WO2016060269A1 - 回転動作制御機構及びシート - Google Patents
回転動作制御機構及びシート Download PDFInfo
- Publication number
- WO2016060269A1 WO2016060269A1 PCT/JP2015/079381 JP2015079381W WO2016060269A1 WO 2016060269 A1 WO2016060269 A1 WO 2016060269A1 JP 2015079381 W JP2015079381 W JP 2015079381W WO 2016060269 A1 WO2016060269 A1 WO 2016060269A1
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- WO
- WIPO (PCT)
- Prior art keywords
- worm
- rotation
- worm wheel
- fulcrum
- locking
- Prior art date
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
- B60N2/2231—Worm and worm gear articulations
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- A—HUMAN NECESSITIES
- A47—FURNITURE; DOMESTIC ARTICLES OR APPLIANCES; COFFEE MILLS; SPICE MILLS; SUCTION CLEANERS IN GENERAL
- A47C—CHAIRS; SOFAS; BEDS
- A47C1/00—Chairs adapted for special purposes
- A47C1/02—Reclining or easy chairs
- A47C1/022—Reclining or easy chairs having independently-adjustable supporting parts
- A47C1/024—Reclining or easy chairs having independently-adjustable supporting parts the parts, being the back-rest, or the back-rest and seat unit, having adjustable and lockable inclination
- A47C1/025—Reclining or easy chairs having independently-adjustable supporting parts the parts, being the back-rest, or the back-rest and seat unit, having adjustable and lockable inclination by means of a rack-and-pinion or like gearing mechanism
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/02—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable
- B60N2/22—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable
- B60N2/2227—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles the seat or part thereof being movable, e.g. adjustable the back-rest being adjustable and provided with braking systems
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2/00—Seats specially adapted for vehicles; Arrangement or mounting of seats in vehicles
- B60N2/90—Details or parts not otherwise provided for
- B60N2/919—Positioning and locking mechanisms
- B60N2/933—Positioning and locking mechanisms rotatable
- B60N2/938—Positioning and locking mechanisms rotatable and provided with braking systems
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60N—SEATS SPECIALLY ADAPTED FOR VEHICLES; VEHICLE PASSENGER ACCOMMODATION NOT OTHERWISE PROVIDED FOR
- B60N2205/00—General mechanical or structural details
- B60N2205/20—Measures for elimination or compensation of play or backlash
Definitions
- the present invention relates to a rotation operation control mechanism that allows rotation between members that rotate relative to each other or locks at an arbitrary angle. More particularly, the present invention relates to a rotation operation control mechanism suitable as a reclining adjuster for appropriately adjusting a tilt angle of a seat back with respect to a seat cushion. The present invention also relates to a seat incorporating such a rotational motion control mechanism.
- Patent Document 1 and Patent Document 2 as a lock mechanism when the seat back is stopped at a predetermined inclination angle, a technique using a slide member that abuts against the tooth surface of the worm and stops the rotation of the worm by friction, and A technique is disclosed in which the worm itself is translated toward the worm wheel and the worm is pressed against the worm wheel to stop the rotation of the worm by friction. In this structure, a large pressing force is required to obtain a necessary locking force.
- the bearings that support both ends of the worm in the axial direction are strictly aligned, and the size of the backlash is adjusted based on a certain meshing relationship. Must be adjusted. Further, since the backlash also changes due to manufacturing errors such as worms and wear and deformation of teeth due to use, it is difficult to reduce the variation among products. Even when the worm is pressed against the worm wheel at the time of locking, a clearance remains between the teeth of the worm and the worm wheel along the thrust direction of the worm. In some cases, it may become a cause of noise and noise.
- Patent Document 3 and Patent Document 4 have proposed the following mechanisms in Patent Document 3 and Patent Document 4 as mechanisms that can eliminate the clearance in the thrust direction of the worm when locked.
- Patent Document 3 a worm having recesses formed on both end surfaces is used, and a bearing having a recess on the surface facing the worm is fixed to a bracket, and a ball is loaded between the worm and the bearing.
- a reclining adjuster has been proposed in which a support mechanism is employed and when the seat back is stopped at a predetermined inclination angle, the tooth portion on the other end side in the axial direction of the worm is pressed against the worm wheel and locked by the pressing means.
- Patent Document 4 in order to make the worm movable range larger than the technique of Patent Document 3, a movable bearing that moves up and down is provided on the other end side in the axial direction of the worm, and the movable bearing is moved up and down to form a worm wheel. Proposes a pressing mechanism.
- Patent Documents 1 to 4 are mechanisms for pressing the worm against the worm wheel when locked, although the worm can be displaced in a direction substantially perpendicular to the axial direction thereof. For this reason, in a state where the worm during normal rotation operation is not pressed as in locking, the worm needs to be supported at a predetermined position so as to mesh with the worm wheel and rotate. If the position of the worm is not accurate, the rotation of the worm itself causes a whirling vibration in which the axial ends of the worm flutter up and down, which also has an adverse effect on the rotational movement of the worm itself. There is also a possibility that the smooth rotation operation of the seat back is also hindered.
- the present applicant has arranged two worm wheels sandwiching a worm as international application number: PCT / JP2014 / 062645, and the relative rotation of the first member and the second member, for example, with respect to the seat cushion
- the driving force of the driving side worm wheel arranged below that supports the rotation axis of the seat back acts to rotate the worm
- the driven side worm wheel arranged above is used as the worm.
- a mechanism to reduce backlash between the two by pressing is proposed.
- the worm is relatively rotated by the rotational force of the driven worm wheel, the driven worm wheel is rotated by the rotational force of the worm, and the rotational force of the driven worm wheel is regenerated to the worm. Therefore, the whirling vibration of the worm is suppressed, and the rotational movement of the worm becomes smooth.
- the driven worm wheel is pressed against the worm so that the teeth come into surface contact with each other, that is, one tooth enters the other tooth like a wedge. In comparison, backlash can be reliably reduced, and locking can be performed in a stepless position.
- the present invention has been made in view of the above, and is a case where a structure in which two worm wheels are arranged with a worm interposed therebetween, while maintaining a stable operation during rotation and receiving an external force of a predetermined level or more during locking.
- Another object of the present invention is to provide a rotation operation control mechanism and a seat that can prevent rotation of the worm and further improve the reliability of locking.
- the rotational motion control mechanism of the present invention is a rotational motion control mechanism that controls the second member to be rotatable with respect to the first member and can be held at an appropriate rotational angle.
- the worm that is pivotally supported between a pair of bearing portions arranged at both ends in the axial direction on one of the first and second members, and the worm so as to mesh with the worm in a positional relationship sandwiching the worm.
- the driven worm wheel When locked, the driven worm wheel is moved to the worm It can be locked in a state where the backlash between the two is reduced by operating in the pressing direction, and provided at both ends in the axial direction, and a rotational fulcrum that serves as a fulcrum when the worm rotates, and an axial direction
- One end portion has a lock fulcrum provided at a position different from the rotation fulcrum, and at the time of rotation, the pair of bearings support the rotation fulcrums at both ends in the axial direction, and at the time of lock
- the worm is displaced in the axial direction as the driven worm wheel is pressed against the worm, so that the locking fulcrum is at one end in the axial direction and the rotation is at the other end in the axial direction.
- the fulcrum is supported by the pair of bearing portions, respectively, and the worm advance angle at the time of locking changes so as to be smaller than the advance angle at the time of rotation. .
- each rotation fulcrum of the worm is provided at the center position of both axial ends, and that the lock fulcrum is provided at an eccentric position at one axial end.
- a projecting portion projecting is formed, and the fulcrum at the time of locking is configured to be any part of the groove portion with which the projecting portion abuts.
- the one bearing portion disposed on the one end side in the axial direction of the worm has an elastic portion that elastically supports the rotation fulcrum, and the worm is displaced in the axial direction at the time of locking. It is preferable that the portion bends in the axial direction, whereby the support position by the one bearing portion at one axial end portion of the worm changes from the rotation fulcrum to the lock fulcrum.
- the one bearing portion disposed on the one end side in the axial direction of the worm includes a bearing holder having a through-hole at which a distal end portion of the rotation fulcrum can project outward, and a projection protruding from the through-hole. It is preferable to have a rotation control cam formed in a shape that comes into contact with the distal end of the rotating fulcrum when the worm rotates and separates when the worm is locked. It is preferable to have a structure including a locking pressing member that presses the surface of the driven worm wheel during locking.
- the pressing member at the time of locking is pressed against the opposing surface of the driven worm wheel by the inclined surface.
- the driven worm wheel is rotatably supported via an eccentric shaft whose center of rotation is eccentric from its center position.When the eccentric shaft is rotated, the driven worm wheel is pressed against the worm, Thereby, it is preferable that the backlash between the two is reduced and the transmission of the rotational force is limited.
- the driven worm wheel has a larger mass than the worm, and a force corresponding to the mass of the driven worm wheel acts on the worm to suppress the whirling vibration of the worm.
- the first member and the second member are two members that rotate relatively among a plurality of members constituting the sheet, and are preferably used for the sheet.
- the first member is any member constituting a frame of a seat cushion
- the second member is any member constituting a frame of a seat back
- an inclination angle of the seat back with respect to the seat cushion It is preferably used as a reclining adjuster for adjusting the angle.
- the seat of the present invention is a seat provided with a seat cushion and a seat back, and any one of the rotational operation control mechanisms described above is between two members that rotate relatively among the plurality of members constituting the seat. It is provided. It is preferable that the rotation operation control mechanism is provided as a reclining adjuster between any member constituting the frame of the seat cushion and any member constituting the frame of the seat back.
- the present invention includes a worm, a main drive worm wheel, and a driven worm wheel that are arranged with the worm interposed therebetween. Accordingly, when the second member is rotated relative to the first member, the worm is rotated relatively by the rotational force of the driven worm wheel, the driven worm wheel is rotated by the rotational force of the worm, and the driven side is rotated. The rotational force of the worm wheel is regenerated by the worm. Thereby, the whirling vibration of the worm is suppressed, the rotational motion of the worm becomes smooth, and the relative rotation of the second member with respect to the first member is made smooth.
- each rotation fulcrum set at both axial ends of the worm is supported by the bearing portion, while at the time of locking, it is set at an eccentric position at one end of the worm in the axial direction.
- the locked fulcrum is supported by one bearing, and the rotation fulcrum is supported by the other bearing as it is at the other axial end.
- the advance angle of the worm supported by the pair of bearing portions changes between the rotation and the lock, and the lock is smaller than the rotation. For this reason, even if a rotational force is input from the driven worm wheel, the worm cannot be rotated, so that the locking reliability is improved.
- FIG. 1 is a perspective view seen from the front right side showing the configuration of a back frame to which a reclining adjuster according to an embodiment of the present invention is attached.
- FIG. 2 is a perspective view seen from the front left side of FIG.
- FIG. 3 is an exploded perspective view of FIG.
- FIG. 4 is a side view of FIG.
- FIG. 5A is a view taken along the line II of FIG. 4 for explaining the action when the worm rotates
- FIG. 5B is a view for explaining the action when the worm is locked.
- Fig. 5 (c) is a view taken along the line II-II of Fig. 4 for explaining the action when a heavy load is input when the worm is locked.
- FIG. 6 is an enlarged view taken along the line II of FIG.
- FIG. 4 showing the state when the worm rotates (broken line) and the state when locked (solid line).
- FIG. 7 is a diagram for explaining the operation at the time of locking by the main drive worm wheel, the driven worm wheel, and the worm.
- FIG. 8 is a view for explaining the structure of the center of the eccentric shaft.
- FIGS. 9A and 9B are views for explaining the positional relationship between the center of the eccentric shaft and the center of the driven worm wheel.
- FIG. 10 is a diagram for explaining the operation during rotation by the main drive worm wheel, the driven worm wheel, and the worm.
- FIG. 11 is a diagram showing a test result of the backward moment intensity.
- FIG. 12A is a perspective view showing a reclining adjuster according to another embodiment of the present invention as seen from one side
- FIG. 12B is a perspective view seen from the other side.
- 13 is an exploded perspective view of FIG.
- FIG. 14 is a view for explaining the operation of the above-described other embodiment at the time of unlocking (at the time of reclining operation)
- (a) is a view seen from the cover bracket side
- (b) is (a)
- (C) is a cross-sectional view taken along the line BB of (a).
- FIGS. 15A and 15B are diagrams for explaining the action of the other embodiment at the time of locking, wherein FIG. 15A is a view seen from the cover bracket side, and FIG. 15B is a line AA in FIG. (C) is a cross-sectional view taken along line BB of (a).
- the reclining adjuster 10 which is a typical example of the rotation operation control mechanism of the present invention will be described as an example.
- the reclining adjuster 10 includes a first member (“any one of the seat cushion frames constituting the seat cushion frame) attached to the rear portion of the side frame constituting the cushion frame of the seat cushion.
- a cushion side bracket 1 as a member) a back side mounting portion 2 corresponding to a lower portion of a side frame 20 constituting a back frame 200 of a seat back as a second member, and the back side mounting portion 2 are covered.
- a cover bracket 3 (corresponding to “any member constituting the frame of the seat back”).
- the cushion side bracket 1 is attached to the rear part of the side frame of the seat cushion frame with a bolt or the like.
- the driving side worm wheel 40 is fixed to the cushion side bracket 1 by welding, for example.
- the main driving side worm wheel 40 has a portion protruding in the circumferential direction at the upper part of the cushion side bracket 1, and teeth formed around the protruding range are used areas of the main driving side worm wheel 40.
- the main drive worm wheel 40 may be a gear having teeth formed on the entire circumference, or may be a sector gear having teeth formed only in the use region. Further, both of the main driving worm wheel 40 and the following driven worm wheel 60 include a case where a helical gear is used as the worm wheel.
- Connection holes 2c, 2d, 3c, and 3d are formed in the back side mounting portion 2 and the cover bracket 3 at positions corresponding to substantially the center in the height direction of the cover bracket 3, and the corresponding connection holes 2c and 3c.
- the connecting holes 2d and 3d are connected via connecting rivets 4 and 4 with a predetermined interval.
- Long worm arrangements are provided between the connecting holes 2c and 2d of the back side mounting portion 2 and between the connecting holes 3c and 3d of the cover bracket in the width direction of the back side mounting portion 2 and the cover bracket 3 (front and rear direction of the seat).
- Holes 2e and 3e are formed, and the worm 50 is disposed in the worm arrangement holes 2e and 3e. Specifically, the worm 50 is disposed so that the axial direction of the worm 50 is along the longitudinal direction of the worm disposition holes 2 e and 3 e, and the worm 50 is disposed so as to mesh with the main drive worm wheel 40.
- the worm 50 is supported at both ends in the axial direction by a pair of bearing portions 510 and 520 disposed at both ends of the worm mounting holes 2e and 3e.
- both sides of the worm 50 disposed in the worm mounting holes 2e and 3e are covered with covers 500 and 501.
- One bearing portion 510 on the front side in the front-rear direction of the seat has a bearing holder 511 formed of a plate-like body disposed at one end (front end) of the worm disposing holes 2e and 3e and an outer surface of the bearing holder 511.
- leaf springs 512 arranged in a stacked manner.
- the bearing holder 511 of one bearing portion 510 is provided with a bearing hole 511a penetrating in the thickness direction at a substantially central portion.
- a shaft portion 50a that protrudes forward is provided at a substantially central portion of one end portion (front end portion) of the worm 50.
- the shaft portion 50a is inserted into the bearing hole 511a, and the tip of the shaft portion 50a is a leaf spring. 512 is brought into contact with 512.
- the other bearing portion 520 on the rear side in the front-rear direction of the seat includes a bearing holder 521 made of a plate-like body disposed at the rear end portions of the worm mounting holes 2e and 3e and a ball 522.
- a holder-side bearing groove 521a is formed at a substantially central portion of the bearing holder 521 of the other bearing portion 520
- a worm-side bearing groove 50b is formed at a substantially central portion of the other end surface (rear end surface) of the worm 50.
- the ball 522 is loaded between the holder side bearing groove 521a and the worm side bearing groove 50b.
- the worm 50 Since the worm 50 is supported in this manner, at the time of rotation in which the back frame 200 is tilted with respect to the cushion frame (cushion side bracket 1), the worm 50 is provided at a substantially central portion supported by the bearing hole 511a of one bearing portion 510.
- the positioned shaft 50a serves as a fulcrum (rotation fulcrum) on one end (front end) side, and the worm side bearing groove 50b in contact with the ball 522 supported by the other bearing 520 is on the other end (rear end) side. (See FIGS. 5A and 6).
- an eccentric position that is, a groove 50c is formed in a circumferential shape around the outer periphery of the shaft 50a projecting substantially at the center.
- a convex portion 511b is formed so as to protrude toward the groove portion 50c of the worm 50 at an eccentric position closer to the outer side than the bearing hole 511a formed in the substantially central portion.
- the worm 50 is displaced in the axial direction when a driven worm wheel 60 (to be described later) comes close to a direction substantially orthogonal to the axial direction and the tooth surfaces come into contact with each other.
- the worm 50 is set to be displaced forward in the axial direction. For this reason, when the worm 50 is displaced forward in the axial direction at the time of locking, the shaft portion 50a presses and deflects the leaf spring 512, and the convex portion 511b engages with the groove portion 50c of the worm 50. 6 is displaced from the broken line state in FIG. 6 to the state indicated by the solid line in FIG. 6, and at one end of the worm 50, the groove part 50c is supported by the convex part 511b and is a fulcrum (locking fulcrum). (See FIG. 5B).
- the other end portion (rear end portion) of the worm 50 maintains a fulcrum that is in contact with the ball 522 supported by the other bearing portion 520 even when the worm side bearing groove 50b, which is a fulcrum at the time of rotation, is locked.
- the worm 50 is supported by the pair of bearing portions 510 and 520 between the fulcrums during rotation along the center line A as shown in FIG.
- the worm 50 is supported along the locking axis B connecting the locking fulcrum on one end and the rotating fulcrum on the other end. Therefore (the state of the solid line in FIG. 6), the advance angle of meshing between the worm 50 and each of the worm wheels 40, 60 is smaller when locked than when rotating. Therefore, even if a rotational force is input from the driven worm wheel 60, the worm 50 is difficult to rotate as compared with the prior art.
- Shaft insertion holes 2f and 3f through which the eccentric shaft 6 is inserted are formed above the worm mounting holes 2e and 3e of the back side mounting portion 2 and the cover bracket 3 (see FIG. 3).
- a driven worm wheel 60 which is a movable gear, is disposed between the back side mounting portion 2 and the cover bracket 3 so as to mesh with the worm 50.
- the driven worm wheel 60 has a shaft insertion hole 2f. , 3f is disposed so that the eccentric shaft 6 inserted into the center of rotation is the center of rotation. That is, as shown in FIGS. 7 to 9, the driven-side worm wheel 60 is attached to the large-diameter portion 6e having a circular cross-sectional shape in the eccentric shaft 6.
- the center 6a of the eccentric shaft 6 is eccentric with respect to the center 60a of the driven side worm wheel 60, and the driven side worm wheel 60 rotates about this eccentric position (center 6a of the eccentric shaft 6).
- the force in the substantially normal direction is canceled, and thereby the whirling vibration of the worm 50 .
- the rotational motion of the worm 50 is stabilized, and the rotational motion of the driven worm wheel 60 itself that meshes with the worm 50 is also stabilized, thereby smoothing these rotational operations.
- the driven worm wheel 60 preferably has a larger mass than the worm 50 in order to allow the driven worm wheel 60 to fully function on the worm 50.
- the reclining adjuster 10 is provided on both sides of the back frame 200 and the cushion frame (cushion side bracket 1), but the lever 7 as an operation member is a cover on one side of the eccentric shaft 6. It connects with the site
- the back side mounting portion 2 and the cover bracket 3 are formed with insertion holes 2h, 3h of the rotary shaft 9 at positions below the worm mounting holes 2e, 3e, corresponding to the insertion holes 2h, 3h of the cushion side bracket 1. Similarly, an insertion hole 1h of the rotary shaft 9 is formed through the position. Accordingly, when the seat back (back frame 200) is tilted, the back side mounting portion 2 and the cover bracket 3 rotate back and forth with respect to the cushion side bracket 1 around the rotation shaft 9.
- Reference numeral 91 denotes a spiral spring that urges the seat back forward.
- the worm 50 is moved back and forth together with the back side mounting portion 2 and the cover bracket 3.
- the worm 50 meshes with the main drive side worm wheel 40
- the worm 50 moves back and forth together with the worm 50 around its axis. Rotate.
- the worm 50 moves like a planetary gear with respect to the main drive side worm wheel 40.
- the driven worm wheel 60 is rotated around the eccentric shaft 6 by the rotation of the worm 50, and the seat back can be tilted by these movements.
- the worm 50 when rotating, the worm 50 is supported and rotated between the fulcrums along the center line A by the pair of bearing portions 510 and 520 as described above (see FIG. 5A). . Since the worm 50 is rotated by the rotational force of the main driving worm wheel 40, the worm 50 is set so that its advance angle is larger than the friction angle of the main driving worm wheel 40 in this posture.
- the lever 7 When locking from the unlocked state, the lever 7 is rotated by the elastic force of the return spring 8 when the lever that has been operating the lever 7 is released. Then, the eccentric shaft 6 connected to the lever 7 rotates in the opposite direction. Since the rotation center 6a of the eccentric shaft 6 is eccentric from the center 60a of the driven worm wheel 60, the driven worm wheel 60 is rotated and pressed toward the worm 50. Thereby, since the clearance gap between both teeth becomes small and the contact area between teeth increases, the worm 50 is displaced forward in the axial direction, and the three gears 40, 50, 60 cannot rotate with respect to each other, Locked in that position, the seat back is adjusted to the desired angle.
- the worm 50 is less likely to rotate even if a rotational force is input from the driven worm wheel 60, and the locking reliability is improved, compared to a structure in which the fulcrum does not change between rotation and locking. Will increase.
- the lock strength against the load applied to the seat back is increased, and the effect of suppressing the tilting of the seat back gradually in the locked state is high.
- the advance angle of meshing between the worm 50 and each worm wheel 40, 60 is reduced. That is, as shown in FIG. 5C, the advance angle when a large load is input is smaller than when the fulcrum does not change.
- the lateral force applied to the driven worm wheel 60 is reduced, so that the engagement with the worm 50 is easily maintained, and the impact of the passenger is reduced. This also contributes to improving the ability to get out of the vehicle.
- FIG. 11 is a view showing a test result of a rear moment intensity measured by applying a rear frame strength to a seat frame (test example) to which the reclining adjuster 10 of the above embodiment is attached.
- the rear moment intensity is about 2900 Nm, which is very high and is displaced substantially linearly.
- the worm 50 of the reclining adjuster 10 and the worm wheels 40, 60 are separated from each other. It can be seen that the teeth are deeply engaged and integrated with the back frame to receive strength. Accordingly, in a collision or the like, the deformation of the back frame proceeds earlier than the reclining adjuster 10, so that energy absorption due to the deformation of the back frame can function smoothly.
- the reclining adjuster 10 has high strength and is easy to maintain the engagement of the worm 50 in the first place.
- the fulcrum supporting the worm 50 is different between the locked state and the unlocked state. Even if the fulcrum is not damaged, even if the fulcrum at the time of locking is damaged, the seat back can be tilted by releasing the lock, so that the seat back can be tilted. High contribution.
- the reclining adjuster 10 was operated. The reclining operation was possible with full stroke.
- FIG 11 shows the rear moment intensity measured under the same conditions as in the test example for the seat frame (comparative example) to which a conventional internal tooth type recliner is attached.
- the recliner is the seat frame. It was found that the seat frame was deformed earlier, the seat frame was deformed thereafter, and the backward moment strength was a low value, and the structure of the test example was superior in terms of the backward moment strength.
- FIGS. 12 to 15 are views showing a reclining adjuster 10A which is a rotational motion control mechanism according to another embodiment of the present invention.
- the main driving side worm wheel 40A is provided on the side of the back side bracket 211 connected to the back frame as the second member, and the driven side worm wheel 60A and the worm 50A are the first members. It is the structure provided in the cushion side bracket 111 which is the cushion frame side.
- the back side bracket 211 is formed using a steel material suitable for gear production, and the main drive side worm wheel 40A is integrally formed on the back side bracket 211 so that the teeth thereof face downward.
- the rotating shaft 9 is inserted into the back side bracket 211, the rotating shaft 9 is fixed to the cushion side bracket 111, and the back frame including the back side bracket 211 tilts back and forth around the rotating shaft 9. .
- a spiral spring 91 that is a balance spring is engaged between the center of the rotary shaft 9 and an engagement pin 211 a provided on the back bracket 211.
- the cushion side bracket 111 is provided with a rotatable driven worm wheel 60A, and a worm 50A is rotatably provided above the driven side worm wheel 60A.
- An operating member (not shown) such as a lever is connected to the eccentric shaft 6A that supports the driven worm wheel 60A via a return spring 70A. Therefore, the eccentric shaft 6A functions as a transmission shaft that transmits the force of the operation member (this is the same as in the above embodiment).
- the back side bracket 211 is disposed between the cushion side bracket 111 and the cover bracket 311, and worm disposition holes 111 e and 311 e are formed in the cushion side bracket 111 and the cover bracket 311, respectively.
- the worm 50 ⁇ / b> A is disposed in the worm mounting holes 111 e and 311 e.
- the worm 50A is arranged so that the axial direction of the worm 50A is along the longitudinal direction of the worm disposing holes 111e and 311e, and the worm 50A can be engaged with the main driving worm wheel 40A and the driven worm wheel 60A. Be placed.
- Covers 500A and 501A are disposed on the outer surface sides of the cushion side bracket 111 and the cover bracket 311 to cover the side surfaces of the worm 50A facing outward from the worm mounting holes 111e and 311e.
- the driving side worm wheel 40A is provided on the back side bracket 211, and both the worm 50A and the driven side worm wheel 60A are provided on the cushion side bracket 111.
- the wheel 40A together with the back bracket 211, rotates back and forth on the upper side of the worm 50A.
- the main drive worm wheel 40A rotates in this manner, the worm 50A meshed with the main drive worm wheel 40A rotates, and the driven worm wheel 60A meshed with the worm 50A rotates around the eccentric shaft 6A.
- the main drive side worm wheel 40A for rotating the worm 50A is arranged on the upper side of the worm 50A, and the force for rotating the worm 50A by the main drive side worm wheel 40A acts in the gravity direction of the worm 50A. It is. That is, since the backlash between the driving side worm wheel 40A and the worm 50A always tends to spread due to the gravity of the worm 50A, the design friction angle required to rotate the worm 50A by the rotation of the driving side worm wheel 40A. Can be made smaller than the type described in the above embodiment in which the main drive worm wheel 40 is disposed below the worm 50.
- both end portions in the axial direction of the worm 50 are provided by the pair of bearing portions 510 and 520 disposed at both end portions of the worm disposing holes 2 e and 3 e.
- the worm 50A is supported by the pair of bearing portions 510A and 520A, and the other bearing portion 520A on the rear side of the seat has a holder-side bearing groove 521A1.
- the same is true for the bearing holder 521A and the ball 522A loaded between the holder-side bearing groove 521A1 and the worm-side bearing groove 50A2 of the worm 50A, but one bearing arranged on the front side of the seat.
- the support structure of the portion 510A is different.
- one bearing portion 510A is configured to include a bearing holder 511A and a rotation control cam 512A, and includes the leaf spring 512 shown in FIGS. 5 and 6 used in the above embodiment. Not done.
- the bearing holder 511A is provided with a bearing hole 511A1 penetrating in the thickness direction at a substantially central portion, and a shaft portion 50A1 provided to protrude forward at a substantially central portion of one end portion (front end portion) of the worm 50A. Is inserted into the bearing hole 511A1, and the tip of the shaft portion 50A1 protrudes outward from the bearing hole 511A.
- the rotation control cam 512A is composed of a plate-like member rotatably supported by a support shaft 513 supported between the cushion side bracket 111 and the cover bracket 311 in front of the seat of the shaft portion 50A1 of the worm 50A.
- the rotation control cam 512A has a recess 512A1 formed on the rear peripheral surface located on the rear side of the seat, and protrudes relatively rearwardly adjacent to the lower side of the recess 512A1.
- a convex portion 512A2 is formed.
- a cam shaft portion 512A3 protrudes from the lower end portion of the rotation control cam 512A.
- the cover bracket 311 is formed with a long hole 311f that is opened so that the rear side is upward, and the cam shaft portion 512A3 protrudes outward from the long hole 311f.
- One end of the link plate 71A is connected to the protruding portion of the cam shaft portion 512A3.
- a link shaft 71B is connected to the other end of the link plate 71A.
- the link shaft 71B is connected to a lever bracket 71C connected to the eccentric shaft 6A.
- the lever bracket 71C is supported around the eccentric shaft 6A, one end is engaged with the engagement hole 71C1 of the lever bracket 71C, and the other end is a protruding piece 501A1 of one cover 501A that covers the side surface of the worm 50A. It is urged by a return spring 70A engaged with.
- the rotational center of the eccentric shaft 6A is eccentric from the center of the driven worm wheel 60A, so that the driven worm wheel 60A is rotated in the direction of the worm 50A.
- the worm 50A is displaced forward in the axial direction, and the worm 50A is supported by the convex portion 511A2 and the ball 522A provided at the eccentric position of the bearing holder 511A along the axis B when locked (FIG. 15). (See (b)).
- the shaft portion 50A1 of the worm 50A is not in contact with anything. In the case of the embodiment shown in FIGS.
- the shaft portion 50a of the worm 50 is in contact with the leaf spring 512 even during the locking (see FIGS. 5 and 6). Therefore, when a load is repeatedly applied to the seat back, depending on the magnitude of the load, the worm 50 may rotate and the seat back may tilt.
- the tip of the shaft portion 50A1 of the worm 50A is not in contact with the rotation control cam 512A at all, the rotation of the worm 50A when a large load is applied at the time of such locking is described above. It is suppressed more than the embodiment.
- a clutch plate 150 having a surface (opposing surface) 151 facing the surface of the driven worm wheel 60A is further provided.
- the clutch plate 150 is disposed on the cushion side bracket 111 with the opposed surface 151 facing inward and the eccentric shaft 6A fixed to the center hole 151c by welding or the like.
- Grooves 151a are formed at three locations on the facing surface 151 at a predetermined interval in the circumferential direction, and each groove 151a has an inclined surface 151b near each end in the circumferential direction.
- balls 152 are supported by three holes 111a formed corresponding to the respective grooves 151a.
- the ball 152 protrudes into the groove 151a and is provided so as to be able to contact the inclined surface 151b, and a part of the ball 152 is provided so as to protrude from the hole 111a toward the driven worm wheel 60A.
- the ball 152 constitutes a pressing member when locked
- the cushion side bracket 111 constitutes a member that supports the pressing member when locked.
- the clutch plate 150 rotates in one direction along with the rotation of the eccentric shaft 6A.
- the ball 152 is placed on a flat portion other than the inclined surface 151b in the groove portion 151a. Are held correspondingly. Therefore, the ball 152 does not press the surface of the driven worm wheel 60A, and the rotation of the driven worm wheel 60A is not hindered.
- the clutch plate 150 rotates by a predetermined angle by the rotation of the eccentric shaft 6A, and the inclined surface 151b becomes a position corresponding to the ball 152 as shown in FIG. Since the ball 152 is pressed by the inclined surface 151b, the ball 152 protrudes from the hole 111a and is pressed against the surface of the driven worm wheel 60A. As a result, the force for holding the driven worm wheel 60A so as not to rotate at the time of locking is further increased.
- the mechanism that strongly acts to prevent the rotation of the worm 50A and the driven worm wheel 60A during locking by the means for pressing the worm 50A support and the surface of the driven worm wheel 60A. is there. Therefore, the effect of suppressing the inclination of the seat back due to the input of a repeated load forward or backward to the seat back at the time of locking is high.
- the description is based on the assumption that the manual type provided with the operation member (lever 7 or the like) is provided, but the present invention is naturally applicable to an electric type.
- the rotational motion control mechanism of the present invention is typically used as a seat relining adjuster.
- a power unit is further used as a rotational motion portion of a front / rear lifter or a parallel lifter. It can also be used as a substitute for a motor locking mechanism.
- the present invention can be applied not only to a vehicle seat such as an automobile but also to a train, an aircraft seat, and the like.
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Abstract
Description
前記ウォームの軸方向一端部に設けられる回転時支点の周囲に円周状に形成された溝部を有し、軸方向一端部側に配置される前記一方の軸受け部の偏心位置に、前記溝部方向に突出する凸部が形成され、前記ロック時支点は、前記凸部が当接する前記溝部のいずれかの部位となる構成であることが好ましい。
前記ウォームの軸方向一端部側に配置される前記一方の軸受け部は、前記回転時支点を弾性的に支持する弾性部を有し、ロック時に前記ウォームが軸方向に変位することにより、前記弾性部が軸方向に撓み、それにより、前記ウォームの軸方向一端部における前記一方の軸受け部による支持位置が、前記回転時支点から前記ロック時支点に変化する構成であることが好ましい。
ロック時において、前記従動側ウォームホイールの面を押圧するロック時押圧部材を有する構成とすることが好ましい。
前記従動側ウォームホイールの少なくとも一方の面に対向する面に形成される傾斜面を有するクラッチプレートを備え、前記従動側ウォームホイールと前記クラッチプレートとの間に配設された部材に前記ロック時押圧部材を支持させ、ロック時に、前記クラッチプレートが回転すると、前記傾斜面により前記ロック時押圧部材が前記従動側ウォームホイールの対向する面に圧接される構成とすることが好ましい。
前記従動側ウォームホイールは、その中心位置から偏心した位置を回転中心とする偏心シャフトを介して回転可能に支持され、前記偏心シャフトを回転させると、前記従動側ウォームホイールが前記ウォームに押し付けられ、それにより両者間のバックラッシュが減少し、回転力の伝達を制限する構成であることが好ましい。
前記従動側ウォームホイールは、前記ウォームよりも質量が大きく、前記従動側ウォームホイールの質量に対応した力が前記ウォームに作用し、前記ウォームのふれまわり振動を抑制する構成であることが好ましい。
前記第1部材が、シートクッションのフレームを構成するいずれかの部材であり、前記第2部材が、シートバックのフレームを構成するいずれかの部材であり、前記シートクッションに対する前記シートバックの傾斜角を調節するリクライニングアジャスタとして用いられることが好ましい。
前記回転動作制御機構が、前記シートクッションのフレームを構成するいずれかの部材と、前記シートバックのフレームを構成するいずれかの部材との間にリクライニングアジャスタとして設けられていることが好ましい。
2 バック側取り付け部
211 バック側ブラケット
3,311 カバーブラケット
6,6A 偏心シャフト
9 回転軸
10,10A リクライニングアジャスタ
40,40A 主動側ウォームホイール
50,50A ウォーム
50a,50A1 軸部(回転時支点)
50b,50A2 ウォーム側軸受け溝(回転時支点)
50c 溝部(ロック時支点)
510,520,510A,520A 軸受け部
511,521,511A,521A 軸受けホルダー
511a,511A1 軸受け孔
511b,511A2 凸部
512A 回転制御カム
521a,521A1 ホルダー側軸受け溝
522,522A ボール
60,60A 従動側ウォームホイール
150 クラッチプレート
151a 溝部
151b 傾斜面
152 ボール
Claims (13)
- 第1部材に対して第2部材を回転可能に制御すると共に、適宜の回転角で保持可能な回転動作制御機構であって、
前記第1及び第2部材のうちのいずれかに、軸方向両端部に配置された一対の軸受け部間に軸支されるウォームと、
前記ウォームを挟んだ位置関係で前記ウォームに噛み合うように、前記第1及び第2部材のうちのいずれか一方に設けられる主動側ウォームホイール及び他方に設けられる従動側ウォームホイールと
を有し、
第1部材及び第2部材を相対的に回転させると、前記主動側ウォームホイールに噛み合う前記ウォームが回転すると共に、前記ウォームに噛み合う従動側ウォームホイールも回転し、
ロック時には、前記従動側ウォームホイールを、前記ウォームに押し付ける方向に動作させて、両者間のバックラッシュを減少させた状態でロック可能であり、
かつ、
軸方向両端部に設けられ、前記ウォームが回転する際の支点となる回転時支点と、軸方向一端部において前記回転時支点と異なる位置に設けられたロック時支点とを有し、
回転時は、前記一対の軸受け部により、前記軸方向両端部の各回転時支点が支持され、
ロック時は、前記従動側ウォームホイールが前記ウォームに押し付けられる方向への動作に伴って前記ウォームが軸方向に変位することにより、軸方向一端部では前記ロック時支点が、軸方向他端部では前記回転時支点が前記一対の軸受け部によりそれぞれ支持され、
ロック時の前記ウォームの進み角が回転時の進み角よりも小さくなるように変化する構造であることを特徴とする回転動作制御機構。 - 前記ウォームの前記各回転時支点は軸方向両端部の中心位置にそれぞれ設けられ、前記ロック時支点が軸方向一端部において偏心位置に設けられている請求項1記載の回転動作制御機構。
- 前記ウォームの軸方向一端部に設けられる回転時支点の周囲に円周状に形成された溝部を有し、
軸方向一端部側に配置される前記一方の軸受け部の偏心位置に、前記溝部方向に突出する凸部が形成され、
前記ロック時支点は、前記凸部が当接する前記溝部のいずれかの部位となる請求項1又は2記載の回転動作制御機構。 - 前記ウォームの軸方向一端部側に配置される前記一方の軸受け部は、前記回転時支点を弾性的に支持する弾性部を有し、ロック時に前記ウォームが軸方向に変位することにより、前記弾性部が軸方向に撓み、それにより、前記ウォームの軸方向一端部における前記一方の軸受け部による支持位置が、前記回転時支点から前記ロック時支点に変化する請求項1~3のいずれか1に記載の回転動作制御機構。
- 前記ウォームの軸方向一端部側に配置される前記一方の軸受け部は、前記回転時支点の先端部が、外方に突出可能な貫通孔を有する軸受けホルダーと、前記貫通孔から突出している前記回転時支点の先端部に、前記ウオームの回転時に接触し、ロック時に離間する形状に形成された回転制御カムを有する請求項1~3のいずれか1に記載の回転動作制御機構。
- ロック時において、前記従動側ウォームホイールの面を押圧するロック時押圧部材を有する請求項1~5のいずれか1に記載の回転動作制御機構。
- 前記従動側ウォームホイールの少なくとも一方の面に対向する面に形成される傾斜面を有するクラッチプレートを備え、前記従動側ウォームホイールと前記クラッチプレートとの間に配設された部材に前記ロック時押圧部材を支持させ、ロック時に、前記クラッチプレートが回転すると、前記傾斜面により前記ロック時押圧部材が前記従動側ウォームホイールの対向する面に圧接される請求項6記載の回転動作制御機構。
- 前記従動側ウォームホイールは、その中心位置から偏心した位置を回転中心とする偏心シャフトを介して回転可能に支持され、
前記偏心シャフトを回転させると、前記従動側ウォームホイールが前記ウォームに押し付けられ、それにより両者間のバックラッシュが減少し、回転力の伝達を制限する構成である請求項1~7のいずれか1に記載の回転動作制御機構。 - 前記従動側ウォームホイールは、前記ウォームよりも質量が大きく、前記従動側ウォームホイールの質量に対応した力が前記ウォームに作用し、前記ウォームのふれまわり振動を抑制する構成である請求項1~8のいずれか1に記載の回転動作制御機構。
- 前記第1部材及び第2部材が、シートを構成する複数の部材の中で、相対的に回転する2つの部材であり、シート用として用いられる請求項1~9のいずれか1に記載の回転動作制御機構。
- 前記第1部材が、シートクッションのフレームを構成するいずれかの部材であり、前記第2部材が、シートバックのフレームを構成するいずれかの部材であり、前記シートクッションに対する前記シートバックの傾斜角を調節するリクライニングアジャスタとして用いられる請求項10記載の回転動作制御機構。
- シートクッションとシートバックとを備えたシートにおいて、
請求項1~11のいずれか1に記載の回転動作制御機構が、前記シートを構成する複数の部材の中で、相対的に回転する2つの部材間に設けられていることを特徴とするシート。 - 前記回転動作制御機構が、前記シートクッションのフレームを構成するいずれかの部材と、前記シートバックのフレームを構成するいずれかの部材との間にリクライニングアジャスタとして設けられている請求項12記載のシート。
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US15/519,427 US10179523B2 (en) | 2014-10-16 | 2015-10-15 | Rotation movement control mechanism and seat |
JP2016554149A JP6588025B2 (ja) | 2014-10-16 | 2015-10-16 | 回転動作制御機構及びシート |
EP15851448.9A EP3208141B1 (en) | 2014-10-16 | 2015-10-16 | Rotating operation control mechanism and seat |
CN201580055907.0A CN107074130B (zh) | 2014-10-16 | 2015-10-16 | 旋转动作控制机构以及座椅 |
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US6764136B2 (en) * | 2002-02-26 | 2004-07-20 | Delta Tooling Co., Ltd. | Reclining adjuster |
JP4245366B2 (ja) | 2002-02-26 | 2009-03-25 | 株式会社デルタツーリング | リクライニングアジャスタ |
DE10248308A1 (de) * | 2002-10-16 | 2004-04-29 | Suspa Holding Gmbh | Sitzträger für einen Stuhl, insbesondere für eine Bürostuhl |
JP4528041B2 (ja) * | 2004-07-07 | 2010-08-18 | 株式会社デルタツーリング | リクライニングアジャスタ |
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JP5347635B2 (ja) * | 2009-03-27 | 2013-11-20 | アイシン精機株式会社 | シート調整装置及びそのシート調整装置を備えた車両用シート装置 |
US9989121B2 (en) | 2013-07-04 | 2018-06-05 | Delta Tooling Co., Ltd. | Rotating movement control mechanism and seat |
JP6330469B2 (ja) * | 2014-05-13 | 2018-05-30 | アイシン精機株式会社 | シート駆動装置 |
US10058178B2 (en) * | 2017-01-30 | 2018-08-28 | Shiroki Corporation | Reclining device |
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2015
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JPS61101493U (ja) * | 1984-12-05 | 1986-06-28 | ||
WO2007043628A1 (ja) * | 2005-10-12 | 2007-04-19 | Delta Tooling Co., Ltd. | リクライニングアジャスタ |
WO2007043233A1 (ja) * | 2005-10-12 | 2007-04-19 | Delta Tooling Co., Ltd. | リクライニングアジャスタ |
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JP6588025B2 (ja) | 2019-10-09 |
CN107074130A (zh) | 2017-08-18 |
EP3208141A1 (en) | 2017-08-23 |
EP3208141A4 (en) | 2018-05-23 |
CN107074130B (zh) | 2019-07-05 |
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