 of the poles 130 outwardly in the radial direction by the shoulders 143 formed on the left and right sides and the lower surfaces of the rotating cam 140, respectively. The recliner 104 is held in a locked state by meshing with the inner tooth row 112A.

  As shown in FIG. 23, the rotating cam 140 is configured so that the hinge cam 150 is rotated in the direction opposite to the urging direction by lifting the reclining lever 105 (see FIG. 15). The operation unit 153 is rotated in the counterclockwise direction in the drawing. As a result, the rotating cam 140 is moved while the concave portions 142 formed on the left and right sides and the lower surface portions of the rotating cam 140 move to positions immediately below the legs 132 of the poles 130 (inner positions in the radial direction). Each hook 144 extending from each surface portion is gradually and deeply hooked to the hooking portion 133 of each pole 130, and each pole 130 is pulled inward in the radial direction to remove from the meshed state with the ratchet 110. To. As a result, the locked state of the recliner 104 is released. In addition, when the operation of the reclining lever 105 is returned, the rotating cam 140 is rotated in the clockwise direction in the figure by the operating portion 153 of the hinge cam 150 that rotates again by receiving the urging force from the lock spring 160, so that each pole The state is returned to the state in which 130 is engaged with the internal tooth row 112A of the ratchet 110 (the state where the recliner 104 is rotationally locked).

  By the way, the rotating cam 140 that pushes each pole 130 described above outward in the radial direction has a relative rotational position between the ratchet 110 and the guide 120 described above. When the above-described riding section 112B is located in the movement destination area of the pole 130C), even if each pole 130 is pushed outward in the radial direction, the one pole 130C does not move to the riding section 112B. By climbing up and being stopped in the middle, all the pawls 130 are stopped at a position just before the meshing movement of the poles 130 is engaged. As described above, the region where the recliner 104 cannot be locked due to the one pole 130C riding on the riding section 112B is the region of the free zone described above with reference to FIG. 15 (stopping the lifting operation of the reclining lever 105). The backrest angle of the seat back 102 is a region that cannot be returned to a fixed state. Further, the area where the recliner 104 can be locked without climbing any of the poles 130 on the riding part 112B (the area where the riding part 112B is located in the upper area between the poles 130B and 130C in FIG. 23). However, this is also the region of the lock zone described above with reference to FIG. 15 (the region where the backrest angle of the seat back 102 is returned to the fixed state by stopping the lifting operation of the reclining lever 105).

  Here, of the three poles 130 (130A to 130C) described above, the pole 130A disposed in the lower pole housing groove 124A shown in FIGS. 22 to 23 is a first divided into two in the circumferential direction. It is comprised by piece 130A1 and 2nd piece 130A2. The first piece 130A1 is configured to occupy most of the shape of the pole 130A, the outer tooth row 131 described above is formed on the outer peripheral surface, and the leg portion 132 on one side of the pole 130A is formed on the inner peripheral portion. And a hook portion 133 are formed. The second piece 130A2 occupies a shape of a part of the pole 130A smaller than the first piece 130A1 described above, and the outer tooth row 131 is not formed on the outer peripheral surface thereof, and the other piece of the pole 130A is formed. It is formed in a small piece shape enough to form the leg portion 132 on the side. The dividing line that divides the pole 130A into the first piece 130A1 and the second piece 130A2 includes a vertical line that divides them straight in the vertical direction in the figure, and a shape in which these are obliquely bent into a horizontal V-shape. And an oblique line that is divided into two.

  As a result of the above division, as shown in FIG. 22, the first piece 130A1 is straight on the left side in the figure adjacent to the second piece 130A2 in the left direction (the direction perpendicular to the forward and backward movement direction of the pole 130A). A vertical surface 130A1a that faces the surface, a first inclined surface 130A1b that faces diagonally in the lower left direction in the figure, and a second inclined surface 130A1c that faces diagonally in the upper left direction in the figure are formed. Also, the second piece 130A2 has a right side in the drawing facing the vertical surface 130A1a of the first piece 130A1 on the right side in the drawing adjacent to the first piece 130A1 (a direction perpendicular to the moving direction of the pole 130A). A vertical surface 130A2a that faces straight to the surface, a first inclined surface 130A2b that faces the first inclined surface 130A1b of the first piece 130A1 and that faces obliquely in the upper right direction in the figure, and a second inclined surface of the first piece 130A1 A second inclined surface 130A2c that faces the surface 130A1c and is inclined obliquely in the lower right direction in the figure is formed.

  As shown in FIG. 22, the pole 130 </ b> A having the divided shape is configured such that the leg 132 of the second piece 130 </ b> A <b> 2 has a radius due to the shoulder 143 of the rotary cam 140 when the rotary cam 140 rotates clockwise. Pushed out of the direction. By this extrusion, the second inclined surface 130A2c of the second piece 130A2 presses the second inclined surface 130A1c of the first piece 130A1 obliquely outward in the radial direction, and the first piece 130A1 and the second piece 130A2 Are pushed outward in the radial direction while being rubbed in the mutually opposite circumferential directions, and the external tooth row 131 of the first piece 130A1 is pressed against the internal tooth row 112A of the ratchet 110 to be engaged. . At this time, the first piece 130A1 and the second piece 130A2 are each rubbed in the mutually opposite circumferential directions to widen the overall lateral width, and support each of the outer sides in the circumferential direction. The outer tooth row 131 of the first piece 130A1 is pressed against the inner tooth row 112A of the ratchet 110 so as to be engaged with the guide wall 123. Thus, the pole 130A is held in a state of being engaged with the ratchet 110 in a state in which the play in the circumferential direction with respect to the guide 120 is eliminated.

  That is, each of the pole receiving grooves 124A described above has a groove width wider than the lateral width of each pole 130 in order to secure the assembling property and the sliding property of each pole 130 assembled therein. . As a result, even when each pole 130 is engaged with the internal tooth row 112A of the ratchet 110, the ratchet 110 and the guide 120 are separated by the gap in which each pole 130 rattles in the circumferential direction in each pole receiving groove 124A. Are in a state of rattling in the circumferential direction. However, since the one divided pole 130A is configured to mesh with the ratchet 110 in a state in which the lateral width is widened and the backlash in the circumferential direction with respect to the guide 120 is packed as described above, the ratchet 110 and the guide 120 can be prevented from rotating in the circumferential direction.

  Further, as shown in FIG. 24, the rotating cam 140 is formed such that a part of its outer peripheral surface is formed on the guide 120 during the operation of pressing each pole 130 against the inner tooth row 112 </ b> A of the ratchet 110 by the rotation. It is pressed prior to the extending portion 123A of the upper left guide wall 123 (contact point C1), and receives an eccentric force that is pushed against the guide 120 from the center toward the lower right in the figure. As a result, the rotating cam 140 pushes out the lower pole 130A and the right pole 130B in the figure so as to push and move the ratchet 110 to a position beyond the position where it presses against the inner tooth row 112A of the ratchet 110. (Contacts C2, C3). Then, by pushing the two poles 130A and 130B to the excess position, the ratchet 110 is pushed to the guide 120 in the lower right direction in the figure, which is the resultant force direction of the pushing force, and the cylindrical portion 112 of the ratchet 110 is pushed. Is pressed against the inner peripheral surface of the cylindrical portion 122 of the guide 120 (contact C4). As a result, since the radial gap set between the cylindrical portion 112 of the ratchet 110 and the cylindrical portion 122 of the guide 120 is filled, the ratchet 110 and the guide 120 are also rattled in the radial direction. Rotation can be stopped in a non-attachable state.

  Specifically, the operation in which the rotating cam 140 pushes the two poles 130A and 130B to the excess positions is performed by the shoulders 143 formed on the lower side and the left outer periphery of the rotating cam 140, respectively. This is performed by pressing the leg 132 of the second piece 130A2 of 130A and the upper leg 132 of the right pole 130B shown in the drawing one by one (contact C2, contact C3). Strictly speaking, each shoulder portion 143 formed at the outer peripheral portion position of the rotating cam 140 corresponding to the other leg portion 132 of each pole 130 has a slight gap between it and the leg portion 132 of each pole 130. In order to prevent the poles 130 from being disengaged from the state in which they are engaged with the ratchet 110, the poles 130 are each awaited and supported on the inner side in the radial direction. Strictly speaking, the extending portion 123A formed on the guide wall 123 on the upper right side of the drawing also has a slight gap between the outer peripheral surface of the rotary cam 140 and each pole 130 is engaged with the ratchet 110. When a load is applied in a direction to be removed from the state, the rotating cam 140 functions so as to receive a reaction force that is biased upward in the drawing.

  As described above, the rotating cam 140 rotates the lower pole 130A and the right pole 130B (two poles arranged adjacent to each other in the circumferential direction) out of the plurality of poles 130 by the rotation. It is configured to push out to the excess position. Further, the extending portion 123A that applies the eccentric force in the pushing direction to the rotating cam 140 is located in a point-symmetric region position with respect to the central portion of the guide 120 in the region between the circumferential positions of the two poles 130A and 130B. The outer circumferential portion of the rotating cam 140 is pressed in advance. As a result, the ratchet 110 is configured to be pressed in the radial direction toward the guide 120 at two points in the circumferential direction, so that a stable pressing state can be obtained.

<< Configuration of Hinge Cam 150 >>
As shown in FIGS. 18 to 19, the hinge cam 150 includes a rectangular tube-shaped spring hanging portion 151, a cylindrical shaft portion 152, and an operation portion 153 having a rectangular shape protruding outward in the radial direction. The shaft member is formed side by side in the direction. At the center of the hinge cam 150, there is formed a through hole 150A penetrating in the shape of a square hole in the axial direction. The hinge cam 150 has a spring hook 151 that passes through the through hole 24 formed in the center of the guide 120 together with the shaft 152 from the inside, so that the operation portion 153 is inside the disc main body 121 of the guide 120. The spring hooking portion 151 protrudes to the outside of the guide 120 at a position where it is brought into contact with the side surface, and the shaft portion 152 is fitted into the guide 120 as a state in which the shaft portion 152 is fitted into the through hole 121A of the guide 120 so as to be rotatable. ing.

  The hinge cam 150 is integrally formed in the rotational direction by fitting the inner end portion of the lock spring 160 wound in a rectangular shape on the rectangular outer peripheral portion of the spring hook portion 151 protruding outside the guide 120. It is assumed that it is hung on a typical state. As shown in FIG. 17, the lock spring 160 is constituted by a spiral spring, and is disposed on the outer surface of the guide 120. The inner end of the lock spring 160 is hooked on the spring hook 151 of the hinge cam 150 described above. The outer end portion is provided in a state of being hooked on a spring hooking portion 125 formed to protrude from the outer surface of the guide 120. Thereby, the lock spring 160 is configured to always exert an urging force that rotates the hinge cam 150 in the direction in which the rotation cam 140 is locked with respect to the guide 120.

  Then, as shown in FIG. 21, the central portion (inside the through hole 150A) of the hinge cam 150 assembled between the ratchet 110 and the guide 120 has an end portion on the side where the spring hook portion 151 is formed. The operation pin 105A is inserted and is firmly joined together by welding. A flange portion having a diameter larger than that of the through hole 150A of the hinge cam 150 is formed at the end of the operation pin 105A opposite to the side inserted into the through hole 150A. The reclining lever 105 is integrally connected to the head by welding. As a result, the hinge cam 150 is integrally connected to the reclining lever 105 via the inserted operation pin 105A, and is rotated by the operation of lifting the reclining lever 105 as described above with reference to FIG. The cam 140 is rotated in the release operation direction (direction in which the lock state of each pole 130 is released).

  As shown in FIG. 21, the above-described operation pin 105 </ b> A is the same as the operation pin 105 </ b> A in which the end portion inserted into the through hole 150 </ b> A of the above-described hinge cam 150 is similarly inserted in the recliner 104 on the other side (not shown). The end portion and the connecting rod 105B are connected to each other in an integral state in the rotational direction. As a result, the operation pins 105 </ b> A inserted through the recliners 104 on both sides are operated so as to rotate together at the same time by operating the reclining lever 105. The operation part 153 of the hinge cam 150 described above is in a state in which the shaft part 152 described above is attached to the inner side surface of the disc main body 121 of the guide 120 by being mounted in the through hole 121A of the guide 120. It can be assembled in a state of being set in the through-hole 141.

<< Configuration of Ring Member 170 >>
As shown in FIGS. 18 to 19, the ring member 170 is formed by punching a thin steel plate into a hollow disc shape and further drawing the punched outer peripheral side portion in the plate thickness direction. The whole is formed in a substantially cylindrical shape having a hollow disk-like seat. Specifically, the ring member 170 includes a hollow disk-shaped pressing portion 171 that faces in the axial direction, a surrounding portion 172 that extends in a cylindrical shape in the axial direction from the outer peripheral edge portion of the pressing portion 171, and a surrounding portion. The coupling portion 173 has a cylindrical shape that is larger than 172 and extends in the axial direction.

  The ring member 170 described above incorporates the ratchet 110 and the guide 120 described above into the cylinder in order in the axial direction, so that the holding portion 171 is a cylindrical portion 112 that is the outer peripheral portion of the ratchet 110 as shown in FIG. The rising portion 173A rises from the surrounding portion 172 to a large cylindrical shape around the coupling portion 173, with the surrounding portion 172 surrounding the cylindrical portion 112 of the ratchet 110 from the outer peripheral side. So that the coupling portion 173 is fitted into the cylindrical portion 122 of the guide 120 from the outer peripheral side. It has become.

  Then, after the assembly, the tip caulking portion 173B extending outward in the axial direction from the cylindrical portion 122 of the guide 120 of the coupling portion 173 of the ring member 170 described above is connected to the cylindrical portion 122 of the guide 120 in the axial direction. The rising portion 173A abutted from the inside is used as a support in the axial direction, and is caulked to be bent inward in the radial direction. As a result, the cylindrical portion 122 of the guide 120 is strongly sandwiched in the axial direction between the bent caulking portion 173B and the rising portion 173A, and the coupling portion 173 of the ring member 170 becomes the cylindrical portion of the guide 120. The state is integrally coupled to 122. With the above configuration, the ratchet 110 and the guide 120 are held in a state where they are prevented from coming off in the axial direction via the ring member 170.

  As shown in FIGS. 21 and 26, the holding portion 171 is applied to the cylindrical portion 112, which is the outer peripheral portion of the ratchet 110, from the outside in the axial direction, and the ratchet 110 is detached from the guide 120 in the axial direction. It is designed to be held so as not to let it. As shown in FIG. 26, the above-described pressing portion 171 has an overhang projecting in a radially bent shape inwardly in the radial direction toward the outer side in the axial direction. The part 171B is formed by being bent into a shape that is connected endlessly over the entire circumference.

  As shown in FIG. 21, the overhanging portion 171B has a slight gap T4 (see FIG. 26) between the outer peripheral surface 111C of the disc body 111 of the ratchet 110 and the outer peripheral surface 111C. Is formed so as to project obliquely inward in the radial direction so as not to contact. Specifically, as shown in FIG. 26, the above-described overhanging portion 171B is a corner on the inner side in the axial direction of the above-described outer peripheral surface 111C that is formed along with the half-punching processing of the above-described cylindrical portion 112 from the disc body 111. The surface is formed so as to project obliquely in a shape substantially parallel to the sag surface 111D that rises in an inclined shape on the surface, and is directed radially inward to a position where the sag surface 111D and the radial arrangement overlap. The shape is long and extended obliquely. With the above-described configuration, the holding portion 171 has an increased second moment in section around the bending point 171C with the surrounding portion 172 as the above-described overhanging portion 171B protrudes, so that the cylindrical portion 112 moves outward in the axial direction. It becomes difficult to bend and deform with respect to the pressed force.

  Specifically, the holding portion 171 is hard to be bent and deformed because its hardness is increased by the bending work hardening of the protruding portion 171B. More specifically, the pressing portion 171 itself has an endlessly connected ring shape, and the above-described overhanging portion 171B is formed endlessly over the entire inner peripheral edge. The peripheral length of the inner peripheral edge is thickened and reinforced in such a way that it is difficult to extend, and this also makes it difficult to bend and deform outward in the axial direction.

  The pressing portion 171 described above is half-cut in the axial direction on the inner peripheral edge of the disk portion facing the outer surface of the cylindrical portion 112 of the ratchet 110 that is radially outward from the overhanging portion 171B. Projected portions 171A that are processed and protrude are formed at a plurality of locations in the circumferential direction so as to be arranged at equal intervals. By these projecting portions 171A, the pressing portion 171 is configured to be applied in a state close to point contact in the axial direction with respect to the cylindrical portion 112 of the ratchet 110, and accompanying the contact with the ratchet 110 when the ratchet 110 rotates. It has a configuration that hardly generates sliding friction resistance.

  By the way, as shown in FIGS. 19 and 22 to 23, each guide wall 123 of the guide 120 that supports each of the poles 130 described above from both sides in the circumferential direction has an outer peripheral edge of an intermediate portion in the circumferential direction. A recessed portion 123B that is partially depressed is formed at each location. Each concave portion 123B is formed in a concave shape with respect to each guide wall 123 by being left without being half-punched when each guide wall 123 is half-punched in the plate thickness direction. . Each concave portion 123B is formed in a concave shape in a rounded right-angled triangle shape that opens toward the outer peripheral side of each guide wall 123.

  Each guide wall 123 described above has a configuration in which each of the poles 130 can be supported with high support rigidity from both outer sides in the circumferential direction by forming the above-described recesses 123B at the intermediate portion thereof. However, as shown in FIG. 25, when the recliner 104 receives an input of a large load accompanied by forced deformation in the rotational direction due to the occurrence of a vehicle collision or the like, each pole engaged with the ratchet 110 130 can be deformed by being pushed together with the ratchet 110 in a circumferential direction. In the present embodiment, the recesses 123B having the above shape are formed in the guide walls 123, so that at the corners on the radially inner side of any one of the recesses 123B (the upper left recess 123B in the drawing) when a heavy load is input, A crack Cr in the direction of 45 degrees obliquely enters. By the above deformation, the guide walls 123 are deformed while the pawls 130 are engaged with the ratchet 110, and an unreasonable load input to the recliner 104 can be absorbed and released.

  That is, since each of the recesses 123B described above is formed at a location spaced circumferentially from the contact surface with each pole 130 in each guide wall 123, each guide wall 123 has each recess 123B on the contact surface. Compared to the case where it is formed in the exposed part, the pressing force received from each pole 130 when supporting each pole 130 from both sides in the circumferential direction is less likely to reach the formation region of each recess 123B. Each pole 130 can be supported without lowering the support rigidity for supporting each pole 130. Therefore, in a state where the recliner 104 is rotationally locked, the above-described configuration with high support rigidity enables the side frame 102Fa (see FIG. 15) of the seat back 102 to be supported firmly without being bent back and forth. When it occurs, the side frame 102Fa of the seat back 102 is bent rearward so that it is not easy to cause whipping.

  Each of the guide walls 123 is provided when a large load (a large load that causes the back of the occupant to press against the seat back 102 due to the rear impact of the vehicle) is input to the recliner 104. In this case, the pressing force received from each pole 130 extends to the formation region of each recess 123B, causing stress concentration in each recess 123B and plastically deforming. Specifically, each depression 123B formed in each guide wall 123 receives a high pressing force from the vicinity of the outer peripheral edge near the load input point of each pole 130 that receives a load input in the rotational direction from the meshed ratchet 110. Formed at the outer periphery. As a result, each guide wall 123 is plastically deformed by effectively concentrating stress at the site where each recess 123B is formed when the large load is input. Due to the deformation of each guide wall 123, the above-mentioned large load is absorbed while maintaining the state in which each pole 130 is engaged with the ratchet 110 without damaging each pole 130 (while the recliner 104 is kept locked). I can take it. Therefore, even if the structural strength of each pole 130 is not excessively increased, a configuration that can withstand the input of a large load can be obtained without releasing the locked state of the recliner 104 when a large load is input.

<Summary>
In summary, the recliner 104 of this embodiment is configured as follows. That is, a recliner (104) that bears a reclining adjustment mechanism for a vehicle seat (101), two disk-like connecting members (110, 120) assembled in an axial direction so as to be relatively rotatable with each other; An anti-rotation mechanism (130, 140, 150, 160) that is provided between the two connecting members (110, 120) and stops the relative rotation thereof, and an outer peripheral portion of the two connecting members (110, 120) (112, 122) and a ring member (170) that holds them in an assembled state in the axial direction. The ring member (170) is coupled to the outer peripheral portion (122) of the one side coupling member (120), the coupling portion (173) is extended in the axial direction from the coupling portion (173), and the other side coupling member (110). ) That surrounds the outer peripheral portion (112) from the outer peripheral side, and the other connecting member (110) that is bent radially inward from the end portion extending in the axial direction of the surrounding portion (172). And a pressing portion (171) applied to the outer peripheral portion (112) of the outer peripheral portion (112) from the outside in the axial direction. An overhang portion (171B) is formed in the holding portion (171) so as to bend and protrude outward in the axial direction.

  With such a configuration, the overhanging portion (171B) formed in the pressing portion (171) of the ring member (170) is bent at the bending portion (172) with the surrounding portion (172) of the pressing portion (171) ( 171C) the moment of inertia of the cross section around is increased, and the pressing portion (171) is less likely to be deformed by the force pressed outward in the axial direction from the connecting member (110) on the other side. With the above configuration, it is possible to increase the structural strength of the ring member (170) that prevents the axial connection between the two disk-shaped connecting members (110, 120).

  Moreover, the overhang | projection site | part (171B) is formed in the edge part inside the radial direction of a holding | suppressing part (171). By adopting such a configuration, the cross-section secondary moment around the bending point (171C) with the enclosure portion (172) of the holding portion (171) is optimally increased by the overhang portion (171B), and the ring The structural strength of the member (170) can be increased appropriately, and the overhang portion (171B) can be easily formed.

  In addition, the overhanging portion (171B) projects from the pressing portion (171) obliquely inward in the radial direction toward the outside in the axial direction. By adopting such a configuration, a long projecting length inward in the radial direction as the entire pressing portion (171) can be secured by the shape projecting diagonally inside the projecting portion (171B). The pressing of the other connecting member (110) by the pressing portion (171) can be appropriately performed over a wider range.

  Moreover, the overhang | projection site | part (171B) is made into the cyclic | annular form connected in the circumferential direction endlessly. By adopting such a configuration, the extension of the inner peripheral length of the pressing portion (171) can be appropriately suppressed by the overhanging portion (171B). The pressed deformation can be suppressed more appropriately.

<< About other embodiments >>
As mentioned above, although the embodiment of the present invention has been described using two examples, the present invention can be implemented in various forms in addition to the above examples. For example, the recliner of the present invention can be widely applied to vehicles used for various vehicles such as vehicles other than automobiles such as railways, airplanes, and ships. Further, the continuously variable recliner shown in the first embodiment may have a manual type configuration in addition to the electric type.

  In the first embodiment, the outer gear and the cylindrical portion are formed in the upper gear that constitutes one of the two gear members, and the inner gear that meshes with the outer gear in the lower gear that constitutes the other of the two gear members. A configuration is shown in which a gear and a circular hole for receiving the cylindrical portion are formed. However, in the configuration of the present invention, an internal gear and a cylindrical portion are formed on the upper gear that constitutes one of the two gear members, as in the configuration disclosed in Japanese Patent Application Laid-Open No. 2015-146873. The lower gear constituting the other of the two gear members may be configured such that an external gear that meshes with the internal gear and a circular hole that receives the cylindrical portion are formed.

  Further, the pressing portion and the overhanging portion of the ring member are not limited to those formed in an annular shape connected endlessly in the circumferential direction, but intermittently or circumferentially at various locations in the circumferential direction. It may be partially formed in a part of the direction. The same applies to the enclosure. Further, the overhanging portion may be formed in a shape bent at a right angle from the pressing portion to the outside in the axial direction. Moreover, the overhang | projection site | part may be formed in the shape bent in the curved shape from the holding | suppressing part. Further, the overhanging part may be formed at an intermediate part between the inner edge part in the radial direction and the outer edge part in addition to the inner edge part in the radial direction of the pressing part. The overhanging part may be formed by molding other than press such as forging.

  In addition, since the ring member has a step shape between the enclosure and the coupling portion as shown in the second embodiment, the structure strength as the ring member can be further increased, and thus such a shape. May be applied to the ring member of the first embodiment.

1 seat (vehicle seat)
2 Seat back 2F Side frame 2Fa Through hole 2Fb Dowel hole 3 Seat cushion 3F Reclining plate 3Fa Fitting hole 3Fb Dowel hole 4 Recliner 5 Drive unit 5R Connecting rod 5Ra Washer 10 Lower gear (other side connecting member)
10R Center position 11 Internal gear (outer periphery)
11A Inner tooth row 11B Outer peripheral surface 11C Sag surface 12 Circular hole 13 Dowel 20 Upper gear (connecting member on one side)
20R Center position 21 External gear 21A External tooth row 22 Cylindrical part 22A Through hole 23 Dowel 24 Recessed part (outer peripheral part)
25 Convex part 40 Wedge (rotation stop mechanism)
41 Hook 50 Lock spring (rotation stop mechanism)
51 End portion 60 Hinge bush 60A Hexagonal hole 61 Cover portion 61A Spring pressing portion 62 Shaft portion 63 Operation projection 64 Projection portion 70 Ring member 71 Coupling portion 71A Indented portion 72 Enclosure portion 73 Holding portion 73A Overhang portion 73B Bending point 80 Cap We Welded area P1, P2 Press point S Circular gap T1, T2, T3 Gap 101 Sheet (vehicle seat)
102 Seat back 102F Back frame 102Fa Side frame 102Fa1 Dowel hole 102Fa2 Through hole 103 Seat cushion 103F Cushion frame 103Fa Side frame 103Fa1 Dowel hole 103Fa2 Through hole 104 Recliner 105 Recliner lever 105A Operation pin 105B Connecting member)
111 disc body 111A through hole 111B dowel 111C outer peripheral surface 111D sag surface 112 cylindrical portion (outer peripheral portion)
112A Inner tooth row 112B Riding part 120 Guide (connecting member on one side)
121 disc main body 121A through hole 121B dowel 122 cylindrical part (outer peripheral part)
123 Guide wall 123A Extension part 123B Recessed part 124 Guide groove 124A Pole accommodation groove 124B Cam accommodation groove 125 Spring hook part 130 Pole (rotation stop mechanism)
130A to 130C Pole 130A1 First piece 130A1a Vertical surface 130A1b First inclined surface 130A1c Second inclined surface 130A2 Second piece 130A2a Vertical surface 130A2b First inclined surface 130A2c Second inclined surface 131 External tooth row 132 Leg 133 Hook 140 Cam (rotation stop mechanism)
141 Through-hole 142 Concavity 143 Shoulder 144 Hook 150 Hinge cam (rotation stop mechanism)
150A Through hole 151 Spring hook portion 152 Shaft portion 153 Operation portion 160 Lock spring (rotation stop mechanism)
170 Ring member 171 Holding part 171A Protruding part 171B Overhanging part 171C Bending point 172 Enclosing part 173 Coupling part 173A Standing part 173B Caulking part C1 to C4 Contact Cr Crack T4 Gap

Claims (4)

A recliner responsible for a vehicle seat reclining adjustment mechanism,
Two disk-shaped connecting members assembled in the axial direction so as to be rotatable relative to each other;
An anti-rotation mechanism that is provided between the two connecting members and stops the relative rotation thereof;
A ring member mounted between the outer peripheral portions of the two connecting members and holding them in an assembled state in the axial direction;
The ring member is coupled to an outer peripheral portion of the one-side connecting member; an enclosure extending in an axial direction from the connecting portion and surrounding the outer peripheral portion of the other connecting member from the outer peripheral side; A pressing portion that is bent inward in the radial direction from the end portion extending in the axial direction of the enclosure portion and applied to the outer peripheral portion of the connecting member on the other side from the outer side in the axial direction;
A recliner in which an overhanging portion that bends and protrudes outward in the axial direction is formed in the pressing portion. The recliner according to claim 1,
A recliner in which the protruding portion is formed at an inner edge in the radial direction of the pressing portion. The recliner according to claim 2,
A recliner in which the projecting portion is bent obliquely inward in the radial direction from the pressing portion toward the outer side in the axial direction. A recliner according to any one of claims 1 to 3,
A recliner in which the projecting portion is formed in an annular shape connected endlessly in a circumferential direction.

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