Source: https://patents.google.com/patent/JP5924987B2/en
Timestamp: 2020-02-19 03:52:23
Document Index: 401602527

Matched Legal Cases: ['art 8', 'art 96', 'art 96', 'art 96', 'art 120', 'art 118', 'art 215', 'art 183', 'art 183', 'art 189', 'art 212', 'art 212', 'art 212', 'art 212', 'art 212']

JP5924987B2 - Seat belt retractor - Google Patents
JP5924987B2
JP5924987B2 JP2012050616A JP2012050616A JP5924987B2 JP 5924987 B2 JP5924987 B2 JP 5924987B2 JP 2012050616 A JP2012050616 A JP 2012050616A JP 2012050616 A JP2012050616 A JP 2012050616A JP 5924987 B2 JP5924987 B2 JP 5924987B2
JP2012050616A
JP2013184540A (en
絵里 山根
仁洙 崔
2012-03-07 Application filed by 芦森工業株式会社 filed Critical 芦森工業株式会社
2012-03-07 Priority to JP2012050616A priority Critical patent/JP5924987B2/en
2013-09-19 Publication of JP2013184540A publication Critical patent/JP2013184540A/en
2016-05-25 Publication of JP5924987B2 publication Critical patent/JP5924987B2/en
The present invention relates to a seatbelt retractor for preventing webbing from being pulled out in an emergency.
Conventionally, various seat belt retractors for preventing webbing from being pulled out in an emergency have been proposed.
For example, a shaft 129 protrudes from the lower end of the main body 130 of the sensor gear 128 at the end opposite to the V gear 126 of the pressing portion 168 that protrudes toward the V gear 126 side. Further, an engaging claw 140 as a connecting member is pivotally supported on the shaft 129 so as to be rotatable. Further, an acceleration sensor 142 is provided below the engagement claw 140, and when the acceleration of a predetermined value or more acts on the vehicle, the sensor claw 150 of the acceleration sensor 142 is pushed up by the hard ball 148, thereby engaging. The claw 140 is rotated upward.
Further, a V gear 126 having ratchet teeth formed on the outer peripheral portion is located on the rotation direction side of the engagement claw 142 rotated upward by the sensor claw 150. Engage with the V gear 126. When the engaging claw 142 engages with the V gear 126, the rotational force of the V gear 126 in the webbing pull-out direction is transmitted to the sensor gear 128, and the pressing portion 168 rotates the lock pawl 160. When the lock pawl 160 is rotated, there is a webbing take-up device configured such that the pawl portion 166 engages with the ratchet portion 172 of the lock base 170 and the spool 24 is prevented from rotating in the webbing pull-out direction ( For example, see Patent Document 1.)
JP 2006-188148 A
However, in the webbing take-up device described in Patent Document 1 described above, after the engaging claw 140 is engaged with the V gear 126, the pawl portion 166 of the lock pawl 160 and the ratchet portion 172 of the lock base 170 are engaged. When a delay occurs in the timing due to a synchronization shift or the like, the engagement claw 140 engaged with the V gear 126 is greatly increased in the shaft 129 direction by relative rotation of the V gear 126 in the webbing pull-out direction with respect to the sensor gear 128. Impact load acts.
For this reason, at least one of the engaging claw 140 and the V gear 126 may be damaged, the lock mechanism may not function, and the spool 24 may not be prevented from rotating in the webbing pull-out direction. Further, in order to improve the sensitivity of the acceleration sensor 142, it is necessary to reduce the size of the engaging claw 140 to reduce its mass. However, the engaging claw 140 needs to withstand the pressing load received from the V gear 126. There is a problem that it is difficult to reduce the size.
Accordingly, the present invention has been made to solve the above-described problems, and is capable of suppressing damage to the pilot lever and the locking gear and reducing the size of the pilot lever. The purpose is to provide.
To achieve the above object, a seatbelt retractor according to claim 1 includes a housing, a winding drum that is rotatably housed in the housing and winds and stores the webbing, and a ratchet that rotates integrally with the winding drum. A gear, a lock mechanism that prevents the winding drum from rotating in the webbing pull-out direction in an emergency, an inertial mass body that swings in response to an acceleration greater than a predetermined value of the vehicle, and the inertial mass body that is pushed. And a sensor lever that swings upward in the vertical direction to activate the lock mechanism, and the lock mechanism is arranged coaxially with the winding drum and is capable of relative rotation. A clutch that guides a pawl that engages with a gear to prevent the winding drum from rotating in the webbing pull-out direction, and is pivotally supported by a mounting boss that is erected on the clutch. A pilot lever that is rotated by being pressed by the oscillating sensor lever, and a locking gear that is integrally and coaxially attached to the winding drum and that is engaged with the pilot lever by rotation. The pilot lever includes a cylindrical shaft portion into which the mounting boss is rotatably fitted, and an outward projection from the outer peripheral surface of the shaft portion so as to face the locking gear. has a engaging claw portion engaged with the gear, and frettage after the engagement claw portion during rapid engages the locking gear teeth formed on the outer periphery of the locking gear, the said pawl ratchet gear When the engagement timing is delayed and the engagement claw is pressed against the locking gear teeth, the engagement claw is elastically deformed toward the shaft portion and the engagement claw and the locking claw. Engagement with gear teeth It is it is possible, if the engagement between the engaging claws and the locking gear teeth off is characterized in that the elastic deformation of the engaging claw portion is eliminated.
Further, the seatbelt retractor according to claim 2 is the seatbelt retractor according to claim 1 , wherein the engagement claw portion has a distal end portion bent obliquely toward the locking gear. When the engaging claw portion is pressed by the locking gear teeth, the tip end portion of the engaging claw portion is elastically deformed toward the shaft portion side at an obliquely bent portion. It is characterized by that.
Further, the seatbelt retractor according to claim 3 is the seatbelt retractor according to claim 1 , wherein the engaging claw portion has an end surface portion facing the locking gear and the shaft-side base end portion. When the engaging claw is pressed against the locking gear teeth, it is formed so as to be gradually lowered over the entire width in the rotational axis direction from both end portions to the substantially central portion. The engaging claw portion is elastically deformed toward the shaft portion side at the substantially central portion.
The seatbelt retractor according to claim 4 is the seatbelt retractor according to any one of claims 1 to 3 , wherein the clutch is rotated by being pressed by the sensor lever. Has an opening provided so as to be engageable with the locking gear teeth, and the opening when the engaging claw is pressed by the locking gear teeth and elastically deforms toward the shaft side. A predetermined gap is formed between the edge portion on the shaft side and the engaging claw portion.
A seatbelt retractor according to a fifth aspect is the seatbelt retractor according to any one of the first to fourth aspects, wherein the pilot lever is provided substantially parallel to the engagement claw portion. And a thin plate-like contact portion that is pressed against the swung sensor lever, and a thin plate-like connection plate portion that connects both ends of the contact portion and the engaging claw portion. And the contact portion is provided so as to be elastically deformable toward the shaft portion side together with the engagement claw portion.
The seatbelt retractor according to claim 6 is the seatbelt retractor according to any one of claims 1 to 5 , wherein the clutch is engaged with the shaft portion fitted into the mounting boss. A pilot lever support portion projecting from the outer peripheral surface of the opposite side in the radial direction with respect to the joint claw portion so as to be opposed to the outer peripheral surface of the shaft portion; It has an upward detent portion that is erected outward in the radial direction so as to face the lever support portion with a predetermined gap in the rotational direction, and the engaging claw portion is an outer periphery of the locking gear in an emergency. When the pilot lever is engaged with the locking gear teeth formed on the portion, the upper detent portion contacts the one end surface in the circumferential direction of the pilot lever support portion and rotates upward in the vertical direction. In a state where the regulation has been, and wherein the rotating the clutch in accordance with rotation of the locking gear.
The seat belt retractor according to claim 7 is the seat belt retractor according to claim 6 , wherein the engaging claw portion engages with a locking gear tooth formed on an outer peripheral portion of the locking gear in an emergency. When the mounting boss is bent, the clutch is rotated according to the rotation of the locking gear while the outer peripheral surface of the shaft portion is in contact with the pilot lever support portion. To do.
The seatbelt retractor according to claim 8 is the seatbelt retractor according to claim 6 or 7 , wherein the pilot lever rotates the pilot lever support portion together with the upward detent portion. The pilot lever has a downward detent that is erected radially outward from the outer peripheral surface of the shaft so as to form a predetermined gap therebetween, and the pilot claw is rotated by its own weight. In this case, the downward rotation prevention portion is in contact with the other circumferential end surface of the pilot lever support portion, and is restricted from rotating downward in the vertical direction.
Further, the seatbelt retractor according to claim 9 is the seatbelt retractor according to any one of claims 1 to 8 , wherein the clutch is disposed between the shaft portion fitted into the mounting boss. A predetermined gap is formed on the shaft portion so as to be elastically deformable radially outward with respect to the shaft portion, and an elastic locking piece having a locking projection protruding toward the shaft portion side is formed at the tip portion. The pilot lever has a convex portion that protrudes radially outward from an outer peripheral surface of the shaft portion that is fitted into the mounting boss and faces the elastic locking piece, and the pilot lever includes the shaft portion. Is inserted into the mounting boss so that the convex portion can be brought into contact with the locking projection from the base end side of the elastic locking piece and can be rotatably mounted on the mounting boss. Features.
In the seatbelt retractor according to the first aspect, the engaging claw portion of the pilot lever protrudes outward from the outer peripheral surface of the cylindrical shaft portion so as to face the locking gear and engages with the locking gear. . In addition, after the engaging claw portion engages with the locking gear teeth formed on the outer peripheral portion of the locking gear, there is a delay in the timing of engagement between the pawl and the ratchet gear. If it pressed, the engaging claw portion is possible is disengaged with the engaging claws and the locking gear teeth elastically deformed in the axial portion. Further, when the engagement claw portion and the locking gear teeth are disengaged, the elastic deformation of the engagement claw portion is eliminated.
As a result, after the engaging claw of the pilot lever is engaged with the locking gear teeth formed on the outer periphery of the locking gear in an emergency, the timing at which the pawl and the ratchet gear are engaged is delayed due to a synchronization shift or the like. when the can, the engaging claw portion elastically deformed to the shaft-side, since out of the engaged locking gear teeth, Ru can suppress damage to the pilot lever and locking gear.
Also, the pilot lever is engaged in the event of a delay in the engagement timing of the pawl and the ratchet gear after the engaging claw portion is engaged with the locking gear teeth formed on the outer periphery of the locking gear in an emergency. Even if the locking gear teeth are disengaged, the engaging claw portion elastically returns to its original shape. Therefore, when it is pressed again by the sensor lever and then rotated upward in the vertical direction, it can be engaged with the opposing locking gear teeth, thus reliably preventing the winding drum from rotating in the webbing pull-out direction. It becomes possible to do.
In an emergency, when the engaging claw engages with the locking gear teeth formed on the outer peripheral portion of the locking gear and the timing at which the pawl and the ratchet gear engage is delayed, the engaging claw is Since it is elastically deformed to the shaft side and is disengaged from the engaged locking gear teeth, the engagement claw can be further reduced in size and thickness, and the pilot lever can be further reduced in size. Can be planned.
Further, in the seatbelt retractor according to claim 2 , the engaging claw portion of the pilot lever is formed in a substantially L shape as viewed in the rotational axis direction with the tip portion obliquely bent toward the locking gear side, and the locking gear teeth When the locking gear teeth are pressed after the engagement, the distal end portion of the engagement claw portion is configured to be elastically deformable toward the shaft portion side at the obliquely bent portion.
As a result, when the engaging claw portion is pressed by the locking gear teeth, the pilot claw portion and the locking gear are elastically deformed toward the shaft portion at the portion where the tip end portion of the engaging claw portion is bent obliquely. It is possible to further reduce the impact load on the pilot lever and to effectively prevent the pilot lever and the locking gear from being damaged. In addition, since the engaging claw portion is bent obliquely toward the locking gear side, the engagement claw portion smoothly disengages from the locking gear teeth formed on the outer peripheral portion of the locking gear when greatly deformed elastically toward the shaft portion side. Therefore, the engagement claw portion can be further reduced in size and thickness, and the pilot lever can be further reduced in size.
In the seatbelt retractor according to the third aspect , the engaging claw portion of the pilot lever has an end surface portion facing the locking gear, which is directed from the both end portions of the shaft portion side base end portion and the distal end portion toward the substantially central portion. Thus, it is formed so as to be gradually lowered over the entire width in the rotational axis direction. And, when the engaging claw part is engaged with the locking gear tooth and then pressed against this locking gear tooth, in the substantially central part from the distal end part of the engaging claw part to the shaft part side base end part, It is configured to be elastically deformable toward the shaft portion side.
Thereby, when the engaging claw portion is pressed by the locking gear teeth, it is elastically deformed toward the shaft portion side at the substantially central portion from the distal end portion of the engaging claw portion to the shaft portion side proximal end portion, The impact load on the pilot lever and the locking gear can be further reduced, and damage to the pilot lever and the locking gear can be effectively suppressed. In addition, the engaging claw portion is elastically deformed toward the shaft portion side at a substantially central portion from the distal end portion to the shaft portion side base end portion, and therefore when the engagement claw portion is largely elastically deformed toward the shaft portion side, the rotation claw direction view is omitted. It can be elastically deformed into a U-shape and can be smoothly removed from the locking gear teeth formed on the outer peripheral portion of the locking gear, and the engagement claw portion can be further reduced in size and thickness. The pilot lever can be further downsized.
Further, in the seatbelt retractor according to the fourth aspect of the present invention , the engaging claw that is elastically deformed by being pressed by the locking gear teeth after entering into the opening of the clutch and engaging the locking gear teeth, and the opening A predetermined gap is formed between the end portion on the shaft portion side. Thereby, the interference to the elastic deformation of the engaging claw portion by the clutch can be surely prevented, the elastic deformation of the pilot lever is not hindered, and the damage of the pilot lever and the locking gear can be further suppressed.
In the seatbelt retractor according to the fifth aspect , the both ends of the engaging claw portion of the pilot lever and the thin plate-like contact portion with which the sensor lever contacts are connected by the thin plate-like connecting plate portion. Since the corresponding contact part is provided so as to be elastically deformable toward the shaft part side together with the engaging claw part, further thinning is achieved while maintaining the mechanical strength of the engaging claw part. Weight reduction and size reduction can be achieved.
In the seatbelt retractor according to the sixth aspect , in an emergency, the engaging claw portion is engaged with the locking gear teeth formed on the outer peripheral portion of the locking gear, and is further pressed by the locking gear and further rotated. In this case, in the pilot lever, the upward rotation preventing portion comes into contact with one end surface in the circumferential direction of the pilot lever support portion, and thus the rotation of the pilot lever in the vertical direction is restricted.
Therefore, the pressing load received from the locking gear of the pilot lever is also supported by the pilot lever support portion via the upward detent portion. As a result, the pressure load received from the pilot lever locking gear can be supported not only by the mounting boss but also by the pilot lever support part via the upward detent part. The deformation and breakage of the boss can be further prevented.
In the seatbelt retractor according to the seventh aspect of the present invention, the pilot lever is configured to sandwich the pilot lever support portion with a predetermined clearance in the rotation direction by the upper rotation prevention portion and the lower rotation prevention portion. Thus, the rotation angle of the pilot lever can be regulated with a simple configuration, and the parts shapes of the clutch and the pilot lever can be further simplified.
In the seatbelt retractor according to the eighth aspect , in the event of an emergency, when the engaging claw engages with the locking gear teeth formed on the outer periphery of the locking gear and the mounting boss bends, the pilot lever The pressing load received from the locking gear can be supported by the pilot lever support part via the outer peripheral surface of the shaft part and the upward rotation prevention part, and it can be mounted with a simple configuration even if a large pressing load is applied by the locking gear The deformation and breakage of the boss and the shaft portion can be further prevented. In addition, by increasing the cross-sectional shape of the pilot lever support portion protruding from the clutch, the mechanical strength of the pilot lever support portion can be increased, and the mounting boss and shaft portion can be effectively deformed and damaged. Can be prevented.
Furthermore, in the seatbelt retractor according to the ninth aspect , the pilot lever has a protruding portion projecting from the outer peripheral surface of the shaft portion by inserting the shaft portion into the mounting boss so that the shaft protrudes from the distal end portion of the elastic locking piece. Since it is attached to the locking projection that protrudes from the base side so that it can come into contact with the elastic locking piece from the base end side, and is rotatably mounted on the mounting boss, the pilot lever can be easily detached from the mounting boss. This can be reliably prevented with a simple configuration.
1 is an external perspective view of a seatbelt retractor according to the present embodiment. It is the perspective view which decomposed | disassembled the seatbelt retractor for every unit. It is the perspective view which decomposed | disassembled the seatbelt retractor for every unit. It is a disassembled perspective view of a housing unit. It is a disassembled perspective view of a ratchet gear, a winding spring unit, and a lock unit. It is a disassembled perspective view of a ratchet gear, a winding spring unit, and a lock unit. It is sectional drawing explaining attachment of a spring case. It is sectional drawing explaining the attachment state of a spring case. It is assembly sectional drawing containing the lock arm of a lock unit. It is a partially cutaway sectional view in which a part such as a bottom surface of a mechanism cover of the lock unit is cut away. It is a principal part expanded sectional view containing the winding spring unit and lock unit of the retractor for seatbelts. It is an outer side perspective view of a clutch. It is an inner side perspective view of a clutch. It is the perspective view which looked at the clutch from diagonally lower. It is a perspective view of a pilot lever. It is a perspective view of a pilot lever. It is a principal part enlarged view which shows the normal state of a pilot lever. It is a principal part enlarged view which shows the state which the pilot lever engaged with the locking gear. It is operation | movement explanatory drawing by the pulling-out acceleration of the webbing of a lock unit (before operation | movement). It is operation | movement explanatory drawing (at the time of an action | operation start) by the pulling-out acceleration of the webbing of a lock unit. It is operation | movement explanatory drawing (at the time of transfer to a locked state) by the pulling-out acceleration of the webbing of a lock unit. It is operation | movement explanatory drawing (lock state) by the pulling-out acceleration of the webbing of a lock unit. It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of webbing winding start). It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of transfer to a lock release state). It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of lock release). It is operation | movement explanatory drawing by the vehicle body acceleration of a lock unit (before operation | movement). It is operation | movement explanatory drawing (at the time of an action | operation start) by the vehicle body acceleration of a lock unit. It is operation | movement explanatory drawing by the vehicle body acceleration of a lock unit (at the time of transfer to a locked state). It is operation | movement explanatory drawing (lock state) by the vehicle body acceleration of a lock unit. It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of webbing winding start). It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of transfer to a lock release state). It is operation | movement explanatory drawing at the time of the webbing winding start of a lock unit (at the time of lock release). It is operation | movement explanatory drawing by the vehicle body acceleration of a lock unit (at the time of a pawl synchronous shift | offset | difference). It is operation | movement explanatory drawing by the vehicle body acceleration of a lock unit (at the time of transfer to a locked state). It is operation | movement explanatory drawing by the vehicle body acceleration of a lock unit (at the time of transfer to a locked state). FIG. 36 is an assembled cross-sectional view including the lock arm of FIG. 35. It is operation | movement explanatory drawing (lock state) by the vehicle body acceleration of a lock unit. It is sectional drawing containing the axial center of a winding drum unit. It is a disassembled perspective view of a winding drum unit. It is the front view which looked at the winding drum from the attachment side of the ratchet gear. It is a perspective view of a ratchet gear. It is an inner side front view of a ratchet gear. It is X1-X1 arrow sectional drawing of FIG. It is a disassembled perspective view of a pretensioner unit. It is sectional drawing which shows the internal structure of a pretensioner unit. It is explanatory drawing which shows operation | movement of the pawl at the time of a vehicle collision. It is operation | movement explanatory drawing which pulls out a wire. It is operation | movement explanatory drawing which pulls out a wire. It is operation | movement explanatory drawing which pulls out a wire. It is operation | movement explanatory drawing which pulls out a wire. It is a perspective view of the pilot lever of the retractor for seatbelts which concerns on other embodiment. It is a perspective view of the pilot lever of the retractor for seatbelts which concerns on other embodiment. FIG. 10 is an operation explanatory view (when a pawl synchronization shift occurs) of a lock unit of a seatbelt retractor according to another embodiment according to vehicle body acceleration. It is operation | movement explanatory drawing (at the time of transfer to a locked state) by the vehicle body acceleration of the lock unit of the retractor for seatbelts which concerns on other embodiment. FIG. 55 is an assembled cross-sectional view including the lock arm of FIG. 54. It is operation | movement explanatory drawing (lock state) by the vehicle body acceleration of the lock unit of the retractor for seatbelts which concerns on other embodiment.
DETAILED DESCRIPTION Hereinafter, a seat belt retractor according to an embodiment of the present invention will be described in detail with reference to the drawings based on an embodiment.
First, a schematic configuration of the seatbelt retractor 1 according to the present embodiment will be described with reference to FIGS. 1 to 3. FIG. 1 is an external perspective view of a seatbelt retractor 1 according to this embodiment. 2 and 3 are exploded perspective views of the seat belt retractor 1 for each unit.
As shown in FIGS. 1 to 3, the seat belt retractor 1 is a device for winding a webbing 3 of a vehicle, and includes a housing unit 5, a winding drum unit 6, a pretensioner unit 7, and a winding unit. A spring unit 8 and a lock unit 9 are included.
Further, the lock unit 9 is fixed to one side wall portion 12 of the housing 11 constituting the housing unit 5 by means of each ny latch 9A and each locking hook 9B formed integrally with the mechanism cover 71 (see FIG. 5). ing. The lock unit 9 constitutes a lock mechanism 10 that stops the pull-out of the webbing 3 in response to a sudden pull-out of the webbing 3 or a rapid acceleration change of the vehicle, as will be described later (see FIG. 10). The take-up spring unit 8 winds the lock unit 9 as described later via three plate-like locking pieces 8A (see FIG. 6) protruding from the outer periphery of the spring case 67 (see FIG. 5). The drum unit 6 is fixed to the outer side in the rotation axis direction (see FIG. 8).
Further, the pretensioner unit 7 is arranged on the other side wall portion 13 opposite to the side wall portion 12 of the housing 11 formed in a substantially U shape in plan view, and on the outer side in the rotation axis direction of the winding drum unit 6 of the pretensioner unit 7. Are screwed by the respective screws 15 inserted therethrough. The pretensioner unit 7 includes a stopper pin 16 inserted into the side wall portion 13 from the outer side in the rotation axis direction of the winding drum unit 6 of the pretensioner unit 7, and the rotation of the winding drum unit 6 of the side wall portion 13 through the stopper pin 16. It is fixed by a push nut 18 inserted from the inside in the axial direction.
The winding drum unit 6 around which the webbing 3 is wound is rotatable between a lock unit 9 fixed to the side wall 12 of the housing unit 5 and a pretensioner unit 7 fixed to the side wall 13. Supported. The winding drum unit 6 is always urged in the winding direction of the webbing 3 by a winding spring unit 8 fixed outside the lock unit 9.
Next, a schematic configuration of the housing unit 5 will be described with reference to FIGS.
FIG. 4 is an exploded perspective view of the housing unit 5.
As shown in FIGS. 2 to 4, the housing unit 5 includes a housing 11, a bracket 21, a protector 22, a pawl 23, a pawl rivet 25, a torsion coil spring 26, a sensor cover 27, and a vehicle acceleration sensor 28. And connecting members 32 and 33 and a rivet 61.
Further, the housing 11 is formed in a substantially U shape in plan view by extending a back plate portion 31 fixed to the vehicle body and side wall portions 12 and 13 facing each other from both side edge portions of the back plate portion 31. It is made of steel. Further, the side wall portions 12 and 13 are connected to each other by connecting members 32 and 33 each having a horizontally long thin plate shape that is long in the direction of the rotation axis of the winding drum unit 6. In addition, an opening is formed in the central portion of the back plate portion 31 so as to reduce the weight and limit the amount of webbing 3 accommodated.
Further, the side wall portion 12 is formed with a through hole 36 into which the ratchet gear 35 of the winding drum unit 6 is inserted while forming a predetermined gap (for example, a gap of about 0.5 mm). The inner peripheral edge of the through hole 36 is configured to be recessed to the winding drum unit 6 side by a predetermined depth inward in the central axis direction, and to be opposed to the ratchet gear 35 of the winding drum unit 6.
Further, a peripheral edge facing the tip 37 (the other end) side portion 37 including the engaging teeth 23A and 23B of the pawl 23 obliquely below (through the diagonally lower left in FIG. 4) of the through hole 36. The notch portion 38 is cut out to a depth in which the distal end portion 37 is accommodated from the portion to the outside in the turning direction of the pawl 23 (the turning direction is away from the ratchet gear 35 of the pawl 23). Is formed. A through hole 41 for rotatably mounting the pawl 23 is formed on the side of the notch 38 on the back plate 31 side. In addition, an arcuate guide portion 38 </ b> A is formed coaxially with the through hole 41 at a portion where the pawl 23 on the through hole 41 side of the cutout portion 38 abuts.
On the other hand, a portion of the pawl 23 made of steel or the like that slides in contact with the guide portion 38A has a height substantially equal to the thickness of the side wall portion 12 and has the same radius of curvature as the guide portion 38A. A stepped portion 37A that is recessed in an arc is formed. Further, a guide hole 116 (see FIGS. 5 and 10) of the clutch 85 constituting the lock unit 9 is provided at the tip of the side surface of the pawl 23 on the outer side in the rotational axis direction (the front side in FIG. 4). A guide pin 42 to be inserted is erected.
A through hole 43 through which the pawl rivet 25 is inserted is formed at the base end portion (one end portion) of the pawl 23 and is rotated from the peripheral portion of the through hole 43 to the through hole 41 of the side wall portion 12. A cylindrical boss portion 45 that can be inserted is erected at a height substantially equal to the thickness dimension of the side wall portion 12. The pawl 23 can be rotated by a pawl rivet 25 fitted into the through hole 43 from the outside of the side wall portion 12 in a state where the boss portion 45 is inserted into the through hole 41 of the side wall portion 12 from the inside of the housing 11. Fixed to. Accordingly, the engaging teeth 23A and 23B of the pawl 23 and the ratchet gear portion 35A formed on the outer peripheral surface of the ratchet gear 35 are arranged so as to be substantially flush with the outer surface of the side wall portion 12.
The head of the pawl rivet 25 is formed in a disk shape having a larger outer diameter than the through hole 41 and a predetermined thickness (for example, a thickness of about 1.5 mm). The torsion coil spring 26, which functions as an example of a return spring, is disposed so as to surround the head of the pawl rivet 25 with one winding, and one end side 26 </ b> A is attached to the guide pin 42 of the pawl 23. . The wire diameter of the torsion coil spring 26 is approximately half the height of the head of the pawl rivet 25 (for example, the wire diameter is about 0.6 mm). Accordingly, the height of one turn of the torsion coil spring 26 is set to be substantially the same as the height of the head of the pawl rivet 25.
Further, the other end side 26B of the torsion coil spring 26 passes through the side wall portion 12 side of the one end side 26A so as to be slidable on the side wall portion 12, and then the inner side direction of the side wall portion 12 (in FIG. 4, the back side of the side wall portion 12). Direction), and is inserted through a mounting hole 46 formed in the side wall portion 12. Further, the end portion of the other end side 26B is bent into a substantially U shape and is brought into contact with the inner surface of the side wall portion 12 to constitute a retaining portion. As a result, the pawl 23 is biased by the torsion coil spring 26 so as to rotate toward the back side of the notch 38 (in the counterclockwise direction in FIG. 3), and the distal end including the engaging teeth 23A and 23B. The side portion 37 is in contact with the back side of the notch 38. Accordingly, the pawl 23 is urged to rotate in a direction away from the ratchet gear 35 by the torsion coil spring 26.
Further, as shown in FIGS. 2 to 4, below the through hole 36 of the side wall portion 12 (downward in FIG. 4), below the central axis of the through hole 36 (downward in FIG. 4). To the back plate portion 31 side, a substantially rectangular opening 47 is formed. In addition, a shallow substantially box-shaped sensor cover 27 having a substantially square cross section substantially the same as the opening 47 is fitted into the opening 47 from the outside (the front side in FIG. 4). The resin-made sensor cover 27 has a flange formed on the opening-side peripheral edge abutting on the outer peripheral edge of the opening 47 (the front-side peripheral edge in FIG. 4), and the sensor cover. 27, a pair of locking claws 27A (in FIG. 4, the locking claw 27A on the upper end surface is shown) projecting from both ends in the up-down direction are shown in FIG. It is inserted in the back side of the direction both ends and is elastically locked.
Further, the vehicle acceleration sensor 28 includes a resin-made sensor holder 51 having a substantially box shape opened to the upper side in the vertical direction (upper side in FIG. 4) and having a mortar-shaped mounting portion formed on the bottom surface portion, Inertial mass 52 formed in a spherical body of metal such as steel and movably mounted on the mounting portion, and placed on the upper side in the vertical direction of inertial mass 52 and opposite to pawl 23 From the sensor lever 53 made of resin, the end edge portion (the right end edge portion in FIG. 4) is supported by the sensor holder 51 so as to be swingable vertically (in the vertical direction in FIG. 4). It is configured.
Then, the vehicle acceleration sensor 28 is fitted into the sensor cover 27, and a pair of locking claws 51 </ b> A (one engagement in FIG. 4) provided on both side surfaces facing both side walls in the sensor cover 27 of the sensor holder 51. The vehicle acceleration sensor 28 is attached to the housing 11 via the sensor cover 27 by inserting and locking the pawl 51A into each locking hole 27B of the sensor cover 27.
Further, the side wall portion 12 has three corners, that is, both corners of an upper edge portion (upper edge portion in FIG. 4) and a lower portion of the through hole 36 (downward direction in FIG. 4). Each mounting hole 55 into which each ny latch 9A of the lock unit 9 is fitted and attached is formed. In addition, each locking piece to which each locking hook 9 </ b> B of the lock unit 9 is elastically locked is located at the center of the left and right side edges of the side wall 12 (the vertical center in FIG. 4). 56 is formed so as to protrude perpendicularly to the rotation axis of the winding drum unit 6.
Further, a through hole 57 through which the winding drum unit 6 is inserted is formed in the side wall portion 13 at the center portion. Further, the side wall portion 13 includes a substantially lower end edge portion (lower end edge portion in FIG. 2), a corner portion on the connecting member 33 side, and an upper end edge portion (upper end edge portion in FIG. 2). The screw holes 58 into which the screws 15 are screwed are formed by burring in the direction of the pretensioner unit 7 at the corners on the back plate portion 31 side. Further, a through hole 59 through which the stopper pin 16 is inserted is formed in the side wall portion 13 at a corner portion on the connecting member 32 side of the upper end edge portion (the upper end edge portion in FIG. 2).
Moreover, the bracket 21 attached to each upper end edge (the upper end edge in FIG. 2) of the back plate 31 by each rivet 61 is formed of a steel material or the like, and the upper end edge of the back plate 31 A laterally long through hole 62 extending in the width direction of the back plate portion 31 from which the webbing 3 is pulled out is formed in an extending portion extending in the direction of the connecting member 32 at a substantially right angle from the side, and is formed of a synthetic resin such as nylon. A horizontally long frame-shaped protector 22 is fitted. Further, a bolt insertion hole 63 through which a bolt is inserted when being attached to a fastening piece (not shown) of the vehicle is formed in the lower end portion (the lower end portion in FIG. 2) of the back plate portion 31. .
[Schematic configuration of winding spring unit]
Next, a schematic configuration of the winding spring unit 8 will be described with reference to FIGS. 2, 3, 5 to 8, and 11.
5 and 6 are exploded perspective views of the winding spring unit 8 and the lock unit 9 including the ratchet gear. 7 and 8 are cross-sectional views for explaining the attachment of the spring case 67. FIG. FIG. 11 is an enlarged cross-sectional view of a main part including the winding spring unit 8 and the lock unit 9 of the seat belt retractor 1.
2, 3, 5, 6, and 11, the winding spring unit 8 includes a spiral spring 65 and an outer end 65 </ b> A of the spiral spring 65 erected from the bottom surface of the inner peripheral edge. A spring case 67 that is fixed to the rib 66 and accommodates the spiral spring 65, and a spring shaft 68 to which the inner end 65B of the spiral spring 65 is connected and the spring force is urged are configured. Further, the spring case 67 is formed with a groove portion 67A having a predetermined depth (for example, a depth of about 2.5 mm) over the entire circumference at the edge portion on the mechanism cover 71 side constituting the lock unit 9. ing.
Further, at the edge of the spring case 67 on the mechanism cover 71 side, plate-shaped locking pieces 8A having a substantially rectangular shape in front view from three locations on the outer peripheral portion are formed in through holes formed in a substantially central portion of the mechanism cover 71. The projection 73 is concentrically provided with respect to the central shaft 73 </ b> A. In addition, the outer peripheral surface on the outer side in the radial direction with respect to the central axis 73A of the through hole 73 of each locking piece 8A is formed so as to be located concentrically.
Further, as shown in FIGS. 6 and 7, the locking piece 8 </ b> A located at the lower end edge of the spring case 67 is continuous with the end edge on the counterclockwise direction side with respect to the central axis 73 </ b> A of the through hole 73. A fixed portion 8B having a square cross section is provided continuously. In addition, a through hole 8C parallel to the central axis 73A of the through hole 73 is formed at a substantially central portion of the fixed part 8B, and fixed so as to close an end of the through hole 8C on the outer side in the central axis 73A direction. The pin 8D is integrally formed.
Further, the shaft diameter of the fixing pin 8D is formed to be substantially the same as the inner diameter of the through hole 8C, and the fixing pin 8D can be pushed into the through hole 8C by pushing the fixing pin 8D toward the mechanism cover 71 with a predetermined load or more. Further, the length of the fixing pin 8D is formed so as to be longer than the thickness of the fixing portion 8B.
On the other hand, the mechanism cover 71 has thick plate-like holding portions 72 having a substantially rectangular cross section protruding from the three locations facing the respective locking pieces 8A on the outer peripheral portion on the winding spring unit 8 side. As shown in FIGS. 5 and 7, the base end portion of each holding portion 72 is notched in the counterclockwise direction with respect to the central axis 73 </ b> A of the through hole 73, and the back end portion is closed. A fitting groove 72A having a substantially rectangular cross section is formed.
In addition, the bottom surface portion on the radially outer side with respect to the central axis 73A of the through hole 73 of each fitting groove portion 72A has a slightly larger radius (for example, approximately about the outer edge in the radial direction of each locking piece 8A of the spring case 67). The radius is larger by 0.2 mm to 0.5 mm.). Further, the width dimension of each fitting groove 72A in the direction of the central axis 73A is formed to be approximately the same as the thickness dimension of each locking piece 8A. As will be described later, each locking piece 8A has each fitting groove 72A. It is comprised so that it may insert in (refer FIG. 8).
The mechanism cover 71 is provided with a substantially ring-shaped rib portion 71A standing at a predetermined height (for example, a height of about 2 mm) along the outer peripheral edge of the winding drum unit 6 in the rotation axis direction. It has been. The rib portion 71A is provided at a position corresponding to the groove portion 67A, and the inner diameter and the outer diameter of the rib portion 71A are in a state in which the rib portion 71A is fitted in the groove portion 64A with respect to the inner diameter and the outer diameter of the groove portion 67A. Each is provided so as to form a predetermined gap (for example, a gap of about 0.1 mm to 0.3 mm).
Further, as shown in FIGS. 5 to 7, in the vicinity of the central axis 73A of the holding portion 72 facing the lower end edge of the rib portion 71A, the spring case 67 is provided in the mechanism cover as will be described later. When attached to 71, a fixing hole 74 having a circular cross section is formed at a position facing the fixing pin 8D.
The inner diameter of the fixing hole 74 is formed to be smaller than the outer diameter of the fixing pin 8D of the spring case 67 by a predetermined dimension (for example, about 0.1 mm to 0.3 mm), and the fixing pin 8D is press-fitted. It is provided so that it can. In addition, a cylindrical boss 75 whose rear side is closed is erected on the rear side of the fixing hole 74, that is, on the peripheral edge portion on the side wall 12 side of the housing 11. Further, the inner diameter of the cylindrical boss 75 is formed in a circular cross section having the same diameter as that of the fixing hole 74 and is formed coaxially with the fixing hole 74.
Here, an attachment method for attaching the take-up spring unit 8 to the mechanism cover 71 will be described.
As shown in FIG. 6, first, the outer end 65 </ b> A of the spiral spring 65 is fitted into a rib 66 erected on the inner side of the spring case 67 and housed in the spring case 67, and the spring is connected to the inner end 65 </ b> B of the spiral spring 65. The mounting groove 68C of the shaft 68 is fitted. As shown in FIGS. 5 and 6, the spring shaft 68 has a pin 69 erected at a substantially central position of the bottom surface portion of the spring case 67 and is inserted into the through hole 68A in the bottom surface portion, and the bottom surface portion side is pinned. 69 is rotatably abutted on the peripheral edge of 69.
Then, as shown in FIG. 7, each locking piece 8 </ b> A protruding radially outward from three locations on the outer peripheral portion of the spring case 67 is connected to the edge portion of the holding portion 72 of the mechanism cover 71 on the front view clockwise side. Position it so as to face. Further, as shown in FIGS. 5 and 11, the distal end portion 93 </ b> A of the rotating shaft portion 93 of the locking gear 81 protruding from the through hole 73 of the mechanism cover 71 is formed in a rectangular cross-section and along the central axis. A shaft hole 93B into which the pin 69 is inserted is formed.
Subsequently, as shown in FIGS. 6 and 11, the distal end portion 93 </ b> A of the rotating shaft portion 93 of the locking gear 81 protruding from the through hole 73 of the mechanism cover 71 is formed in a cylindrical hole formed in a rectangular cross section of the spring shaft 68. The rotary shaft portion 93 of the locking gear 81 is connected to the spring shaft 68 so as not to be relatively rotatable. At the same time, as shown in FIG. 7, the rib portion 71 </ b> A standing on the peripheral edge portion of the mechanism cover 71 is inserted into the groove portion 67 </ b> A of the spring case 67.
Then, as shown in FIGS. 7 and 8, the spring case 67 is rotated in the webbing pull-out direction, that is, in the counterclockwise direction when viewed from the front (in the direction of arrow 70 in FIG. 7). 8A is inserted into the fitting groove portion 72A of each holding portion 72 of the mechanism cover 71 and is brought into contact with the back side of each fitting groove portion 72A. Accordingly, the spring case 67 is positioned so as not to move in the radial direction and the axial direction with respect to the central axis 73A of the through hole 73 of the mechanism cover 71.
Thereafter, in this state, the fixing pin 8 </ b> D of the spring case 67 is pressed and press-fitted into the through hole 8 </ b> C of the fixing portion 8 </ b> B and the fixing hole 74 of the mechanism cover 71, whereby the winding spring unit 8 is inserted into the mechanism cover 71. On the other hand, the winding spring unit 8 is fixed in a relatively non-rotatable manner, and is attached in a state where the winding spring unit 8 is in contact with the outer side in the rotation axis direction of the winding drum unit 6 of the mechanism cover 71.
As a result, the rib portion 71 </ b> A erected on the peripheral portion of the mechanism cover 71 is fitted into the groove portion 67 </ b> A of the spring case 67, and dust and dust are prevented from entering the spring case 67. Further, as shown in FIG. 11, the end of the spring shaft 68 on the lock unit 9 side with the bottom surface of the mechanism cover 71 in contact with the peripheral edge of the pin 69 so as to be rotatable, A predetermined gap (for example, a gap of about 0.3 mm) is formed between the peripheral edge portion of the through hole 73 formed in the substantially central portion of the mechanism cover 71.
At the same time, a predetermined gap (for example, a gap of about 0.3 mm) is also formed between the bottom surface of the cylindrical hole 68B of the spring shaft 68 and the distal end portion 93A of the rotating shaft portion 93 of the locking gear 81. Yes. Therefore, the spring shaft 68 is provided between the spring case 67 and the mechanism cover 71 so as to be movable in the axial direction of the central shaft 73A by a predetermined gap.
[Schematic configuration of locking mechanism]
Next, FIG. 5, FIG. 6, FIG. 9 thru | or FIG. 9 about schematic structure of the lock unit 9 which comprises the lock mechanism 10 which stops the pull-out of the webbing 3 in response to the rapid change of the webbing 3 and the rapid acceleration of a vehicle. This will be described with reference to FIG.
FIG. 9 is an assembly sectional view including the lock arm of the lock unit 9. FIG. 10 is a partially cutaway cross-sectional view in which a part of the bottom surface of the mechanism cover 71 of the lock unit 9 is cut away. FIG. 12 is an outer perspective view of the clutch. FIG. 13 is an inside perspective view of the clutch. FIG. 14 is a perspective view of the clutch as viewed obliquely from below. 15 and 16 are perspective views of the pilot lever. FIG. 17 is an enlarged view of a main part showing a normal state of the pilot lever. FIG. 18 is an enlarged view of a main part showing a state where the pilot lever is engaged with the locking gear.
As shown in FIGS. 5, 6, and 9 to 11, the lock unit 9 includes a mechanism cover 71, a locking gear 81, a lock arm 82, a sensor spring 83, a clutch 85, and a pilot lever 86. In the present embodiment, among the members constituting the lock unit 9, the members excluding the sensor spring 83 are formed of synthetic resin, and the friction coefficient between the members when they are in contact with each other is small. is there.
The mechanism cover 71 is formed with a substantially box-shaped mechanism housing portion 87 having a substantially circular bottom surface that is open on the side wall 12 side of the housing 11, and is configured to house the locking gear 81, the clutch 85, and the like. Yes. Further, the mechanism cover 71 is formed in a concave shape having a substantially square cross section at a corner portion (the lower left corner portion in FIG. 6) facing the vehicle acceleration sensor 28 attached to the housing 11 via the sensor cover 27. The sensor housing portion 88 is provided.
When the mechanism cover 71 is attached to the side wall portion 12 by the ny latches 9A and the locking hooks 9B, the sensor holder 51 of the vehicle acceleration sensor 28 is fitted into the sensor housing portion 88, and the sensor lever 53 is moved in the vertical direction. It is configured so as to be swingable vertically (in the vertical direction in FIG. 6). Further, the mechanism housing portion 87 and the sensor housing portion 88 are opened so as to communicate with the lower end portion substantially central portion (in FIG. 6, the lower end portion substantially central portion) of the mechanism cover portion 71 of the mechanism cover 71. An opening 89 is formed.
The opening 89 has a vertically extending vertical end of the lock claw 53A that protrudes upward from the front edge of the sensor lever 53 of the vehicle acceleration sensor 28 (the upward direction in FIG. 6). In FIG. 6, the front end of the lock claw 53 </ b> A is positioned in the vicinity of the receiving plate portion 122 (see FIG. 10) of the pilot lever 86. As will be described later, when the inertial mass body 52 is moved by acceleration exceeding a predetermined value and the sensor lever 53 is rotated upward in the vertical direction, the lock claw 53A is connected to the pilot lever 86 via the opening 89. The pilot lever 86 is configured to rotate upward in the vertical direction by contacting the receiving plate portion 122 (see FIG. 27).
Further, a cylindrical support boss 91 is erected on the substantially circular bottom surface portion of the mechanism accommodating portion 87 from the peripheral edge portion of the through hole 73 formed in the central portion. The outer periphery of the tip end portion of the support boss 91 on the side of the locking gear 81 is formed with a tapered chamfered portion 91A inclined at a predetermined angle (for example, an inclination angle of about 30 °) toward the tip end over the entire circumference. ing. The support boss 91 is fitted with a cylindrical rotary shaft portion 93 protruding from the back side facing the mechanism cover 71 at the center portion of the disc-shaped bottom surface portion 92 of the locking gear 81 for sliding rotation. Supported as possible.
The locking gear 81 is erected in an annular shape from the entire circumference of the disk-shaped bottom surface portion 92 toward the clutch 85, and locking gear teeth 81 </ b> A that engage with the pilot lever 86 are formed on the outer peripheral portion. The locking gear teeth 81A are formed so as to engage with the engaging claws 86A of the pilot lever 86 only when the locking gear 81 rotates in the webbing pull-out direction (see FIG. 16).
Further, as shown in FIGS. 5, 6, 10, and 11, a shaft portion standing on the center portion of the end surface of the ratchet gear 35 on the side of the locking gear 81 is provided at the center portion of the bottom surface portion 92 of the locking gear 81. A through hole into which 76 is inserted is formed. A cylindrical base 94 is erected from the peripheral edge of the through hole on the mechanism cover 71 side at substantially the same height as the axial height of the locking gear teeth 81A. The cylindrical rotating shaft portion 93 of the locking gear 81 is smaller than the base portion 94 from the edge of the mechanism base 71 side of the cylindrical base portion 94, and is substantially equal to the inner diameter of the support boss 91. Coaxially extending toward the mechanism cover 71 with the same outer diameter. Further, the end of the rotary shaft 93 on the side of the mechanism cover 71 is closed, and a distal end portion 93A having a rectangular cross section extends coaxially.
Therefore, inside the base portion 94 and the rotating shaft portion 93, the shaft portion 76 that opens to the end surface on the ratchet gear 35 side of the locking gear 81 and is erected on the center portion of the end surface on the mechanism cover 71 side of the ratchet gear 35. A shaft hole portion 94A having a circular cross section is formed. In addition, a plurality of ribs 94B are erected at the same height in the radial direction along the axial direction on the inner peripheral surface of the shaft hole portion 94A, and come into contact with the outer peripheral surface of the shaft portion 76 of the ratchet gear 35. Is provided. In addition, the shaft portion 76 is formed in a truncated cone shape with a half portion on the base end portion side of the total length, and a half portion on the distal end side is continuous with the truncated cone shape.
Further, around the base end portion of the rotating shaft portion 93, an annular rib 95 is erected coaxially at a height substantially equal to the thickness dimension of the substantially disc-shaped plate portion 111 of the clutch 85, An insertion groove 95A is formed. The inner peripheral wall portion of the annular rib 95 is inclined radially outward at an angle equal to or greater than the inclination angle of the tip end portion of the support boss 91 (for example, an inclination angle of about 45 °). Further, the outer diameter of the bottom surface portion of the insertion groove 95 </ b> A formed inside the annular rib 95 is formed to be substantially the same as the outer diameter of the tip portion of the support boss 91.
Further, the outer diameter of the annular rib 95 is formed to be substantially the same as the inner diameter of the through hole 112 formed in the central portion of the plate portion 111 of the clutch 85 and is smaller than the outer diameter of the base portion 94. It is formed in the diameter. Further, an annular rib 112A is erected at a predetermined height (for example, a height of about 0.5 mm) at the end edge portion of the through hole 112 of the clutch 85 on the side of the locking gear 81. Has been.
Thus, after the annular rib 95 of the locking gear 81 is fitted into the through hole 112 of the clutch 85 and the annular rib 112A is brought into contact with the outer peripheral side base end portion of the rib 95, the rotary shaft portion 93 is The back surface of the locking gear 81 is inserted into the support boss 91 of the mechanism cover 71 and the tip of the support boss 91 is brought into contact with the bottom surface of the insertion groove 95 </ b> A formed on the radially inner side of the annular rib 95. A rotating shaft portion 93 protruding from the side is attached coaxially to and supported by the support boss 91 over almost the entire height. The annular rib 95 of the locking gear 81 is fitted into the through hole 112 so as to be slidable and rotatable, and the clutch 85 is accommodated between the locking gear 81 and the mechanism cover 71 so as to be rotatable within a certain rotation range. The
As shown in FIGS. 5, 6, and 11, the end face of the locking gear 81 on the ratchet gear 35 side has four convex portions 96 that project into a substantially rectangular cylindrical shape having a long cross section in the circumferential direction. , And are erected so as to be located on concentric circles at a predetermined distance (for example, a distance of about 14 mm) outward in the radial direction from the rotation shaft 81B at equal central angles. One convex portion 96 is partially cut away at the outer peripheral edge in the radial direction. Further, a positioning hole 97 having a predetermined inner diameter (for example, an inner diameter of about 3.5 mm) is provided at a substantially central position between a pair of convex portions 96 adjacent in the circumferential direction on the bottom surface of the locking gear 81. Is formed.
Further, on the end surface portion of the ratchet gear 35 that faces the locking gear 81, four through holes 98 having a substantially rectangular cross section that is substantially the same shape as the convex portion 96 of the locking gear 81 and having a substantially rectangular cross section are formed at an equal central angle. In addition, it is formed at a position facing each convex portion 96 that is separated from the rotation shaft 81B by a predetermined distance (for example, a distance of about 14 mm) radially outward.
Further, on the end surface portion of the ratchet gear 35 facing the locking gear 81, the inner diameter of the positioning hole 97 is set at a position facing the positioning hole 97 between a pair of circumferentially adjacent through holes 98. Positioning pins 99 formed with substantially the same outer diameter are provided upright. Further, the height of the shaft portion 76 erected on the outer end surface of the ratchet gear 35 in the rotation axis direction is formed to be substantially equal to the depth of the shaft hole portion 94 </ b> A of the locking gear 81. Further, the depth of the shaft hole portion 94 </ b> A of the locking gear 81 is formed such that the tip end of the shaft portion 76 is located on the inner side in the rotation axis direction than the tip end of the tip end portion 93 </ b> A of the rotation shaft portion 93.
Accordingly, the shaft portion 76 of the ratchet gear 35 is fitted into the shaft hole portion 94A of the locking gear 81, and the positioning pin 99 of the ratchet gear 35 is fitted into the positioning hole 97 of the locking gear 81. The convex portion 96 is fitted into each through hole 98 of the ratchet gear 35. As a result, the locking gear 81 is coaxially attached to the ratchet gear 35 in a relatively non-rotatable manner while the locking gear 81 is in contact with the end surface of the ratchet gear 35 in the rotational axis direction. 76 is positioned and supported in the support boss 91 of the mechanism cover 71 via the rotating shaft portion 93 of the locking gear 81.
Further, on the outer peripheral surface of each convex portion 96 of the locking gear 81, a rib (not shown) protruding outward in the radial direction is erected along the rotation axis direction of the ratchet gear 35. And each convex part 96 of the locking gear 81 is press-fitted and attached to each through hole 98 of the ratchet gear 35 while crushing each rib. As a result, the locking gear 81 can be attached to the ratchet gear 35 without rattling, and the locking gear 81 is held by the ratchet gear 35, so that the assembly work can be made more efficient.
Further, the ratchet gear 35 of the winding drum unit 6 is attached coaxially to the spring shaft 68 of the winding spring unit 8 through the distal end portion 93A of the rotating shaft portion 93 of the locking gear 81 so as not to be relatively rotatable. Accordingly, the winding drum unit 6 is always urged to rotate in the webbing winding direction via the winding spring unit 8.
In addition, although each convex part 96 was formed in the cylinder shape, you may form so that a cross section may protrude in the substantially rectangular solid shape long in the circumferential direction. In addition, four through holes 98 having a substantially rectangular cross section that is long in the circumferential direction are provided at positions facing the respective convex portions 96 of the ratchet gear 35. The cross sectional shape of the through holes 98 is the same as that of the through holes 98. You may make it provide four recessed parts recessed at the depth more than the height of each convex part 96. FIG.
Further, as shown in FIGS. 5, 6, 9 to 11, a cylindrical support boss 101 adjacent to the base portion 94 is provided on the surface of the bottom surface portion 92 of the locking gear 81 on the clutch 85 side. It is erected at a height lower than the locking gear teeth 81A. The lock arm 82 made of synthetic resin formed in a substantially arcuate shape so as to surround the base portion 94 is inserted into the through-hole 102 formed in the end portion on the base portion 94 side in the substantially central portion in the longitudinal direction. A support boss 101 is rotatably inserted and pivotally supported.
Further, an elastic locking piece 103 having an inverted L-shaped cross section is erected on the mechanism cover 71 side at a position near the outer side in the radial direction with respect to the support boss 101 on the bottom surface portion 92 of the locking gear 81. The elastic locking piece 103 is inserted into the window 104 having a stepped portion having a substantially fan shape formed on the side of the through hole 102 of the lock arm 82, and is elastic to be rotatable around the axis of the base 94. Is locked.
Further, as shown in FIGS. 9 and 10, the locking gear 81 has a spring support pin 105 in which one end side of the sensor spring 83 is fitted into a rib portion extending radially outward from the outer peripheral surface of the base portion 94. The webbing pull-out direction is perpendicular to the axis of the base 94. Further, a spring support pin 106 into which the other end side of the sensor spring 83 is fitted is erected on the side wall of the lock arm 82 facing the spring support pin 105.
Accordingly, as shown in FIGS. 9 and 10, the lock arm 82 moves toward the webbing pull-out direction side with respect to the axis of the support boss 101 by fitting both ends of the sensor spring 83 into the spring support pins 105 and 106 ( In FIG. 9, it is biased with a predetermined load so as to rotate (in the direction of arrow 107). The lock arm 82 has a stopper 114 formed so that an end edge portion on the engagement claw 109 side that engages with the clutch gear 108 of the clutch 85 protrudes radially outward from the base portion 94 of the locking gear 81. It is in contact with.
On the other hand, as will be described later, the lock arm 82 is rotated in the webbing take-up direction (in the opposite direction to the arrow 107 in FIG. 9) against the urging force of the sensor spring 83 and engaged with the clutch gear 108. In this case, the end edge of the engagement claw 109 opposite to the engagement portion has a spindle-shaped detent 115 with a predetermined clearance (for example, a clearance of about 0). .3 mm)) (see FIG. 20).
In addition, as shown in FIGS. 5, 6, 9 to 14, the clutch 85 is sandwiched between the locking gear 81 and the mechanism cover 71 and can be rotated in the mechanism housing portion 87 within a certain rotation range. Be contained. On the side of the locking gear 81 of the clutch 85, an outer diameter slightly smaller than the inner peripheral diameter of the annular rib formed on the outer peripheral portion of the locking gear tooth 81A of the locking gear 81 is coaxial with the through hole 112. An annular rib portion 113 is provided upright.
A clutch gear 108 that engages with the engaging claw 109 of the lock arm 82 is formed on the inner peripheral surface of the rib portion 113 (see FIG. 20). As will be described later, the clutch gear 108 is formed so as to engage with the engagement claw 109 of the lock arm 82 only when the locking gear 81 rotates in the webbing pull-out direction with respect to the axis of the through hole 112. (See FIG. 20).
An annular outer rib portion 117 is provided upright on the outer peripheral portion of the substantially disc-shaped plate portion 111 of the clutch 85 so as to surround the rib portion 113. Further, the edge of the outer rib 117 on the side of the ratchet gear 35 is extended outward in the radial direction with respect to the central axis of the through hole 112, and extended slightly inclined toward the ratchet gear 35. The flange portion 118 is formed over substantially the entire circumference.
Further, the corner of the outer rib 117 facing the pawl 23 (the lower left corner in FIG. 9) is vertically downward from the outer peripheral surface of the outer rib 117 (downward in FIG. 5). ) Is provided. The guide block portion 119 has a substantially elongated guide hole 116 in which a guide pin 42 erected on the side surface of the tip portion including the engaging teeth 23A and 23B of the pawl 23 is loosely fitted from the ratchet gear 35 side. Is formed.
As shown in FIG. 10, the guide hole 116 is formed in a long groove shape substantially parallel to the webbing pull-out direction (vertical direction in FIG. 10) at the corner of the outer rib portion 117 facing the pawl 23. ing. As a result, when the clutch 85 is rotated in the webbing pull-out direction (indicated by arrow 107 in FIG. 9) as will be described later, the guide pin 42 is moved along the guide hole 116 and the pawl 23 is moved. Each engagement tooth 23A, 23B is rotated so as to approach the ratchet gear portion 35A of the ratchet gear 35 (see FIGS. 20 to 22).
Further, the pawl 23 is urged to rotate away from the ratchet gear 35 by the torsion coil spring 26, and the clutch 85 is urged by the guide pin 42 of the pawl 23 that is loosely fitted in the guide hole 116. . Due to this urging force, the clutch 85 is the end edge portion at the position farthest away from the ratchet gear 35 in the rotation radial direction of the clutch 85 in the guide hole 116 (the lower end edge portion of the guide hole 116 in FIG. 9). ) Is biased so as to be in a rotational posture in a state where the guide pin 42 of the pawl 23 abuts, so that the webbing is pulled out in a direction opposite to the drawing direction. Therefore, the clutch urging mechanism 129 is configured by the pawl 23 and the torsion coil spring 26.
At the same time, the pawl 23 is normally the end edge portion at the position farthest away from the ratchet gear 35 in the radial direction of the clutch 85 in the guide hole 116 (the lower end edge portion of the guide hole 116 in FIG. 9). ), The guide pin 42 of the pawl 23 abuts and the rotation is restricted, so that it is held so as to be located in the vicinity of the back side of the notch 38 formed in the side wall 12.
Further, the lower end edge portion (the lower end edge portion in FIG. 6) of the outer rib portion 117 of the clutch 85 is located above the sensor housing portion 88 from the end surface portion on the ratchet gear 35 side of the guide block portion 119 (in FIG. 6). The plate-like extension part 120 extended from the flange part 118 to the outer side in the radial direction in a substantially arc shape is formed up to the part facing the upper direction. Further, as shown in FIGS. 9, 10, 12 to 14, the cylindrical shaft of the pilot lever 86 is positioned in the vicinity of the end edge portion on the opposite side to the guide block portion 119 of the extension portion 120. A thin columnar mounting boss 123 fitted into the portion 121 (see FIG. 15) is erected on the mechanism cover 71 side at substantially the same height as the outer rib portion 117.
Here, as shown in FIGS. 9, 10, 15, and 16, the pilot lever 86 includes a cylindrical shaft portion 121, a plate-like engagement claw portion 86 </ b> A, and a thin plate-like receiving plate portion 122. , And a thin plate-like connecting plate portion 124. The axial length of the shaft portion 121 is formed to be approximately the same as the height of the mounting boss 123 provided upright on the extension portion 120. Further, the plate-like engagement claw portion 86A is formed in a substantially L shape in the rotational axis direction when the tip portion is obliquely bent toward the locking gear 81 side. Further, the plate-like engaging claw portion 86A is formed from the outer peripheral surface of the shaft portion 121 so as to be substantially horizontal when the pilot lever 86 is rotated by its own weight and is restricted from rotating downward in the vertical direction. A predetermined length projecting toward the guide hole 116 with a width shorter than the length of the shaft 121 is provided.
Further, the thin plate-like receiving plate portion 122 is projected from the outer peripheral surface of the shaft portion 121 to the tangential guide hole 116 side so as to face the engaging claw portion 86A, and the distal end portion is the distal end side of the engaging claw portion 86A. It is bent at an angle so that it is almost parallel to. Further, the thin plate-like connecting plate portion 124 is formed so as to connect the engaging claw portion 86 </ b> A and the front end portion of the receiving plate portion 122. Further, in the vicinity of the base end portion of the engaging claw portion 86A, an upward detent portion 125 that restricts the rotation of the pilot lever 86 in the locking gear 81 side direction, that is, the upward rotation in the vertical direction, is a shaft portion. The outer peripheral surface 121 protrudes radially outward. Further, the upward detent portion 125 has a predetermined height (for example, a height) that is substantially the same width as the width of the engaging claw portion 86A and is substantially perpendicular to the base end portion of the engaging claw portion 86A. It is about 1.5 mm.) Projected.
Further, on the end surface portion (the upper end surface portion in FIG. 15) of the engagement claw portion 86A that faces the locking gear 81, the engagement claw portion 86A starts from the portion where the tip portion is obliquely bent toward the locking gear 81 side. The rib portion 86B is provided upright at the substantially central portion in the width direction along the longitudinal direction. The rib portion 86B is about half the width of the engaging claw portion 86A, and has a constant height (for example, a constant height) from a portion where the tip portion is obliquely bent toward the locking gear 81 side to a substantially central portion in the longitudinal direction. Furthermore, it is erected in a substantially triangular shape as viewed in the rotational axis direction from the substantially central portion in the longitudinal direction to the base end portion of the upward detent portion 125 continuously.
Therefore, the engaging claw portion 86A has a bending strength in the locking gear 81 side direction from the portion bent obliquely to the locking gear 81 side by the rib portion 86B to the substantially central portion in the longitudinal direction, and the locking gear 81 at the distal end portion. It is formed so as to be larger than the bending strength in the lateral direction. In addition, the engaging claw 86A has a bending strength in the locking gear 81 side direction from the substantially central portion in the longitudinal direction to the proximal end of the engaging claw 86A on the shaft 121 side by the rib 86B. It is formed so as to be larger than the bending strength in the direction toward the locking gear 81 from the portion bent obliquely to the side to the substantially central portion in the longitudinal direction.
Further, on the opposite side to the receiving plate 122 of the shaft 121 in the tangential direction, a downward detent for restricting rotation of the pilot lever 86 in the direction of the sensor lever 53, that is, downward rotation in the vertical direction. 126 protrudes radially outward from the outer peripheral surface of the shaft 121. Further, the downward rotation preventing portion 126 has a width dimension in the rotation axis direction narrower than the width in the rotation axis direction of the receiving plate portion 122 from the end surface side opposite to the ratchet gear 35 of the shaft portion 121. A predetermined height (for example, a height of about 1.5 mm) is provided so as to face the base end portion of the portion 122.
Further, a predetermined depth in the radial direction (for example, a depth of about 0.5 mm) is provided on the outer peripheral surface from the base end portion of the receiving plate portion 122 of the shaft portion 121 to the base end portion of the downward rotation preventing portion 126. Thus, a concave portion 127 having a substantially sectoral cross section that is recessed to a substantially central portion in the axial direction is formed. In addition, a plate-like convex portion 128 is provided at the end edge on the axially central portion side of the concave portion 127 with a predetermined height (for example, a height of about 1) outward in the radial direction over the entire circumferential width of the concave portion 127. .5 mm)).
Further, as shown in FIGS. 9, 10, 12 to 14, the pilot lever support block 131 is substantially the same height as the outer rib portion 117 at the edge portion of the extension portion 120 facing the mounting boss 123. And projecting toward the mechanism cover 71 side. As shown in FIG. 14, the pilot lever support block 131 has an inner side facing the mounting boss 123 extending vertically downward from the outer peripheral surface of the outer rib portion 117, and the pilot lever 86 is locked as described later. An upper restricting end surface portion 132 with which the upper detent portion 125 abuts when rotated to the gear 81 side is formed.
As shown in FIG. 14, the inner side of the pilot lever support block 131 facing the mounting boss 123 is further extended from the upper regulating end surface portion 132 to the vertical lower end edge portion of the extending portion 120. A smooth curved surface that is substantially semicircular when viewed from the front with a radius of curvature that is coaxial with the mounting boss 123 and slightly larger than the radius of the outer peripheral surface of the shaft 121 of the pilot lever 86 (for example, about 0.1 mm larger). A load receiving surface 133 is provided.
As shown in FIGS. 12 and 14, a stepped portion 135 is formed at the edge portion on the lower side in the vertical direction of the pilot lever support block 131 by notching a predetermined height to the extending portion 120 side. As will be described later, when the pilot lever 86 is rotated by its own weight, a downward regulating end surface portion 136 is formed to which the downward rotation stopper 126 abuts. Further, the height of the stepped portion 135 from the extended portion 120 is formed to be lower than the downward rotation preventing portion 126.
Further, an elastic locking piece 137 having an inverted L-shaped cross section with a locking projection 137A formed at the tip is attached to the edge of the extending portion 120 that faces the mounting boss 123 vertically downward. It is erected so as to be elastically deformable radially outward with respect to the boss 123. This elastic locking piece 137 forms a predetermined gap (for example, a gap of about 0.3 mm) and opposes the convex portion 128 protruding from the outer peripheral surface of the shaft portion 121 of the pilot lever 86. At the same time, the locking protrusion 137A formed at the tip is erected so as to be slightly higher than the convex portion 128 (for example, about 0.2 mm higher).
As shown in FIGS. 9, 10, 12 to 14, an opening 138 penetrating vertically in the vertical direction is provided at a position facing the engaging claw 86 </ b> A of the pilot lever 86 of the outer rib 117. It has a predetermined width in the circumferential direction and is formed by cutting out a predetermined dimension from the edge of the plate portion 111 to the inside. As will be described later, the opening 138 enters the opening 138 and engages with the locking gear teeth 81A when the engaging claw 86A is pressed and rotated by the lock claw 53A of the sensor lever 53. It can be formed (see FIG. 18).
Accordingly, as shown in FIGS. 17 and 18, until the engaging claw 86 </ b> A of the pilot lever 86 faces the opening 138, the shaft 121 is fitted into the mounting boss 123, and abuts on the extension 120. By pushing, the locking protrusion 137A of the elastic locking piece 137 forms a predetermined gap (for example, a gap of about 0.2 mm) and faces the convex portion 128, so that the pilot lever 86 is attached to the mounting boss 123. Can be prevented from falling out.
The locking protrusion 137 </ b> A is opposed to the peripheral surface of the recess 127 formed in the shaft portion 121 by forming a predetermined gap (for example, a clearance of 0.2 mm) and the outer periphery of the shaft portion 121. Since a predetermined clearance 139 (for example, a clearance of about 0.1 mm) is formed between the surface and the load receiving surface 133 of the pilot lever support block 131, the pilot lever 86 can be smoothly moved up and down in the vertical direction. Rotate.
As shown in FIG. 17, when the pilot lever 86 is rotated downward in the vertical direction (downward in FIG. 17) due to its own weight, the downward detent portion 126 has the pilot lever support block. 131 abuts on the lower regulating end face portion 136, and the rotation angle to the lower side in the vertical direction (the lower direction in FIG. 17) is regulated. Further, in a normal state, a gap is formed between the receiving plate portion 122 of the pilot lever 86 and the lock claw 53A of the sensor lever 53.
As shown in FIG. 18, when the sensor lever 53 is turned upward in the vertical direction (upward in FIG. 18), and the pilot lever 86 is turned upward in the vertical direction by the lock claw 53A. The engaging claw portion 86A of the pilot lever 86 abuts on the locking gear 81 and engages with the locking gear tooth 81A. Further, when the locking gear 81 rotates in the webbing pull-out direction (in the direction of arrow 141) with the engaging claw portion 86A of the pilot lever 86 engaged with the locking gear tooth 81A (see FIG. 27). The load in the direction of the mounting boss 123 (in the direction of the arrow 142) is applied to the engaging claw portion 86A.
When the tip portion of the engaging claw 86A that is bent obliquely toward the locking gear 81 due to the load applied to the engaging claw 86A is elastically deformed toward the shaft 121 and further rotated. The upward rotation stop portion 125 of the pilot lever 86 is brought into contact with the upward restriction end surface portion 132 of the pilot lever support block 131. Further, when the mounting boss 123 is bent due to a load applied to the engaging claw portion 86 </ b> A, the outer peripheral surface of the shaft portion 121 contacts the load receiving surface 133 of the pilot lever support block 131.
Accordingly, the pressing load applied to the engaging claw 86 </ b> A can be supported by the pilot lever support block 131 through the upward rotation stopper 125 and the shaft 121. Thereby, even if the pilot lever 86 and the mounting boss 123 are made small, it is possible to prevent deformation and breakage of the upward detent portion 125, the shaft portion 121, and the mounting boss 123 that support the pressing load applied to the engaging claw portion 86A. .
In addition, as shown in FIGS. 6, 9, 10, 12, and 13, the flange portion 118 of the clutch 85 has a through hole 112 on the substantially opposite side to the through hole 112 of the guide block portion 119. A notch portion 145 is formed by notching to the outer rib portion 117 at a predetermined center angle (for example, the center angle is about 60 degrees) with respect to the center axis. In addition, between both ends in the circumferential direction with respect to the central axis of the through-hole 112 of the notch 145, a rib-like elastic rib 146 extends from one end to the other end more than the width of the flange 118. A narrow width is formed in an arc shape concentric with the central axis of the through hole 112.
In addition, the elastic rib 146 has a substantially U-shaped cross section that protrudes at a predetermined height (for example, a height of about 1.2 mm) outward in the radial direction from the outer diameter of the flange portion 118 at the center in the circumferential direction of the elastic rib 146. The formed clutch side protrusion 146A is provided. Further, the rib-shaped elastic rib 146 is configured such that the clutch-side protrusion 146A has a radius larger than the outer diameter of the flange 118 when the clutch-side protrusion 146A formed at the center in the circumferential direction is pressed inward in the radial direction. It is formed to be elastically deformable so that it can move inward.
Further, as shown in FIGS. 6, 9, and 10, the inner wall portion facing the flange portion 118 of the clutch 85 of the mechanism housing portion 87 of the mechanism cover 71 is concentric with the central axis 73 </ b> A of the through hole 73. It is formed and faces the flange portion 118 by forming a predetermined gap (for example, a gap of about 1.5 mm).
Further, on the inner wall portion of the mechanism accommodating portion 87, the clutch 85 is rotated in the webbing pull-out direction as will be described later at a portion facing the elastic rib 146 of the clutch 85, and the pawl 23 is the ratchet gear portion of the ratchet gear 35. When engaged with 35A, a rib-like fixed-side protrusion 148 is erected along the direction of the central axis 73A at a position where the clutch-side protrusion 146A can get over (see FIG. 22). The fixed protrusion 148 is formed in a substantially semicircular cross section that protrudes from the inner wall portion of the mechanism housing portion 87 to the inside in the radial direction with a predetermined height (for example, a height of about 1.2 mm).
The notch 145 of the clutch 85 is not limited to the portion of the flange portion 118 that is substantially opposite to the through hole 112 of the guide block portion 119, but is the flange that is substantially opposite to the through hole 112 of the extension portion 120. The elastic rib 146 may be formed by providing the portion 118 or the flange portion 118 on the substantially opposite side of the through hole 112 of the pilot lever support block 131.
Further, when the pawl 23 is engaged with the ratchet gear portion 35 </ b> A of the ratchet gear 35, the fixed-side protruding portion 148 formed on the inner wall portion of the mechanism housing portion 87 is engaged with the portion of the inner wall portion facing each elastic rib 146. In addition, the clutch side protrusion 146A may be provided at a position where it can be overcome.
Next, the operation of the lock mechanism 10 will be described with reference to FIGS. In each figure, the pulling direction of the webbing 3 is the arrow 151 direction, and the pulling direction of the webbing 3 is the arrow 152 direction. In each figure, the counterclockwise rotation direction is the rotation direction (webbing pull-out direction) of the winding drum unit 6 when the webbing 3 is pulled out. Further, for the explanation of the operation of the lock mechanism 10, a part of the drawing is cut out and displayed as necessary.
Here, the lock mechanism 10 is a “webbing sensitive lock mechanism” that operates when the webbing 3 is suddenly pulled out, and a “vehicle body sensitive type” that operates in response to acceleration caused by a vehicle shake or tilt. It operates as two types of lock mechanisms, “lock mechanism”. The operation of the pawl 23 is common to both the “webbing sensitive lock mechanism” and the “vehicle body sensitive lock mechanism”. For this reason, in FIG. 19 thru | or FIG. 37, about the part which shows the relationship between the pawl 23 and the ratchet gear 35, the part is displayed as a notch state.
[Description of webbing-sensitive locking mechanism]
First, the operation of the “webbing sensitive lock mechanism” will be described with reference to FIGS. 19 to 25 are explanatory diagrams for explaining the operation of the “webbing sensitive lock mechanism”. In the “webbing sensitive lock mechanism”, in addition to the portion indicating the relationship between the pawl 23 and the ratchet gear 35, the portion indicating the relationship between the lock arm 82 and the clutch gear 108 and the portion indicating the movement of the sensor spring 83 are cut off. Missing shows.
First, the locking operation of the “webbing sensitive locking mechanism” will be described with reference to FIGS. 19 and 20, since the lock arm 82 is rotatably supported by the support boss 101 of the locking gear 81, the pull-out acceleration of the webbing 3 is a predetermined acceleration (for example, about 2.0G). If 1G≈9.8 m / s2 is exceeded, a delay in inertia occurs in the lock arm 82 with respect to the rotation of the locking gear 81 in the webbing pull-out direction (the direction of the arrow 153). .
For this reason, the lock arm 82 that has been in contact with the stopper 114 maintains its initial position against the urging force of the sensor spring 83, so that the lock gear 82 is clockwise with respect to the locking gear 81 around the support boss 101 (arrow 155 Direction), and is rotated to the vicinity of the detent 115. Therefore, the engagement claw 109 of the lock arm 82 is rotated radially outward with respect to the rotation shaft of the locking gear 81 and engaged with the clutch gear 108 of the clutch 85.
As shown in FIGS. 20 and 21, when the webbing 3 is continuously pulled out beyond a predetermined acceleration, the locking gear 81 is further rotated in the webbing withdrawal direction (in the direction of the arrow 153). The engagement claw 109 of the lock arm 82 is rotated in the webbing pull-out direction (in the direction of the arrow 153) while being engaged with the clutch gear 108.
Accordingly, since the clutch gear 108 is rotated in the webbing pull-out direction (in the direction of arrow 156) by the lock arm 82, the clutch 85 is urged to rotate away from the ratchet gear 35 by the torsion coil spring 26. Against the urging force of the pawl 23 by the guide pin 42, it rotates in the webbing pull-out direction (in the direction of arrow 156) around the axis of the rib 95 of the locking gear 81, that is, around the axis of the rotating shaft 93. Moved.
As a result, the guide pin 42 of the pawl 23 is guided by the guide hole 116 of the clutch 85 as the clutch 85 rotates in the webbing pull-out direction (in the direction of the arrow 156). It is rotated toward the ratchet gear 35 against the biasing force of the torsion coil spring 26 (in the direction of arrow 157). Further, the clutch-side protrusion 146A of the elastic rib 146 provided on the flange portion 118 on the substantially opposite side in the diameter direction with respect to the guide hole 116 of the clutch 85 so as to be elastically deformable radially inward is also rotated by the clutch 85. Along with this, the mechanism cover 71 is rotated toward the fixed projection 148 provided on the inner peripheral wall of the mechanism accommodating portion 87 of the mechanism cover 71.
Then, as shown in FIG. 22, when the webbing 3 is further pulled out beyond the predetermined acceleration, the clutch 85 is urged to rotate away from the ratchet gear 35 by the torsion coil spring 26. The webbing is further rotated in the webbing pull-out direction (in the direction of the arrow 156) against the urging force of the 23 guide pins 42. For this reason, the guide pin 42 of the pawl 23 is further guided by the guide hole 116 of the clutch 85, and the pawl 23 is engaged with the ratchet gear 35 against the urging force of the torsion coil spring 26. Thereby, the rotation of the winding drum unit 6 is locked and the drawer of the webbing 3 is locked.
In addition, the elastic rib 146 of the clutch 85 further contacts the fixed-side protrusion 148 because the clutch-side protrusion 146A is further rotated toward the fixed-side protrusion 148 provided on the inner peripheral wall of the mechanism housing portion 87. It is pressed in contact and elastically deformed inward in the radial direction, and smoothly gets over the fixed-side protrusion 148. In the clutch 85, the engaging teeth 23A and 23B of the pawl 23 come into contact with the ratchet gear portion 35A of the ratchet gear 35 and the pawl 23 stops rotating. At the position where 146A gets over the fixed-side protrusion 148, the rotation in the webbing pull-out direction (the direction of the arrow 156) is stopped.
In addition, the clutch-side protrusion 146A of the elastic rib 146 provided so as to protrude radially outward from the outer peripheral portion of the clutch 85 is elastically deformed radially inward and is erected on the inner peripheral wall of the mechanism housing portion 87. The fixed-side protruding portion 148 is overcome and positioned in contact with or close to the side surface of the fixed-side protruding portion 148 on the webbing pull-out direction side.
[Unlock operation]
Next, the unlocking operation of the “webbing sensitive lock mechanism” will be described with reference to FIGS. As shown in FIG. 23, when the rotation of the winding drum unit 6 is locked and the drawer of the webbing 3 is locked, the pulling force applied to the webbing 3 is loosened and the webbing 3 is slightly wound. (For example, about 5 mm in the direction of arrow 152), the winding drum unit 6 is slightly rotated in the webbing winding direction (in the direction of arrow 158) by the urging force of the winding spring unit 8.
As a result, the locking gear 81 is coupled to the ratchet gear 35 so as not to rotate relative to the ratchet gear 35. Therefore, the locking gear 81 is rotated together with the ratchet gear 35 in the webbing winding direction (in the direction of the arrow 159). . On the other hand, the clutch 85 abuts on the elastic rib 146 with the clutch-side protrusion 146A getting over the fixed-side protrusion 148, and therefore the rotation in the webbing take-up direction (the direction of the arrow 159) is the locking gear. Relatively late with respect to 81 rotation.
Therefore, as shown in FIG. 23, the clutch-side protrusion 146A provided so as to protrude from the elastic rib 146 integrally formed on the outer peripheral portion radially outward with respect to the rotational axis of the clutch 85, and the side wall of the housing 11 The mechanism cover 71 fixed to the portion 12 is erected radially inward on the inner peripheral wall of the mechanism housing portion 87 and protrudes so as to come into contact with the clutch side protrusion 146A when the clutch 85 rotates in the webbing pull-out direction. The rotation-side imparting mechanism 149 that delays the rotation of the clutch 85 in the webbing take-up direction relative to the rotation of the locking gear 81 can be configured by the fixed-side protrusion 148 to be performed.
Therefore, the locking gear 81 rotates in the webbing take-up direction relatively ahead of the rotation of the clutch 85 in the webbing take-up direction, and the engagement side corner of the engagement claw 109 of the lock arm 82 and the clutch gear A gap that allows the lock arm 82 to rotate in the rotational direction in which the lock arm 82 is disengaged from the clutch gear 108 is generated. In addition, a gap is generated between the ratchet gear portion 35 </ b> A of the ratchet gear 35 and the engaging teeth 23 </ b> A and 23 </ b> B of the pawl 23 so that the pawl 23 can rotate in the turning direction to release the engagement with the ratchet gear 35. .
Then, as shown in FIG. 24, the lock arm 82 can be rotated in a direction to release the engagement with the clutch gear 108, and therefore the counter-clockwise direction around the support boss 101 is applied by the urging force of the sensor spring 83. (In the direction of arrow 161). Then, the lock arm 82 is disengaged from the clutch gear 108 and returns to the initial position where it comes into contact with the stopper 114.
Next, as shown in FIGS. 24 and 25, the pawl 23 can be rotated in the rotational direction for releasing the engagement with the ratchet gear 35, and therefore the direction (arrow) away from the ratchet gear 35 by the torsion coil spring 26. 162 direction), and the engagement with the ratchet gear 35 is released. At the same time, the guide pin 42 of the pawl 23 moves in the direction opposite to that during the locking operation with the rotation of the pawl 23 due to the biasing force of the torsion coil spring 26. It is urged to rotate (in the direction of arrow 163).
Thereby, the elastic rib 146 of the clutch 85 is pressed while the clutch side protrusion 146A abuts against the fixed side protrusion 148 erected on the inner peripheral wall of the mechanism accommodating portion 87, and elastically deforms radially inward. The fixed side protrusion 148 is smoothly overcome. Thereafter, the clutch 85 rotates in the webbing take-up direction (in the direction of the arrow 163) as the pawl 23 is rotated by the biasing force of the torsion coil spring 26, and the guide pin 42 is the most ratchet gear in the guide hole 116. The reference rotational posture returns to the normal state where it abuts on the end edge portion (the lower end edge portion of the guide hole 116 in FIG. 25) located away from 35.
Further, since the engagement between the engaging teeth 23A and 23B of the pawl 23 and the ratchet gear 35 is released and the pawl 23 is separated from the ratchet gear 35, the locked state of the winding drum unit 6 by the pawl 23 is released. The webbing 3 can be pulled out. Therefore, the rotation lock of the winding drum unit 6 can be released with a slight winding amount of the webbing 3.
[Explanation of body-sensitive locking mechanism]
Next, the operation of the “vehicle body sensitive locking mechanism” will be described with reference to FIGS. 26 to 32 are explanatory diagrams for explaining the operation of the “vehicle body sensitive locking mechanism”. FIGS. 33 to 37 are explanatory diagrams for explaining the operation when the synchronization shift of the pawl 23 of the “vehicle body sensitive locking mechanism” occurs. In the “body-sensitive locking mechanism”, in addition to the portion indicating the relationship between the pawl 23 and the ratchet gear 35, the portion indicating the relationship between the pilot lever 86 and the locking gear 81, the sensor holder 51 of the vehicle acceleration sensor 28, and the sensor A portion of the lever 53 is cut away.
[Normal lock operation]
First, the normal locking operation of the “body-sensitive locking mechanism” will be described with reference to FIGS. As shown in FIGS. 26 and 27, since the spherical inertia mass body 52 of the vehicle acceleration sensor 28 is placed on the mortar-shaped bottom surface portion of the sensor holder 51, the acceleration due to the shaking or tilting of the vehicle body is caused. When a predetermined acceleration (for example, about 2.0 G) is exceeded, the bottom surface of the sensor holder 51 is moved to rotate the sensor lever 53 upward in the vertical direction.
For this reason, the lock claw 53A of the sensor lever 53 abuts on the receiving plate portion 122 of the pilot lever 86 that is rotatably attached to the attachment boss 123 that is erected on the extension portion 120 of the clutch 85, and the pilot The lever 86 is rotated upward in the vertical direction. Accordingly, the pilot lever 86 is rotated clockwise (in the direction of the arrow 164) around the axis of the mounting boss 123, and the engaging claw portion 86A of the pilot lever 86 is connected to the opening 138 of the clutch 85 (FIG. 10). (See) and engages with the locking gear teeth 81 </ b> A formed on the outer peripheral portion of the locking gear 81. At this time, a predetermined gap (for example, a gap of about 0.1 mm) is formed between the upward detent portion 125 and the upward regulating end surface portion 132 of the pilot lever support block 131.
27 and 28, when the webbing 3 is pulled out with the pilot lever 86 engaged with the locking gear teeth 81A of the locking gear 81, the locking gear 81 is pulled in the webbing pull-out direction ( In the direction of arrow 165). The rotation of the locking gear 81 in the webbing pull-out direction is transmitted to the clutch 85 via the pilot lever 86, the mounting boss 123, and the pilot lever support block 131.
Therefore, as the locking gear 81 rotates in the webbing pull-out direction, the clutch 85 is urged by the guide pin 42 of the pawl 23 that is urged to rotate away from the ratchet gear 35 by the torsion coil spring 26. Against this, it is rotated in the webbing pull-out direction (in the direction of arrow 166) around the axis of the rib 95 of the locking gear 81, that is, around the axis of the rotating shaft 93.
As a result, the guide pin 42 of the pawl 23 is guided to the guide hole 116 of the clutch 85 as the clutch 85 rotates in the webbing pull-out direction (in the direction of the arrow 166). It is rotated toward the ratchet gear 35 (in the direction of arrow 167). Further, the clutch-side protrusion 146A of the elastic rib 146 provided on the flange portion 118 on the substantially opposite side in the diameter direction with respect to the guide hole 116 of the clutch 85 so as to be elastically deformable radially inward is also rotated by the clutch 85. Along with this, the mechanism cover 71 is rotated toward the fixed projection 148 provided on the inner peripheral wall of the mechanism accommodating portion 87 of the mechanism cover 71.
As shown in FIG. 29, when the webbing 3 is further pulled out, the clutch 85 is urged to rotate away from the ratchet gear 35 by the torsion coil spring 26. The webbing is further rotated in the webbing pull-out direction (in the direction of arrow 166) against the urging force of 42. For this reason, the guide pin 42 of the pawl 23 is guided by the guide hole 116 of the clutch 85, and the engagement teeth 23 </ b> A and 23 </ b> B of the pawl 23 are engaged with the ratchet gear portion 35 </ b> A of the ratchet gear 35. Thereby, the rotation of the winding drum unit 6 is locked and the drawer of the webbing 3 is locked.
In addition, the elastic rib 146 of the clutch 85 further contacts the fixed-side protrusion 148 because the clutch-side protrusion 146A is further rotated toward the fixed-side protrusion 148 provided on the inner peripheral wall of the mechanism housing portion 87. It is pressed in contact and elastically deformed inward in the radial direction, and smoothly gets over the fixed-side protrusion 148. In the clutch 85, the engaging teeth 23A and 23B of the pawl 23 come into contact with the ratchet gear portion 35A of the ratchet gear 35 and the pawl 23 stops rotating. At the position where 146A gets over the fixed-side protrusion 148, the rotation in the webbing pull-out direction (the direction of arrow 166) is stopped.
Next, the unlocking operation of the “vehicle body sensitive locking mechanism” will be described with reference to FIGS. 30 to 32. As shown in FIG. 30, when the rotation of the winding drum unit 6 is locked and the drawer of the webbing 3 is locked, the pulling force applied to the webbing 3 is loosened and the webbing 3 is slightly wound. (For example, about 5 mm in the direction of arrow 152), the winding drum unit 6 is slightly rotated in the webbing winding direction (in the direction of arrow 168) by the urging force of the winding spring unit 8. At this time, if the acceleration of the vehicle is equal to or less than a predetermined value, the inertial mass body 52 of the vehicle acceleration sensor 28 returns to the normal time when it is located at the center of the mortar-shaped bottom surface of the sensor holder 51.
As a result, the locking gear 81 is coupled to the ratchet gear 35 so as not to rotate relative to the ratchet gear 35 by the convex portions 96, so that the locking gear 81 is integrated with the ratchet gear 35 in the webbing take-up direction (the direction of the arrow 169). Slightly rotated. On the other hand, the clutch 85 comes into contact with the elastic rib 146 with the clutch-side protrusion 146A getting over the fixed-side protrusion 148, so that the rotation in the webbing take-up direction (the direction of the arrow 169) is the locking gear. Relatively late with respect to 81 rotation.
Therefore, as shown in FIG. 30, the clutch-side protrusion 146 </ b> A provided so as to protrude from the elastic rib 146 integrally formed on the outer peripheral portion radially outward with respect to the rotation axis of the clutch 85, and the side wall of the housing 11. The mechanism cover 71 fixed to the portion 12 is erected radially inward on the inner peripheral wall of the mechanism housing portion 87 and protrudes so as to come into contact with the clutch side protrusion 146A when the clutch 85 rotates in the webbing pull-out direction. The rotation-side imparting mechanism 149 that delays the rotation of the clutch 85 in the webbing take-up direction relative to the rotation of the locking gear 81 can be configured by the fixed-side protrusion 148 to be performed.
Therefore, the locking gear 81 rotates in the webbing winding direction relatively earlier than the rotation of the clutch 85 in the webbing winding direction, and the tip of the engaging claw portion 86A of the pilot lever 86 and the locking gear teeth 81A. Between the two, a clearance is generated that allows the pilot lever 86 to rotate in the turning direction to release the engagement with the locking gear teeth 81A. In addition, a gap is generated between the ratchet gear portion 35 </ b> A of the ratchet gear 35 and the engaging teeth 23 </ b> A and 23 </ b> B of the pawl 23 so that the pawl 23 can rotate in the turning direction to release the engagement with the ratchet gear 35. .
As shown in FIG. 31, the pilot lever 86 can be rotated in a direction to release the engagement between the engagement claw portion 86 </ b> A and the locking gear 81, and therefore is vertically downward (in the direction of the arrow 171) by its own weight. )). Then, the pilot lever 86 is disengaged from the locking gear 81, and at the initial position where the downward rotation preventing portion 126 of the pilot lever 86 abuts the downward regulating end surface portion 136 of the pilot lever support block 131. Return to state.
Subsequently, as shown in FIGS. 31 and 32, the pawl 23 can rotate in the rotational direction for releasing the engagement with the ratchet gear 35, and therefore, the direction (arrow) away from the ratchet gear 35 by the torsion coil spring 26. 172 direction), and the engagement with the ratchet gear 35 is released. At the same time, the guide pin 42 of the pawl 23 moves in the direction opposite to that during the locking operation with the rotation of the pawl 23 due to the biasing force of the torsion coil spring 26. It is urged to rotate (in the direction of arrow 173).
Thereby, the elastic rib 146 of the clutch 85 is pressed while the clutch side protrusion 146A abuts against the fixed side protrusion 148 erected on the inner peripheral wall of the mechanism accommodating portion 87, and elastically deforms radially inward. The fixed side protrusion 148 is smoothly overcome. Thereafter, the clutch 85 rotates in the webbing take-up direction (in the direction of the arrow 173) as the pawl 23 is rotated by the urging force of the torsion coil spring 26, and the guide pin 42 is the most ratchet gear in the guide hole 116. It returns to the reference rotation posture in the normal state in contact with the end edge portion (the lower end edge portion of the guide hole 116 in FIG. 32) located away from 35.
Further, the pilot lever 86 is rotated to the vehicle acceleration sensor 28 side by its own weight, and the receiving plate portion 122 returns to the normal state in the vicinity of the lock claw 53A of the sensor lever 53. Then, the engagement between the engaging teeth 23A, 23B of the pawl 23 and the ratchet gear 35 is released, and the pawl 23 is separated from the ratchet gear 35, so that the winding drum unit 6 is unlocked by the pawl 23. The webbing 3 can be pulled out. Therefore, the rotation lock of the winding drum unit 6 can be released with a slight winding amount of the webbing 3.
[Locking action when a synchronization error occurs in the pawl]
Here, the locking operation when the synchronization shift of the pawl 23 of the “body-sensitive locking mechanism” occurs will be described with reference to FIGS. 28, 33 to 37. As shown in FIGS. 28 and 33, when the webbing 3 is pulled out with the engaging claw portion 86A of the pilot lever 86 engaged with the locking gear teeth 81A of the locking gear 81, the locking gear 81 is It is rotated in the webbing pull-out direction (the direction of the arrow 165). Further, as the locking gear 81 rotates in the webbing pull-out direction, the clutch 85 is rotated in the webbing pull-out direction (in the direction of the arrow 166), and the pawl 23 is rotated toward the ratchet gear 35 ( Arrow 167 direction).
The elastic rib 146 of the clutch 85 abuts against the fixed-side protrusion 148 because the clutch-side protrusion 146A is rotated toward the fixed-side protrusion 148 provided on the inner peripheral wall of the mechanism housing portion 87. And is elastically deformed radially inward, and smoothly gets over the fixed-side protrusion 148.
Subsequently, as shown in FIGS. 33 and 34, in the clutch 85, the engaging teeth 23A and 23B of the pawl 23 come into contact with the ratchet gear portion 35A of the ratchet gear 35, and the rotation of the pawl 23 is stopped. Therefore, the rotation in the webbing pull-out direction (the direction of the arrow 166) is locked.
On the other hand, as shown in FIG. 33, there is still a slight gap between each engaging tooth 23A, 23B of the pawl 23 and each tooth of the ratchet gear portion 35A engaged with each engaging tooth 23A, 23B. Therefore, when the webbing 3 is continuously pulled out, the ratchet gear 35 rotates in the webbing pull-out direction (in the direction of the arrow 175) until the lock is completed. At the same time, the locking gear 81 rotates integrally with the ratchet gear 35 and presses the engaging claw 86A of the pilot lever 86 engaged with the locking gear teeth 81A.
For this reason, the pilot lever 86 is further rotated clockwise around the axis of the mounting boss 123, and the upward detent portion 125 is brought into contact with the upward regulating end surface portion 132 of the pilot lever support block 131, The upward rotation in the vertical direction is restricted. At the same time, the mounting boss 123 is bent toward the pilot lever support block 131 and the shaft 121 of the pilot lever 86 is brought into contact with the load receiving surface 133 of the pilot lever support block 131.
Then, as shown in FIGS. 34 to 36, the ratchet gear 35 is moved until the end of each engagement tooth 23A, 23B of the pawl 23 comes into contact with each tooth of the ratchet gear portion 35A until the locking operation is completed. It is further rotated in the webbing pull-out direction (the direction of the arrow 175). At the same time, the engaging claw portion 86A of the pilot lever 86 and the receiving plate portion 122 connected via the connecting plate portion 124 are pressed toward the shaft portion 121 by the locking gear teeth 81A. It is elastically deformed to the 121 side and is bent into a substantially U shape protruding outward in the radial direction. At this time, the distal end portion of the engaging claw portion 86A formed in a substantially L shape when viewed in the rotational axis direction is elastically deformed toward the shaft portion 121 side mainly at a portion bent obliquely toward the locking gear 81 side.
36, the opening 138 into which the pilot lever 86 of the clutch 85 enters has an engaging claw 86A and a receiving plate 122 connected via a connecting plate 124 as a shaft portion. It is formed in a size that does not contact even if it is elastically deformed to the 121 side and is bent into a substantially U shape protruding outward in the radial direction. Further, the distal end portion of the engaging claw portion 86A of the pilot lever 86 is elastically deformed and bent outwardly in the radial direction with respect to the locking gear teeth 81A (arrow 176) as it bends in a substantially U shape protruding outward in the radial direction. Direction.) It will shift.
Accordingly, as shown in FIGS. 35 to 37, the elastic deformation of the engaging claw portion 86A of the pilot lever 86 and the receiving plate portion 122 connected via the connecting plate portion 124 toward the shaft portion 121 is caused by When the engaging claw 86A reaches an elastic deformation amount that disengages from the locking gear teeth 81A, the tip of the engaging claw 86A disengages radially outward from the locking gear teeth 81A.
As shown in FIG. 37, when the pilot lever 86 is disengaged from the locking gear teeth 81A, the elastic deformation of the receiving claw portion 122 connected via the engaging claw portion 86A and the connecting plate portion 124 is released. To return to the normal shape. Further, since the engagement between the engagement claw portion 86A and the locking gear 81 is released, the pilot lever 86 is rotated downward in the vertical direction (in the direction of the arrow 177) by its own weight, and the pilot lever 86 is moved downward. The anti-rotation portion 126 returns to the initial position where the pilot lever support block 131 is in contact with the downward regulating end surface portion 136.
Further, the distal ends of the engaging teeth 23A and 23B of the pawl 23 come into contact with the teeth of the ratchet gear portion 35A, and the locking operation is completed. Thereby, the rotation of the winding drum unit 6 is locked and the drawer of the webbing 3 is locked.
It should be noted that the engaging claw portion 86A is elastically deformed toward the shaft 121 side of the engaging claw portion 86A of the pilot lever 86 and the receiving plate portion 122 connected via the connecting plate portion 124. Even when the amount of elastic deformation does not deviate from the clutch, the clutch-side protrusion 146A of the elastic rib 146 provided so as to protrude radially outward from the outer periphery of the clutch 85 is elastically deformed radially inward, It overlies the fixed-side protrusion 148 erected on the inner peripheral wall of the mechanism accommodating portion 87 and is in contact with or close to the side surface of the fixed-side protrusion 148 on the webbing pull-out direction side.
Therefore, during the unlocking operation of the “body-sensitive locking mechanism”, the rotation difference applying mechanism 149 releases the engagement between the pilot lever 86 and the locking gear 81 with a slight winding amount of the webbing 3 and the winding. The rotation lock of the take-up drum unit 6 can be released.
[Schematic configuration of winding drum unit]
Next, a schematic configuration of the winding drum unit 6 will be described with reference to FIGS. 2, 3, 38 to 43. FIG. 38 is a cross-sectional view including the axis of the winding drum unit 6. FIG. 39 is an exploded perspective view of the winding drum unit 6. FIG. 40 is a front view of the winding drum 181 as viewed from the side where the ratchet gear 35 is attached. FIG. 41 is a perspective view of the ratchet gear 35. FIG. 42 is an inner front view of the ratchet gear 35. 43 is a cross-sectional view taken along arrow X1-X1 in FIG.
As shown in FIGS. 38 and 39, the winding drum unit 6 includes a winding drum 181, a torsion bar 182, a wire 183, and a ratchet gear 35.
As shown in FIGS. 2, 3, 38 and 39, the take-up drum 181 is formed by aluminum die casting, zinc die casting, or the like, and is formed in a substantially cylindrical shape with the end surface portion on the pretensioner unit 7 side closed. Has been. Further, an end edge portion on the pretensioner unit 7 side in the axial direction of the winding drum 181 extends in the radial direction from the outer peripheral portion, and further in a substantially right-angled outward direction (the left side direction in FIG. 38). An extended flange portion 185 is formed. Further, an internal gear to which each clutch pawl 232 (see FIG. 44) is engaged and the rotation of the pinion gear 215 (see FIG. 44) is transmitted to the inner peripheral surface of the flange portion 185 at the time of a vehicle collision as will be described later. 186 is formed.
Further, a cylindrical boss 187 is erected at the center position of the end surface portion of the winding drum 181 on the pretensioner unit 7 side. The boss 187 is fitted into a bearing 235 (see FIG. 44) formed of a synthetic resin material such as polyacetal described later, and the base end portion of the boss 187 is brought into contact with the bearing 235. Thereby, the one end side of the winding drum unit 6 is rotatably supported by the boss | hub part 215D (refer FIG. 44) of the pinion gear 215 which comprises the pretensioner unit 7 via the bearing 235. FIG. Accordingly, the take-up drum unit 6 is rotatably supported by the pretensioner unit 7 and the lock unit 9 while preventing backlash in the rotation axis direction.
Further, a shaft hole 181A having a draft angle formed so as to be gradually reduced along the central axis is formed inside the winding drum 181. Further, as shown in FIGS. 38 and 40, five protrusions 188A to 188E having a substantially trapezoidal cross section are formed at regular intervals in the circumferential direction on the inner peripheral surface of the end portion on the flange portion 185 side in the shaft hole 181A. And projecting in a rib shape inward in the radial direction. The torsion bar 182 is formed of a shaft portion 182C formed of a steel material or the like and having a circular cross section, and splines 182A and 182B formed at both ends of the shaft portion 182C.
Further, the projecting portions 188A to 188E are provided so as to be fitted between the projecting portions of the spline 182A formed at one end portion of the torsion bar 182 formed of a steel material or the like. Accordingly, as shown in FIGS. 38 and 39, the torsion bar 182 is inserted by inserting the spline 182A side of the torsion bar 182 into the shaft hole 181A of the take-up drum 181 and press-fitting between the protrusions 188A to 188E. It is press-fitted and fixed in the take-up drum 181 so as not to be relatively rotatable.
Further, as shown in FIGS. 38 to 40, the end edge of the winding drum 181 on the lock unit 9 side in the axial direction is extended in the radial direction from the outer peripheral surface slightly inward in the axial direction from the end edge. A flange portion 189 having a substantially circular shape when viewed from the front is formed. In addition, a cylindrical step portion 191 having a slightly smaller outer diameter is formed on the outer side in the axial direction from the flange portion 189. The step 191 is provided so as to surround the spline 182B on the other end side of the torsion bar 182 press-fitted into the shaft hole 181A with a predetermined gap.
In addition, a bent portion 183A at one end of a wire 183 having a circular cross section made of a metal material such as stainless steel is provided on the outer peripheral portion of a step portion 191 having a substantially circular shape in front view formed on the outer surface in the axial direction of the flange portion 189. A holding-side bending path 192 in which is inserted and held is integrally formed.
As shown in FIGS. 39 and 40, the holding-side bending path 192 includes a projecting portion 193 formed in a substantially trapezoidal shape that protrudes from the axially outer side surface of the flange portion 189 and faces inward in the radial direction of the front view, and a stepped portion. A concave portion 194 facing the convex portion 193 on the outer periphery of 191, and an outer peripheral surface of the step portion 191 that is a little away from the end portion of the concave portion 194 on the counterclockwise direction in the front view (on the counterclockwise side in FIG. 40) The groove portion 195 is formed in a diagonally inward direction inclined in the counterclockwise direction when viewed from the front, and the outer peripheral surface between the recess portion 194 and the groove portion 195 of the step portion 191.
Further, as shown in FIGS. 39 and 40, on the opposing surface on the groove 195 side (in FIG. 40, the counterclockwise direction side) inclined obliquely with respect to the radial direction of the convex portion 193 and the concave portion 194, A pair of opposing ribs 196 is provided along the depth direction of the holding-side bending path 192. In addition, on the opposite surface (the clockwise side in FIG. 40) of the groove 195 inclined obliquely with respect to the radial direction of the convex portion 193 and the concave portion 194, the radially outer wire 183 is provided. Two pairs of opposing ribs 197 and 198 are provided along the depth direction of the holding-side bent path 192, respectively, at the outlet side end and the inner side in the radial direction.
A pair of opposing ribs 199 are provided on the opposing surface of the groove portion 195 along the depth direction of the holding-side bending path 192. As shown in FIGS. 40 and 43, the opposing ribs 196 to 199 are disposed on a plane orthogonal to the axis of the wire 183 with the wire 183 inserted into the holding-side bending path 192 interposed therebetween. The holding-side bent path 192 is erected along the depth direction so as to face each other. Further, the distance between the opposing ribs 196 to 199 is formed to be smaller than the outer diameter of the wire 183. The height of each rib 196 to 199 from the bottom surface portion of the holding-side bending path 192 is formed to be equal to or higher than the outer diameter of the wire 183.
As shown in FIGS. 39 and 43, the bent portion 183A at one end of the wire 183 is fitted into the holding-side bent path 192 while being crushed each of the ribs 196 to 199, and is fixedly held. In addition, a substantially inverted U-shaped bent portion 183B formed continuously from the bent portion 183A of the wire 183 is formed to protrude outward from the outer periphery of the flange portion 189. A bent portion 183C formed continuously with the bent portion 183B of the wire 183 is formed in an arc shape along the outer peripheral surface of the step portion 191.
Therefore, the bent portion 183A of the wire 183 is sandwiched between the two sets of ribs 197 and 198 disposed along the axial direction of the wire 183 at the outlet side end portion of the holding-side bent path 192. The inclination of the bent part 183B continuous from the outlet side of the holding-side bent path 192 can be made substantially constant.
Further, as shown in FIGS. 38, 39, 41, and 42, the ratchet gear 35 is formed by aluminum die casting, zinc die casting, or the like, and has a substantially ring-shaped axial cross section, and a ratchet gear portion 35A is formed on the outer peripheral portion. A cylindrical fixed boss 201 is erected at the inner center position. A spline groove 201 </ b> A into which a spline 182 </ b> B formed on the other end side of the torsion bar 182 is press-fitted is formed on the inner peripheral surface of the fixed boss 201. Further, the inner peripheral portion of the ratchet gear portion 35A is formed to have an inner diameter into which the step portion 191 of the winding drum 181 can be inserted.
The maximum outer diameter of the spline 182B formed on the other end of the torsion bar 182 is slightly smaller than the outer diameter of the spline 182A formed on one end of the torsion bar 182.
The ratchet gear 35 has a ring shape in a front view from the end surface portion of the ratchet gear portion 35A on the winding drum 181 side to the outer side in the radial direction from the outer diameter of the flange portion 189 of the winding drum 181. Further, a flange portion 202 is formed that extends from the outer peripheral portion of a predetermined center angle (for example, the center angle is about 60 degrees) to the radially outer side in a substantially trapezoidal shape in which the front end side in the front view is narrow. . Further, the outer diameter of the flange portion 202 is formed to be approximately the same as the outer diameter of the flange portion 185 of the winding drum 181.
Further, the inner side surface of the substantially trapezoidal trapezoidal trapezoidal portion 202A that extends outward in the radial direction of the flange portion 202 and narrows in the front view is on the winding drum 181 side from the trapezoidal portion 202A to the outer side in the rotation axis direction. A protruding portion 203 having a substantially chevron shape in front view, into which a bent portion 183B having a substantially inverted U-shape in front view of the wire 183 is fitted, is formed at a substantially central portion.
Further, the inner surface of the flange portion 202 on the winding drum 181 side is erected with an inner diameter slightly larger than the outer diameter of the flange portion 189 of the winding drum 181 and along the outer peripheral portion of the trapezoidal portion 202A. A flange portion 205 having a generally oval shape in front view is formed. Further, the inner peripheral portion of the flange portion 205 and the outer peripheral portion of the convex portion 203 form a deformation imparting bending path 206 having a generally inverted U shape in front view through which the wire 183 is slid and guided. 43). In addition, on the outer peripheral portion of the flange portion 205, window portions 207 that are notched in the circumferential direction are formed at two locations so that the attached wire 183 is visible.
Further, as shown in FIGS. 41 to 43, when the deformation-applying bending path 206 rotates relative to the holding-side bending path 192 as will be described later (see FIG. 48), the deformation-applying bending path from which the wire 183 is pulled out. The ribs 208 and 209 of the ridges are erected along the depth direction of the deformation imparting bending path 206 at the opposite end portions of the 206 at the side surfaces facing each other.
One rib 208 has a side surface opposite to a rotation direction side (a counterclockwise side in FIG. 43) in which the holding-side bending path 192 rotates relative to the deformation-applying bending path 206 when the wire is pulled out. It is erected at the end of the drawer side. Further, the other rib 209 is on the side facing the rib 208 across the wire 183 of the deformation imparting bending path 206, and is on the far side in the axial direction of the wire 183 from the rib 208 (in FIG. 42, radially outside). ).
Further, the distance between the ribs 208 and 209 in the direction perpendicular to the axis of the wire 183 is formed to be substantially the same as the outer diameter of the wire 183. Therefore, when the wire 183 passes through the deformation-applying bending path 206, it is bent and deformed at least at the apex of the convex portion 203 having a substantially mountain shape when viewed from the front, and a drawing resistance is generated. The distance between the ribs 208 and 209 in the direction orthogonal to the axis of the wire 183 may be formed to be slightly smaller than the outer diameter of the wire 183.
Here, attachment of the wire 183 to the ratchet gear 35 and the take-up drum 181 will be described with reference to FIGS. 38, 39, and 43.
As shown in FIGS. 39 and 43, first, a bent portion 183A bent in a substantially S-shape on one end side of the wire 183 is bent into a holding-side bent formed on the flange portion 189 and the step portion 191 of the winding drum 181. The ribs 196 to 199 are inserted into the path 192 while being crushed. Further, a substantially inverted U-shaped bent portion 183B formed continuously from the bent portion 183A of the wire 183 is projected outward from the outer periphery of the flange portion 189.
Further, an arc-shaped bent portion 183 </ b> C formed continuously with the bent portion 183 </ b> B of the wire 183 is disposed along the outer peripheral surface of the step portion 191. As a result, the bent portion 183A on one end side of the wire 183 is fitted and fixedly held in the holding-side bent path 192 formed in the flange portion 189 and the step portion 191 of the winding drum 181 and the wire 183 is bent. The part 183C is arranged in a state of facing the flange part 189.
Subsequently, for attaching the ratchet gear 35 to the winding drum 181, first, a bent portion 183 </ b> B having a substantially inverted U shape in front view of the wire 183 protruding outward from the outer periphery of the flange portion 189 of the winding drum 181 is provided. The ribs 208 and 209 are inserted into the deformation imparting bending path 206 formed in the outer peripheral portion of the convex portion 203 provided on the trapezoidal portion 202A of the flange portion 202 of the ratchet gear 35 while being positioned.
At the same time, the fixed boss 201 of the ratchet gear 35 is inserted into the step portion 191 of the take-up drum 181 and the spline 182B formed on the other end of the torsion bar 182 is press-fitted into the spline groove 201A of the fixed boss 201. To do. Accordingly, the wire 183 is disposed between the flange portion 189 of the winding drum 181 and the flange portions 202 and 205 of the ratchet gear 35, and the ratchet gear 35 is attached to the winding drum 181.
Next, a schematic configuration of the pretensioner unit 7 will be described with reference to FIGS. 2, 3, 44 and 45. FIG. 44 is an exploded perspective view of the pretensioner unit 7. FIG. 45 is a cross-sectional view showing the internal structure of the pretensioner unit 7.
The pretensioner unit 7 is configured to rotate the take-up drum 181 in the webbing take-up direction in an emergency such as a vehicle collision to remove the slack of the webbing 3 and firmly restrain the occupant to the seat.
As shown in FIGS. 44 and 45, the pretensioner unit 7 includes a gas generation member 211, a pipe cylinder 212, a piston 213, a pinion gear 215, a clutch mechanism 216, and a bearing 235.
The gas generating member 211 includes a gas generating agent such as explosive, and is configured to ignite the gas generating agent by an ignition signal from a control unit (not shown) and generate gas by combustion of the gas generating agent. Yes.
The pipe cylinder 212 is formed as an L-shaped cylinder member in which a gas introduction part 212B is connected to one end of a linear piston guide cylinder part 212A. A gas generating member 211 is accommodated in the gas introduction part 212B. Accordingly, the gas generated by the gas generating member 211 is introduced from the gas introduction part 212B into the piston guide cylinder part 212A. Further, an opening 217 is formed in the longitudinal intermediate portion on one side of the piston guide cylinder portion 212A, and a part of the pinion gear teeth 215A of the pinion gear 215 is disposed as will be described later.
The pipe cylinder 212 is sandwiched between the base plate 218 on the side wall 13 side of the housing 11 and the outer cover plate 221, and is sandwiched between the base block 222 and the cover plate 221. The screw 15 is attached and fixed to the outer surface of the side wall 13.
Further, the pretensioner unit 7 is attached to the side wall portion 13 at the upper end portion of the piston guide cylinder portion 212A, and a stopper pin 16 that functions as a stopper for the piston 213, a stopper for the pipe cylinder 212, and a rotation stopper can be inserted. A pair of through holes 212C are formed to face each other.
The piston 213 is formed of a metal member such as a steel material, has a substantially rectangular cross section that can be inserted from the upper end side of the piston guide cylinder portion 212A, and has a long shape as a whole. A rack 213A that meshes with the pinion gear teeth 215A is formed on the side surface of the piston 213 on the pinion gear 215 side. Further, the end surface of the piston 213 on the gas generating member 211 side is formed into a circular end surface 213B corresponding to the cross-sectional shape of the piston guide cylinder portion 212A. A seal plate 223 formed of a rubber material or the like is attached to the circular end surface 213B.
This piston 213 is formed with a through-hole 213C having a long cross-sectional rectangular shape along the longitudinal direction thereof, and both side surfaces thereof are communicated with each other. Further, a gas vent hole 225 communicating with the through hole 213C from the pressure receiving side surface for receiving the gas of the seal plate 223 is formed in the piston 213 and the seal plate 223. As shown in FIG. 45, the piston 213 is configured so that the rack 213A is not connected to the pinion gear teeth 215A before the pretensioner unit 7 operates, that is, in a normal standby state where no gas is generated by the gas generating member 211. The piston guide cylinder portion 212A is inserted and arranged to the back side up to the meshing position.
The pinion gear 215 is a columnar member made of a steel material or the like, and pinion gear teeth 215A that can mesh with the rack 213A are formed on the outer peripheral portion thereof. A cylindrical support portion 215B extending from the pinion gear teeth 215A toward the cover plate 221 is formed. This support portion 215B is rotatably fitted in a support hole 226 formed in the cover plate 221 attached to the side wall portion 13.
In a state where the support portion 215B is rotatably fitted in the support hole 226, a part of the pinion gear teeth 215A is disposed in the opening 217 of the piston guide cylinder portion 212A. As shown in FIG. 45, when the piston 213 moves from the normal standby state to the tip end side of the piston guide tube portion 212A, the rack 213A meshes with the pinion gear teeth 215A, and the pinion gear 215 rotates in the webbing take-up direction. To do.
The rotation of the pinion gear 215 is transmitted to the winding drum 181 through the clutch mechanism 216.
That is, a cylindrical boss portion 215D protruding along the axial direction is formed at the end of the pinion gear 215 on the side wall 13 side in the axial direction. On the outer peripheral surface of the boss portion 215D, a spline composed of six protrusions having the outer diameter of the base end portion is formed. The boss portion 215D is rotatably fitted in a through hole 227 formed in the base plate 218, and protrudes from the winding drum 181 side.
Further, the clutch mechanism 216 rotates the pinion gear 215 from the state in which the winding drum 181 is freely rotated with respect to the pinion gear 215 in a normal state (the state in which the clutch pawl 232 is accommodated) when the pretensioner unit 7 is operated. It is configured to be switchable to a state where it is transmitted to the winding drum 181 (a state where the clutch pawl 232 protrudes).
The clutch mechanism 216 is formed of a pawl base 231 formed of steel or the like, four clutch pawls 232 formed of steel or the like, and a synthetic resin such as polyacetal, and is disposed on the base plate 218 side of the pawl base 231. A substantially annular pawl guide 233 that is abutted, and a synthetic resin such as polyacetal, is abutted against the winding drum 181 side of the pawl base 231, and together with the pawl guide 233, the pawl base 231 and each clutch pawl. And a substantially annular bearing 235 that sandwiches 232.
A fitting hole 236 in which six spline grooves are formed so that the boss 215 </ b> D of the pinion gear 215 is fitted is provided at the center of the pawl base 231. The boss portion 215D of the pinion gear 215 is press-fitted into the fitting hole 236 of the pawl base 231 with the base plate 218 and the pawl guide 233 interposed therebetween, so that the pawl base 231 is attached to the pinion gear 215 so as not to rotate relative to the pinion gear 215. . That is, the pawl base 231 and the pinion gear 215 are configured to rotate integrally.
The bearing 235 is configured to be locked to the outer peripheral portion of the pawl guide 233 by a plurality of elastic locking pieces 235A protruding from the outer peripheral portion to the pawl guide 233 side. Further, a through hole 235 </ b> B having an inner diameter substantially equal to the outer diameter of the boss 187 of the winding drum 181 is formed at the center of the bearing 235. Further, a cylindrical bearing portion 235C having the same inner diameter as the through-hole 235B and having an outer diameter substantially equal to the inner diameter of the boss portion 215D of the pinion gear 215 is continuous from the peripheral portion on the pawl base 231 side of the through-hole 235B. It is erected so as to protrude.
When the boss portion 215D of the pinion gear 215 is press-fitted into the fitting hole 236 of the pawl base 231, the cylindrical bearing portion 235C provided upright at the center portion of the bearing 235 is fitted into the boss portion 215D. . Further, a boss 187 erected at the center position of the end surface portion of the winding drum 181 on the pretensioner unit 7 side is rotatably fitted into the bearing 235. Each pawl base 231 is supported on the pawl base 231 in an accommodation posture. The accommodated posture is a posture in which each clutch pawl 232 is accommodated within the outer peripheral edge of the pawl base 231.
The pawl guide 233 is a substantially annular member, and is disposed at a position facing the pawl base 231 and each clutch pawl 232. Four positioning protrusions (not shown) protrude from the side surface of the pawl guide 233 on the base plate 218 side, and the positioning protrusions are fitted into the positioning holes 218A of the base plate 218. The pawl guide 233 is attached and fixed to the base plate 218 in a non-rotatable state.
Further, on the surface of the pawl guide 233 on the side of the pawl base 231, each posture changing projection 233 </ b> A is protruded corresponding to each clutch pawl 232. Then, when the pawl base 231 and the pawl guide 233 rotate relative to each other by the operation of the pretensioner unit 7, each clutch pawl 232 comes into contact with the attitude changing projection 233A, and the attitude is changed from the accommodated attitude to the locked attitude. It is like that. The locking posture is a posture in which the tip end portion of the clutch pawl 232 protrudes outward from the outer peripheral edge portion of the pawl base 231.
Further, when each clutch pawl 232 changes its position to the locked position, it engages with the winding drum 181. Specifically, the clutch mechanism 216 is fitted into the boss 187 of the take-up drum 181 via the bearing 235 and rotatably supports the take-up drum 181, and each clutch pawl 232 has an outer peripheral edge of the pawl base 231. When projecting outward, the inner gear 186 formed on the inner peripheral surface of the flange 185 can be engaged.
Then, when each clutch pawl 232 is changed to the locked posture, the tip end portion of each clutch pawl 232 is engaged with the internal gear 186, whereby the pawl base 231 rotates the take-up drum 181. The engagement between the clutch pawl 232 and the internal gear 186 is an engagement structure in only one direction that rotates the winding drum 181 in the winding direction of the webbing 3.
Further, once engaged, the clutch pawls 232 are engaged with the internal gear 186 with deformation, and when the take-up drum 181 rotates in the webbing pull-out direction after the engagement, the pinion gear 215 is moved by the pretensioner unit 7. The piston 213 is rotated back through the clutch mechanism 216 in the direction opposite to the direction of operation, and the piston 213 is pushed back in the direction opposite to the operation direction. When the piston 213 is pushed back to a position where the engagement between the rack 213A of the piston 213 and the pinion gear teeth 215A of the pinion gear 215 is disengaged, the pinion gear 215 is disengaged from the piston 213, so that the winding drum 181 rotates freely with respect to the piston 213. become able to.
Next, the operation of the pretensioner unit 7 configured as described above to operate and wind up the webbing 3 will be described with reference to FIGS. 45 and 46. FIG. 46 is an explanatory diagram showing the operation of the pawl 23 when the vehicle collides.
As shown in FIG. 45, when the gas generating member 211 of the pretensioner unit 7 is operated at the time of a vehicle collision or the like, the piston 213 moves toward the tip side of the piston guide cylinder portion 212A by the pressure of the generated gas. At the same time, the pinion gear 215 having the pinion gear teeth 215A meshed with the rack 213A rotates (rotates counterclockwise in FIG. 45).
Further, in the event of a vehicle collision or the like, the inertial mass body 52 of the vehicle acceleration sensor 28 moves on the bottom surface of the sensor holder 51 and rotates the sensor lever 53 upward in the vertical direction. The lock claw 53A rotates the pilot lever 86 upward in the vertical direction. Then, the engaging claw portion 86 </ b> A of the pilot lever 86 is brought into contact with a locking gear tooth 81 </ b> A formed on the outer peripheral portion of the locking gear 81.
The engagement between the engagement claw portion 86A of the pilot lever 86 and the locking gear tooth 81A is an engagement structure in only one direction that operates in a direction that does not rotate the take-up drum 181 in the pull-out direction of the webbing 3. . Therefore, when the pretensioner unit 7 is operating, the winding drum 181 rotates smoothly in the winding direction of the webbing 3 even if the engaging claw 86A of the pilot lever 86 contacts the locking gear teeth 81A. To do.
As shown in FIG. 45, when the pinion gear 215 rotates, the pawl base 231 rotates together with the pinion gear 215. At this time, since the pawl base 231 rotates relative to the pawl guide 233, each posture changing projection 233A formed on the pawl guide 233 comes into contact with the clutch pawl 232, and each clutch pawl 232 is engaged. Changed to a stop posture.
As a result, the front end of each clutch pawl 232 engages with the internal gear 186 of the winding drum 181, and the force that the piston 213 attempts to move to the front end side of the piston guide cylinder portion 212 </ b> A causes the pinion gear 215, the pawl. It is transmitted to the winding drum 181 via the base 231, each clutch pawl 232, and the internal gear 186, so that the winding drum 181 is rotationally driven in the winding direction of the webbing 3, and the webbing 3 is wound around the winding drum 181. It is done.
Further, when the pretensioner unit 7 is actuated at the time of a vehicle collision or the like, when the webbing 3 is continuously pulled out and the take-up drum 181 is rotated in the webbing pulling direction, the engaging claw portion 86A of the pilot lever 86 is provided. Engages with the locking gear teeth 81A formed on the outer peripheral portion of the locking gear 81, and the clutch 85 is rotated in the webbing pull-out direction. Therefore, as shown in FIG. 46, the pawl 23 guided by the guide hole 116 of the clutch 85 is engaged with the ratchet gear portion 35 </ b> A of the ratchet gear 35.
Accordingly, when the webbing 3 is subsequently pulled out after the pretensioner unit 7 is actuated at the time of a vehicle collision or the like, the ratchet gear 35 of the winding drum unit 6 is engaged by the engagement between the pawl 23 and the ratchet gear portion 35A. Is prevented from rotating in the direction in which the webbing 3 is pulled out. The pawl 23 and the ratchet gear portion 35 </ b> A are engaged in only one direction in which the winding drum 181 is rotated in the drawing direction of the webbing 3.
Next, after the pretensioner unit 7 is actuated at the time of a vehicle collision or the like, the occupant is moved forward relative to the vehicle while the engagement between the pawl 23 and the ratchet gear portion 35A of the ratchet gear 35 is still maintained. When the webbing 3 is moved, a large pulling force acts on the webbing 3. When the pulling output acting on the webbing 3 exceeds a predetermined value set in advance, rotational torque in the webbing pulling direction acts on the winding drum 181.
The spline 182A side press-fitted and fixed to the back side of the shaft hole 181A of the winding drum 181 of the torsion bar 182 is rotated by the rotational torque in the webbing pull-out direction acting on the winding drum 181 and the shaft portion of the torsion bar 182 is rotated. The torsional deformation of 182C is started. As the shaft portion 182C of the torsion bar 182 is twisted and deformed, the winding drum 181 rotates in the pulling direction of the webbing 3, and the impact energy is absorbed by the torsional deformation of the torsion bar 182 as a “first energy absorbing mechanism”. Made.
At the same time, when the winding drum 181 is rotated, the pawl 23 and the ratchet gear 35 are engaged with each other, so that relative rotation occurs between the ratchet gear 35 and the winding drum 181. Accordingly, relative rotation occurs between the wire 183 and the ratchet gear 35 as the winding drum 181 rotates, and the impact energy is absorbed by the wire 183 as the “second energy absorbing mechanism”.
[Wire drawing operation]
Here, the operation of the wire 183 when the impact energy is absorbed by the wire 183 will be described with reference to FIGS. 43 and 47 to 50. 47 to 50 are operation explanatory views for pulling out the wire 183. FIG.
As shown in FIG. 43, in the initial state of the winding drum 181 and the ratchet gear 35, the exit side end portion of the wire 183 of the convex portion 193 and the concave portion 194 constituting the holding side bending path 192 of the winding drum 181. Is located near the end portion on the pull-out side of the deformation imparting bending path 206 formed on the outer peripheral portion of the convex portion 203 protruding from the trapezoidal portion 202A of the flange portion 202.
The substantially S-shaped bent portion 183A of the wire 183 is fitted and fixedly held in a holding-side bent path 192 constituted by the convex portion 193, the concave portion 194, and the groove portion 195 of the winding drum 181. Further, a substantially inverted U-shaped bent portion 183B that is continuous with the bent portion 183A of the wire 183 is a deformation-applying bent path 206 formed on the outer peripheral portion of the convex portion 203 protruding from the trapezoidal portion 202A. It is inserted in.
In addition, the wire 183 has a substantially S-shaped bent portion 183A sandwiched between ribs 197 and 198 provided on opposite side surfaces of the convex portion 193 and the concave portion 194 constituting the holding-side bent path 192. . Further, a substantially inverted U-shaped bent portion 183B that is continuous with the bent portion 183A is erected on the rib 208 provided on the side surface portion of the end portion on the drawer side of the convex portion 203 and the outer peripheral portion of the trapezoidal portion 202A. The flange portion 205 is positioned in the deformation-applying bending path 206 by a rib 209 erected on the back side of the rib 208.
As a result, the outlet-side end portion of the wire 183 of the holding-side bending path 192 and the drawing-side end portion of the deformation-applying bending path 206 are opposed to each other through the wire 183 so as to be in a straight line. In addition, a predetermined gap (for example, a gap of about 0.2 mm) is formed between the side surface portion facing the rib 208 at the pull-out side end portion of the deformation imparting bending path 206 and the wire 183, and the rib 209 is formed. A predetermined gap (for example, a gap of about 0.2 mm) is also formed between the outer peripheral surface of the convex portion 203 and the wire 183.
47 to 50, when the winding drum 181 is rotated in the webbing pull-out direction (in the direction of the arrow X2) by pulling out the webbing 3, the ratchet gear 35 is prevented from rotating by the pawl 23. Then, as the winding drum 181 rotates, the step portion 191 is rotated relative to the trapezoidal portion 202A of the ratchet gear 35 in the webbing pull-out direction (in the direction of arrow X2).
As a result, the wire 183 in which the bent portion 183A is fixedly held on the holding-side bent path 192 of the stepped portion 191 is projected to the flange portion 205 protruding from the outer peripheral portion of the trapezoidal portion 202A and the central portion of the trapezoidal portion 202A. It is pulled out in the direction of the arrow X3 while being sequentially squeezed from the deformation imparting bending path 206 having a substantially inverted U shape when viewed from the front formed by the portion 203 and wound around the outer peripheral surface of the step portion 191. At this time, the torsion bar 182 is also twisted and deformed with the rotation of the winding drum 181 at the same time as the wire 183 is pulled out.
In addition, when the wire 183 passes through the deformation imparting bending path 206 having a substantially inverted U shape when viewed from the front while being deformed, the wire 183 faces the rib 208 at the end of the deformation imparting bending path 206 on the drawer side. And slides on the side surface portion in the rotation direction (in the direction of arrow X2) and the outer peripheral surface of the convex portion 203 facing the rib 209 provided on the inner side in the axial direction of the wire 183 relative to the rib 208. . As a result, sliding resistance is generated between the convex portion 203 and the wire 183, and bending resistance is generated by the wire 183 itself, and the impact energy is absorbed by the wire 183 by the sliding resistance and the drawing resistance due to the bending resistance. The
As shown in FIG. 50, when the end of the bent portion 183C of the wire 183 is detached from the deformation-applying bent path 206 as the winding drum 181 rotates, the impact energy is absorbed by the wire 183. After that, only the absorption of impact energy due to the torsional deformation of the torsion bar 182 with the rotation of the winding drum 181 occurs.
As described in detail above, in the seatbelt retractor 1 according to the present embodiment, the ratchet of the pawl 23 when the engaging claw 86A of the pilot lever 86 engages the locking gear teeth 81A of the locking gear 81 in an emergency. When the webbing 3 is pulled out with a delay due to a synchronization shift or the like in the timing of engaging with the gear 35, the engaging claw portion 86A of the pilot lever 86 is mainly bent at an oblique end. In the portion, the receiving plate portion 122 connected via the connecting plate portion 124 is elastically deformed toward the shaft portion 121 side, and elastically deformed toward the shaft portion 121 side, so that the engaging claw portion 86A moves outward in the radial direction. Elastically deforms into a protruding substantially U-shape.
Then, the engaging claw portion 86A is engaged with the engaging claw portion 86A and the elastic deformation of the receiving plate portion 122 connected via the connecting plate portion 124 to the shaft portion 121 side. When the amount of elastic deformation that deviates from the upper limit is reached, the tip of the engaging claw 86A is disengaged radially outward from the locking gear teeth 81A. Thereafter, the pilot lever 86 disengaged from the locking gear teeth 81A is released from the elastic deformation of the engaging claw portion 86A and the receiving plate portion 122 connected via the connecting plate portion 124, and is brought into a normal state shape. Return.
As a result, when there is a delay in the timing at which the pawl 23 and the ratchet gear 35 are engaged after the engaging claw portion 86A of the pilot lever 86 is engaged with the locking gear tooth 81A in an emergency, due to a synchronization shift or the like. Since the engaging claw portion 86A is greatly elastically deformed toward the shaft portion 121 and is disengaged from the engaged locking gear tooth 81A, the pilot lever 86 and the locking gear 81 can be prevented from being damaged. Further, since the engaging claw portion 86A is bent obliquely toward the locking gear 81 side, the engaging claw portion 86A can be smoothly detached from the locking gear teeth 81A when greatly elastically deforming toward the shaft portion 121 side.
In addition, when the engaging claw portion 86A and the receiving plate portion 122 connected via the connecting plate portion 124 are engaged with the locking gear teeth 81A and pressed, they can be elastically deformed toward the shaft portion 121 side. It is possible to reduce the thickness and size of the pilot lever 86 to a certain extent, and the pilot lever 86 can be reduced in size. Further, since both the end portions of the engaging claw portion 86A and the thin plate-like receiving plate portion 122 are connected by the thin plate-like connecting plate portion 124, the mechanical strength of the engaging claw portion 86A is further maintained. The pilot lever 86 can be reduced in weight and size by reducing the thickness.
Further, after entering the opening 138 of the clutch 85 and engaging with the locking gear teeth 81A, the engaging claw 86A that is elastically deformed by being pressed by the locking gear teeth 81A, and the shaft portion 121 of the opening 138. A predetermined gap is formed between the side edge portions. Thereby, it is possible to reliably prevent the clutch 85 from interfering with the elastic deformation of the engaging claw portion 86A, and to prevent the pilot lever 86 from being elastically deformed and to further prevent the pilot lever 86 and the locking gear 81 from being damaged. .
Further, in a state where the engaging claw portion 86A is engaged with the locking gear teeth 81A, a load is applied to the engaging claw portion 86A in the direction of the mounting boss 123, and the engaging claw portion 86A is mainly inclined at the tip portion. In the case where the bent portion is elastically deformed and further rotated, the upward detent portion 125 of the pilot lever 86 is brought into contact with the upward regulating end surface portion 132 of the pilot lever support block 131. Further, when the mounting boss 123 is bent, the outer peripheral surface of the shaft 121 is brought into contact with the load receiving surface 133 of the pilot lever support block 131.
As a result, the pressure load applied to the pilot lever 86 can be supported by the pilot lever support block 131 via the upward detent portion 125 and the shaft portion 121. Therefore, even if the pilot lever 86 and the mounting boss 123 are made small, it is possible to prevent the shaft portion 121 and the mounting boss 123 that support the pressing load with a simple configuration from being deformed or damaged.
In addition, the pilot lever 86 has a predetermined clearance in the rotational direction between the upper restricting end surface portion 132 and the lower restricting end surface portion 136 of the pilot lever support portion block 131 by the upward detent portion 125 and the downward detent portion 126. By forming the structure such that the pilot lever 86 is sandwiched, the rotation angle of the pilot lever 86 can be regulated with a simple structure, and the parts shapes of the clutch 85 and the pilot lever 86 can be further simplified.
Further, the pilot lever 86 has the protruding portion 128 protruding from the outer peripheral surface of the shaft portion 121 protruding from the distal end portion of the elastic locking piece 137 toward the shaft portion 121 by inserting the shaft portion 121 into the mounting boss 123. Since it is attached to the engaging protrusion 137A to be able to contact from the base end side of the elastic engaging piece 137 and is rotatably attached to the attaching boss 123, the pilot lever 86 is disengaged from the attaching boss 123. Can be reliably prevented with a simple configuration.
In addition, this invention is not limited to the said embodiment, Of course, various improvement and deformation | transformation are possible within the range which does not deviate from the summary of this invention. For example, the following may be used. In the following description, the same reference numerals as those of the seat belt retractor 1 according to the embodiment shown in FIGS. 1 to 50 are the same as those of the seat belt retractor 1 according to the embodiment. The corresponding part is shown.
(A) A seatbelt retractor 241 according to another embodiment will be described with reference to FIGS. 51 and 52 are perspective views of a pilot lever 286 of a seatbelt retractor 241 according to another embodiment. 53 to 56 are explanatory views for explaining the operation when the synchronization shift of the pawl 23 of the “vehicle body sensitive locking mechanism” of the seatbelt retractor 241 according to another embodiment occurs. 53, 54 and 56, the portion showing the relationship between the pawl 23 and the ratchet gear 35, the portion showing the relationship between the pilot lever 86 and the locking gear 81, and the sensor holder 51 and the sensor lever 53 of the vehicle acceleration sensor 28. The part of is notched.
The schematic configuration of the seatbelt retractor 241 according to another embodiment is substantially the same as the configuration of the seatbelt retractor 1 according to the embodiment.
However, as shown in FIGS. 51 and 52, the pilot lever 286 has substantially the same configuration as the pilot lever 86, but the engaging claw portion 286A has an end surface portion facing the locking gear 81 (the upper end surface in FIG. 51). Is formed so as to gradually decrease over the entire width in the rotational axis direction from both end portions of the shaft portion 121 side base end portion and the tip end portion toward the substantially central portion. Thus, the engaging claw portion 286A is formed with a bent portion 286B having a plate thickness smaller than both end portions of the shaft portion 121 side proximal end portion and the distal end portion over the entire width in the rotational axis direction at the substantially central portion in the longitudinal direction. Has been.
The plate thickness at the bent portion 286B formed at the substantially central portion in the longitudinal direction of the engaging claw portion 286A is larger than the plate thickness at the substantially central portion in the longitudinal direction of the engaging claw portion 86A of the pilot lever 86 of the above embodiment. You may form so that it may become. Thereby, the mechanical strength of the engaging claw portion 286A can be easily increased more than the mechanical strength of the engaging claw portion 86A of the pilot lever 86.
Next, the lock operation when the synchronization shift of the pawl 23 of the “body-sensitive lock mechanism” occurs will be described with reference to FIGS. 53 to 56. As shown in FIG. 53, when the webbing 3 is pulled out in the direction of the arrow 151 in a state where the engaging claw portion 286A of the pilot lever 286 is engaged with the locking gear tooth 81A of the locking gear 81, the locking gear 81 Is rotated in the webbing pull-out direction (the direction of the arrow 165). Further, as the locking gear 81 rotates in the webbing pull-out direction, the clutch 85 is rotated in the webbing pull-out direction (in the direction of the arrow 166), and the pawl 23 is rotated toward the ratchet gear 35 ( Arrow 167 direction).
Further, the elastic rib 146 of the clutch 85 abuts against the fixed-side protrusion 148 because the clutch-side protrusion 146A is rotated toward the fixed-side protrusion 148 provided upright on the inner peripheral wall of the mechanism housing portion 87. And is elastically deformed radially inward, and smoothly gets over the fixed-side protrusion 148.
Subsequently, as shown in FIGS. 53 and 54, in the clutch 85, the engaging teeth 23 </ b> A and 23 </ b> B of the pawl 23 come into contact with the ratchet gear portion 35 </ b> A of the ratchet gear 35, and the rotation of the pawl 23 is stopped. Therefore, the rotation in the webbing pull-out direction (the direction of the arrow 166) is locked.
On the other hand, as shown in FIG. 53, there is still a slight gap between the engaging teeth 23A and 23B of the pawl 23 and the teeth of the ratchet gear portion 35A engaged with the engaging teeth 23A and 23B. Therefore, when the webbing 3 is continuously pulled out, the ratchet gear 35 rotates in the webbing pull-out direction (in the direction of the arrow 175) until the lock is completed. At the same time, the locking gear 81 rotates integrally with the ratchet gear 35 and presses the engaging claw portion 286A of the pilot lever 286 engaged with the locking gear tooth 81A.
For this reason, the pilot lever 286 is further rotated clockwise around the axis of the mounting boss 123, and the upward detent portion 125 is brought into contact with the upward regulating end surface portion 132 of the pilot lever support block 131, The upward rotation in the vertical direction is restricted. At the same time, the mounting boss 123 bends toward the pilot lever support block 131 and the shaft 121 of the pilot lever 286 is brought into contact with the load receiving surface 133 of the pilot lever support block 131.
Then, as shown in FIGS. 54 to 56, the ratchet gear 35 is moved until the end of each engagement tooth 23A, 23B of the pawl 23 comes into contact with each tooth of the ratchet gear portion 35A until the locking operation is completed. It is further rotated in the webbing pull-out direction (the direction of the arrow 175). At the same time, the engaging claw portion 286A of the pilot lever 286 and the receiving plate portion 122 connected via the connecting plate portion 124 are pressed toward the shaft portion 121 by the locking gear teeth 81A, and the shaft portion It is elastically deformed to the 121 side and is bent into a substantially U shape protruding outward in the radial direction. At this time, the bent portion 286 </ b> B formed at a substantially central portion in the longitudinal direction of the pilot lever 286 is elastically deformed toward the shaft portion 121 side.
Further, as shown in FIG. 55, the opening 138 into which the pilot lever 286 of the clutch 85 enters has an engaging claw portion 286A and a receiving plate portion 122 connected through a connecting plate portion 124 as a shaft portion. It is formed in a size that does not contact even if it is elastically deformed to the 121 side and is bent into a substantially U shape protruding outward in the radial direction. Further, the distal end portion of the engaging claw portion 286A of the pilot lever 286 has a substantially U shape in which the engaging claw portion 286A is elastically deformed at a bent portion 286B formed at a substantially central portion in the longitudinal direction and protrudes outward in the radial direction. As it bends in a letter shape, it shifts radially outward (in the direction of arrow 176) with respect to the locking gear teeth 81A.
Therefore, as shown in FIGS. 53 to 56, the elastic deformation of the receiving claw portion 286 </ b> A of the pilot lever 286 and the receiving plate portion 122 connected via the connecting plate portion 124 toward the shaft portion 121 side is as follows. When the engaging claw portion 286A reaches an elastic deformation amount that is disengaged from the locking gear teeth 81A, the distal end portion of the engaging claw portion 286A is disengaged radially outward from the locking gear teeth 81A.
As shown in FIG. 56, the pilot lever 286 released from the locking gear tooth 81A is released from the elastic deformation of the engaging claw portion 286A and the receiving plate portion 122 connected via the connecting plate portion 124. To return to the normal shape. Further, since the engagement between the engagement claw portion 286A and the locking gear 81 is released, the pilot lever 286 is rotated downward in the vertical direction (in the direction of the arrow 177) by its own weight, and the downward direction of the pilot lever 286. The anti-rotation portion 126 returns to the initial position where the pilot lever support block 131 is in contact with the downward regulating end surface portion 136.
As a result, when the engaging claw portion 286A is pressed by the locking gear teeth 81A, the engaging claw portion 286A is elastic toward the shaft portion 121 side at a substantially central portion from the distal end portion of the engaging claw portion 286A to the base end portion on the shaft portion 121 side. By deforming, the impact load on the pilot lever 286 and the locking gear 81 can be reduced, and damage to the pilot lever 286 and the locking gear 81 can be effectively suppressed. In addition, the engaging claw portion 286A is elastically deformed toward the shaft portion 121 side at a substantially central portion from the distal end portion to the shaft portion 121 side base end portion. It can be elastically deformed into a substantially U shape in the axial direction and smoothly disengage from the locking gear teeth 81A formed on the outer peripheral portion of the locking gear 81, and the engagement claw portion 286A can be further reduced in size and thickness. As a result, the pilot lever 286 can be further reduced in size.
The engaging claw portion 286A is elastically deformed toward the shaft portion 121 side of the engaging claw portion 286A of the pilot lever 286 and the receiving plate portion 122 connected via the connecting plate portion 124. Even when the amount of elastic deformation does not deviate from the clutch, the clutch-side protrusion 146A of the elastic rib 146 provided so as to protrude radially outward from the outer periphery of the clutch 85 is elastically deformed radially inward, It overlies the fixed-side protrusion 148 erected on the inner peripheral wall of the mechanism accommodating portion 87 and is in contact with or close to the side surface of the fixed-side protrusion 148 on the webbing pull-out direction side.
Accordingly, during the unlocking operation of the “body-sensitive locking mechanism”, the rotation difference applying mechanism 149 releases the engagement between the pilot lever 286 and the locking gear 81 with a slight winding amount of the webbing 3 and the winding. The rotation lock of the take-up drum unit 6 can be released.
1,241 Seat belt retractor 3 Webbing 5 Housing unit 6 Take-up drum unit 9 Lock unit 10 Lock mechanism 11 Housing 23 Pawl 28 Vehicle acceleration sensor 35 Ratchet gear 52 Inertial mass 53 Sensor lever 81 Locking gear 81A Locking gear tooth 82 Lock arm 85 Clutch 86, 286 Pilot lever 86A, 286A Engaging claw portion 86B Rib portion 121 Shaft portion 122 Receiving plate portion 123 Mounting boss 124 Connection plate portion 125 Upward detent portion 126 Downward detent portion 128 Convex portion 131 Pilot lever support Block 132 Upper restriction end face portion 136 Lower restriction end face portion 137 Elastic locking piece 137A Locking protrusion 138 Opening portion 286B Bending portion
A winding drum that is rotatably stored in the housing and winds and stores the webbing;
A ratchet gear that rotates integrally with the winding drum;
A locking mechanism for preventing rotation of the winding drum in the webbing pull-out direction in an emergency;
An inertial mass that swings in response to an acceleration greater than a predetermined value of the vehicle;
A sensor lever which is pushed by the inertial mass body and swings upward in the vertical direction to activate the lock mechanism;
A clutch that is coaxial with the take-up drum and that is rotatable relative to the take-up drum, and that engages with the ratchet gear by rotation to induce a pawl that prevents rotation of the take-up drum in the webbing pull-out direction;
A pilot lever that is pivotally supported by a mounting boss that is erected on the clutch and is rotated by being pressed by the swinging sensor lever;
A locking gear that is integrally and coaxially attached to the take-up drum, and that engages the pilot lever by rotation;
The pilot lever is
A cylindrical shaft portion into which the mounting boss is rotatably inserted;
An engaging claw portion that protrudes outward from the outer peripheral surface of the shaft portion so as to face the locking gear and engages the locking gear;
Frettage After the engaging claw portion at the time of sudden engages the locking gear teeth formed on the outer periphery of the locking gear, engaging claws is delayed the timing of engagement of the said pawl ratchet gear occurs When pressed by the locking gear teeth, the engagement claw portion is elastically deformed toward the shaft portion side, and the engagement claw portion and the locking gear teeth can be disengaged. A seatbelt retractor characterized in that elastic deformation of the engagement claw portion is eliminated when the engagement claw portion and the locking gear teeth are disengaged.
The engaging claw portion is formed in a substantially L shape when viewed from the rotational axis direction with a tip portion obliquely bent toward the locking gear side,
The said engaging claw part is elastically deformed to the said axial part side in the part where the front-end | tip part of this engaging claw part was bent diagonally, when this locking gear tooth is pressed. 2. A retractor for a seat belt according to 1 .
The engaging claw portion has an end surface portion facing the locking gear that is gradually lowered over the entire width in the rotational axis direction from both end portions of the shaft-side base end portion and the distal end portion toward a substantially central portion. Formed to be
2. The seat according to claim 1, wherein when the engaging claw is pressed against the locking gear teeth, the sheet is elastically deformed toward the shaft portion at the substantially central portion of the engaging claw. Belt retractor.
The clutch has an opening provided so that the pilot lever rotated by being pressed by the sensor lever enters and can be engaged with the locking gear teeth,
When the engaging claw is pressed by the locking gear teeth and is elastically deformed toward the shaft, a predetermined gap is formed between the shaft side edge of the opening and the engaging claw. The seatbelt retractor according to any one of claims 1 to 3 , wherein the seatbelt retractor is provided.
A thin plate-like contact portion that is provided substantially parallel to the engagement claw portion and is pressed against the swung sensor lever;
A thin plate-like connecting plate portion for connecting both tip sides of the contact portion and the engaging claw portion;
The retractor for a seat belt according to any one of claims 1 to 4 , wherein the contact portion is provided so as to be elastically deformable toward the shaft portion side together with the engagement claw portion.
The clutch is a pilot lever support portion projecting so as to be opposed to the outer peripheral surface on the opposite side in the radial direction with respect to the engagement claw portion of the shaft portion fitted into the mounting boss. Have
The pilot lever has an upward detent portion erected outward in the radial direction so as to be opposed to the pilot lever support portion with a predetermined gap in the rotational direction from the outer peripheral surface of the shaft portion. ,
In an emergency, when the engaging claw is engaged with the locking gear teeth formed on the outer peripheral portion of the locking gear, the pilot lever has the upper detent portion in the circumferential direction of the pilot lever support portion. the one end face in a state where the rotation regulation has been in the vertically upward abuts, according to any one of claims 1 to 5, characterized in that rotating the clutch in accordance with rotation of the locking gear Seat belt retractor.
The pilot lever is a downward detent that is erected radially outward from the outer peripheral surface of the shaft portion so as to sandwich the pilot lever support portion together with the upward detent portion with a predetermined gap in the rotational direction. Part
In the pilot lever, when the engaging claw is rotated by its own weight, the downward rotation preventing portion comes into contact with the other end surface in the circumferential direction of the pilot lever supporting portion, thereby restricting the rotation downward in the vertical direction. The retractor for a seat belt according to claim 6 , wherein the retractor is used.
In an emergency, when the engaging claw engages with the locking gear teeth formed on the outer peripheral portion of the locking gear and the mounting boss is bent, the outer peripheral surface of the shaft portion becomes the pilot lever support portion. The retractor for a seat belt according to claim 6 or 7 , wherein the clutch is rotated in accordance with the rotation of the locking gear in a contact state.
The clutch is erected so as to be elastically deformable radially outward with respect to the shaft portion by forming a predetermined gap between the clutch portion and the shaft portion fitted into the mounting boss. It has an elastic locking piece formed with a locking projection protruding on the part side,
The pilot lever has a convex portion that protrudes radially outward from an outer peripheral surface facing the elastic locking piece of the shaft portion fitted into the mounting boss,
The pilot lever is provided so that the convex portion can be brought into contact with the locking projection from the base end side of the elastic locking piece by fitting the shaft portion into the mounting boss. The seatbelt retractor according to any one of claims 1 to 8 , wherein the seatbelt retractor is rotatably attached.
JP2012050616A 2012-03-07 2012-03-07 Seat belt retractor Active JP5924987B2 (en)
JP2012050616A JP5924987B2 (en) 2012-03-07 2012-03-07 Seat belt retractor
DE112013002142.0T DE112013002142T5 (en) 2012-03-07 2013-02-25 webbing take
US14/381,080 US20150034753A1 (en) 2012-03-07 2013-02-25 Seatbelt retractor
PCT/JP2013/054802 WO2013133072A1 (en) 2012-03-07 2013-02-25 Seatbelt retractor
KR1020147028092A KR102056711B1 (en) 2012-03-07 2013-02-25 Seatbelt retractor
JP2013184540A JP2013184540A (en) 2013-09-19
JP5924987B2 true JP5924987B2 (en) 2016-05-25
ID=49116554
JP2012050616A Active JP5924987B2 (en) 2012-03-07 2012-03-07 Seat belt retractor
US (1) US20150034753A1 (en)
JP (1) JP5924987B2 (en)
KR (1) KR102056711B1 (