JP3233519B2 - Seat belt retractor - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a seatbelt device mounted on a vehicle such as an automobile for protecting an occupant.
In particular, the present invention relates to a seat belt retractor that locks the rotation of a reel shaft that winds up a webbing in an emergency and prevents the webbing from extending.

[0002]

2. Description of the Related Art A conventional seat belt retractor mounted on a vehicle such as an automobile is disclosed in, for example, Japanese Patent Laid-Open No. 5-1934.
As disclosed in Japanese Patent Publication No. 41, there is a frame lock type seat belt retractor in which a rotation of a reel shaft for winding a webbing in a pulling-out direction is prevented by a frame when necessary.

As shown in FIG. 22, a seat belt retractor 101 is a reel shaft on which a webbing 102 is wound.
103, a U-shaped frame 104 that rotatably supports both ends of the reel shaft 103, and is disposed between the frame 104 and the reel shaft 103 to allow the normal rotation of the reel shaft 103 to allow rotation when necessary. Locking means 105 and 106 which operate to prevent the reel shaft 103 from rotating at least in the webbing withdrawing direction, and deceleration sensing means (not shown) which is activated when a deceleration of a predetermined value or more is applied to the vehicle.
And a lock operating means (not shown) for operating the lock means by operating the deceleration sensing means.

[0004] Such a seat belt retractor 101
In normal operation, the reel shaft 103 is freely rotatable at normal times, so that the webbing 102 can be freely pulled out, and the occupant can freely move forward.
In an emergency such as when a large deceleration acts on the vehicle, deceleration sensing means (not shown) called a vehicle sensor detects the deceleration and activates the lock operating means. Actuation of the lock means 105,10
6 works. Also, when the webbing 102 is suddenly pulled out, a webbing sensor (not shown) detects the sudden withdrawal of the webbing 102 and activates the lock operating means. 105 and 106 operate.

The operation of the locking means 105 and 106 prevents the rotation of the reel shaft 103 and prevents the webbing 102 from being pulled out.
The vehicle is restrained by 02 and is prevented from moving forward due to the inertia of the occupant.

As shown in FIGS. 22 and 23, a locking means 105 is rotatably and radially movable on an annular tooth 104b attached to a left side wall 104a of a frame 104 and a left end face of a reel shaft 103. And a main pawl 107 engageable with the teeth 104b. As shown in FIGS. 22 and 24, the lock means 106 is provided on the right side wall 104c of the frame 104 with an annular tooth 104d and on the right end face of the reel shaft 103 so as to be rotatable.
And a backup pawl 108 which can be engaged with 04d.

When the vehicle sensor or the webbing sensor operates as described above, the main pawl 107
And the backup pawl 108 is operated, and the teeth 107a, 108a of the right and left side walls 104a, 104c are respectively
And engage with each other. Thereby, the rotation of the webbing 102 in the pull-out direction α is prevented, and the webbing 102 is prevented from being pulled out.

[0008]

In such a conventional seat belt retractor, when the teeth 107a, 108a of the main pawl 107 and the backup pawl 108 are engaged with the teeth 104b, 104d of the left and right side walls 104a, 104c, The pull-out force of the webbing 102 is transmitted to the frame 104 via the reel shaft 103, the main pawl 107, and the backup pawl 108. That is, webbing 1
The pullout force of 02 is supported by the frame. In this case, the main pawl 107 and the backup pawl 108 are moved by the vibration of the vehicle, the rotation of the reel shaft 103, and the like.
24, a complicated motion is obtained by adding a motion in a direction perpendicular to the paper of FIG. For this reason, it is conceivable that the teeth 107a, 108a of the main pawl 107 and the backup pawl 108 are shifted left and right in FIG. 22 and mesh with the teeth 104b, 104d of the left and right side walls 104a, 104c.

When the teeth 107a, 108a of the main pawl 107 and the backup pawl 108 are engaged with the teeth 104b, 104d which are largely shifted left and right, the teeth 107a, 108a and the teeth 107a, 108a
The engagement with 104b and 104d becomes uncertain.

However, as shown in FIGS. 25 and 26, the teeth 107a, 108a of the conventional main pawl 107 and backup pawl 108 are simply formed from a flat plate. It is conceivable that the teeth 107a and 108a of the backup pawl 108 are largely shifted left and right with respect to the teeth 104b and 104d.

SUMMARY OF THE INVENTION The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a locking means for preventing at least rotation of a reel shaft in a webbing withdrawal direction, and a tooth on a reel shaft side and a tooth on a frame side. The present invention is to provide a seat belt retractor capable of preventing a shift of the meshing position between the pawl and the tooth, and stably and reliably meshing the pawl with the teeth.

[0012]

SUMMARY OF THE INVENTION In order to solve the above-mentioned problems, a first aspect of the present invention provides a reel shaft for winding a webbing, a frame for rotatably supporting both ends of the reel shaft, and a frame. And a lock means disposed between the reel shafts, which normally allows the rotation of the reel shaft and operates when necessary to prevent the rotation of the reel shaft at least in the webbing pull-out direction. A seat belt retractor comprising: deceleration sensing means that operates when deceleration is applied; and lock actuation means that actuates the locking means by actuation of the deceleration sensing means. And a plurality of teeth provided on any one of the frame and any one of the reel shaft and the frame. And a pawl that is normally held in a non-operating position that does not mesh with the teeth and moves to an operating position that meshes with the teeth when necessary and prevents rotation of the reel shaft in at least the webbing withdrawal direction. Wherein the pawl has a plurality of teeth meshable with two or more predetermined number of teeth among a plurality of teeth provided on one of the reel shaft and the frame,
Large displacement prevention means is provided on the pawl for preventing a plurality of teeth of the pawl from meshing with the teeth provided on any one of the reel shaft and the frame in the axial direction of the reel shaft. Wherein the large displacement prevention means comprises a web-like large displacement prevention flange provided between a plurality of teeth of the pawl,
The web-like large misalignment preventing flange is provided on one of the reel shaft and the frame when the plurality of teeth of the pawl mesh with teeth provided on one of the reel shaft and the frame. It is characterized in that the meshing position is prevented from being largely shifted in the axial direction of the reel shaft by abutting on the side surface of the tooth.

[0013] The invention according to claim 2 is characterized in that the web-like large displacement prevention flange is provided on a side of the pawl facing the other of the reel shaft and the frame, the reel shaft and the frame. The pawl is provided so as to come into contact with a side surface of a tooth provided on any one of the reel shaft of the pawl and the other side of the frame.

[0014]

In the seat belt retractor according to the present invention having the above-described structure, when the plurality of teeth of the pawl mesh with the teeth provided on one of the reel shaft and the frame, the pawl moves from the pawl to the reel shaft and the frame. Even if a load acts on the teeth provided on any one of the teeth in a diagonal direction or the like, even if the meshing positions of the plurality of teeth of the pawl and the teeth provided on any one of the reel shaft and the frame are largely shifted, The pawl is prevented from largely moving in the axial direction of the reel shaft by contacting the web-like large misalignment prevention flange with the side surface of the teeth provided on one of the reel shaft and the frame. Thereby, the plurality of teeth of the pawl and the teeth provided on one of the reel shaft and the frame are stably and reliably meshed.

[0015]

Embodiments of the present invention will be described below with reference to the drawings. FIGS. 1 and 2 are exploded perspective views showing an embodiment of a seat belt retractor according to the present invention. FIG. 1 is a left side portion thereof, and FIG. 2 is a right side portion thereof. The lines A ₁ and B ₁ in FIG. ₁ are aligned with the lines A ₂ and B _{2 in} FIG. 2, respectively, to form an exploded perspective view of the entire embodiment. FIGS. 3 to 5 show the assembled state of the seat belt retractor of this embodiment. FIG. 3 is a right side view of the seat belt retractor with a cover removed and a part of the cross section taken away. FIG. 5 is a front view taken along a line IV-IV in FIG. 3, and FIG. 5 is a sectional view taken along a line VV in FIG.

As shown in FIGS. 1 to 5, the seat belt retractor 1 in this embodiment includes right and left side walls 2a,
2b is provided with a frame 2 formed in a U shape. These right and left side walls 2a, 2b are connected to each other by a connecting member 2c, whereby the frame 2 is reinforced. Also, a circular hole 2d is formed in the right side wall 2a as shown in FIG. 6, and a circular hole 2e is formed in the left side wall 2b as shown in FIG.
Further, on the inner peripheral surfaces of the holes 2d and 2e in the right and left side walls 2a and 2b, a predetermined number (in the illustrated example, 3
), 2g... Are formed.
These teeth 2f and 2g are formed in the same shape of a triangular chevron. In this case, the surface facing the webbing withdrawing direction α is a relatively steep inclined surface, whereas the webbing winding direction is The surface facing β is a relatively gentle slope. The phase of the left tooth 2g is set ahead of the phase of the right tooth 2f by a predetermined angle (for example, 3 °) in the webbing withdrawing direction α. Further, four locking holes 2h, 2i, 2j, 2k are formed in the left side wall 2b, and four locking holes 2m, 2n, 2p, 2q are formed in the right side wall 2a. Has been established.

As shown in FIG. 4, a reel shaft 4 for winding the webbing 3 is disposed between the right and left side walls 2a, 2b of the frame 2. As shown in FIG. 8, the reel shaft 4 has a central webbing take-up portion 4a and circular guides formed at both right and left ends of the webbing take-up portion 4a to guide the winding and pulling out of the webbing 3. The first rotating shaft 4 provided at the center of the flange portions 4b and 4c and the right guide flange portion 4b and protruding outward in the axial direction.
d, provided at the center of the guide flange 4c,
It comprises a rotating shaft 4d and a coaxial second rotating shaft 4e. The first rotating shaft 4d and the second rotating shaft 4e coaxial with each other are located on the central axis of the webbing winding portion 4a. The webbing take-up portion 4a is provided with a radial through hole 4f into which the tip of the webbing 3 is inserted and locked so that the webbing 3 can be taken up.

The right guide flanges 4b as shown in FIG. 9 (a) is formed in a circular shape having a diameter d _1, in the right guide flanges 4b, pawl spring 18 (shown in FIG. 2) is accommodated 4 g of first concave fitting portions and main pawl 1
7 (the details are shown in FIG. 13 to be described later), a second concave fitting portion 4h in which the claw portion 17c is disposed, and a claw portion 1 of the main pawl 17
A load receiving portion 4j formed with a load receiving surface 4i for receiving a load applied to 7c, and an axial through hole 4k into which a joint pin 19 (details are shown in FIG. 14 described later) is rotatably loosely fitted. Is provided. The load receiving surface 4i is formed of a circular arc having a predetermined length concentric with the through hole 4k.

Further, on the outer peripheral surface of the guide flange portion 4b, a webbing take-up portion 4a of the reel shaft 4 is provided on the right,
When disposed at a predetermined position between the left side walls 2a and 2b, an arc-shaped retaining flange 4m for preventing the reel shaft 4 from coming out of the hole 2d of the right side wall 2a is provided. The retaining flange 4m is set to have substantially the same diameter as the outer diameter of the guide flange portion 4b, and is eccentric so as to protrude by a predetermined amount from the outer peripheral surface of the guide flange portion 4b substantially opposite to the through hole 4k. Is provided. Then, the maximum size of the dimension d ₂ of the outer peripheral surface formed from a stop flange 4m missing a guide flange portion 4b, right, left side wall 2a, 2b of the holes 2d, formed in the inner peripheral surface of 2e teeth The inner diameter d ₃ (shown in FIGS. 6 and 7) of the tip of 2f, 2g is set slightly smaller. That is, the guide flange portion 4b including the retaining flange 4m can pass through the through holes 2d and 2e.

As shown in FIG. 9B, a third pawl 20c of a backup pawl 20 (details are shown in FIG. 15 described later) is disposed on the left guide flange 4c.
The concave fitting portion 4n and the claw portion 20 of the backup pawl 20
A load receiving portion 4q formed with a load receiving surface 4p for receiving a load applied to c, and an axial through hole 4k in which the joint pin 19 is rotatably loosely fitted are provided. The load receiving surface 4p is formed of a circular arc of a predetermined length concentric with the through hole 4k.

Further, when the webbing take-up portion 4a is disposed at a predetermined position on the outer peripheral surface of the guide flange portion 4c between the right and left side walls 2a and 2b, the reel shaft 4 is connected to the hole 2e of the left side wall 2b. An arc-shaped stopper flange 4r is provided to prevent the flange 4r from slipping out of the hole. This retaining flange 4r is the same as the right retaining flange 4 described above.
It is formed in the same size as m.

As apparent from FIG. 8, the through hole 4k not only penetrates the guide flanges 4b and 4c, but also penetrates the central webbing winding portion 4a in the axial direction. It is provided so as to penetrate the reel shaft 4 in the axial direction.

As shown in FIGS. 1 and 4, the left side wall 2b
Is provided with an urging force applying means 5 for applying a winding force of the webbing 3 to the reel shaft 4. Furthermore,
As shown in FIGS. 2, 3 and 4, a seat belt lock operating means 6 is attached to the right side wall 2a, and when a predetermined deceleration is applied to the vehicle, the deceleration is sensed and the seat belt is locked. A deceleration sensing means 7 for operating the lock operation means 6 is provided.

As is clear from FIG. 1, the urging force applying means 5
Is a power spring 8 composed of a spiral spring, a bush 9 to which an inner end 8a of the power spring 8 is connected to apply a spring force, and a spring for fixing the outer end 8b of the power spring 8 and accommodating the power spring 8. It comprises a case 10, a cover 11 attached to the spring case 10 to cover the power spring 8, and a cap 12 for closing a hole for a spring stopper.

The bush 9 is fitted and connected to the second rotating shaft 4e so as to be relatively non-rotatable, whereby the spring force of the spring 8 is applied to the reel shaft 4 via the bush 9 in the winding direction of the webbing 3. It always acts on β.

On the other hand, as is apparent from FIG. 2, the seat belt lock operating means 6 includes a lock gear first cover 13 fixed to the right side wall 2a of the frame 2 and a lock gear 14
And an inertia body 15 swingably attached to the lock gear 14, a control spring 16 disposed between the lock gear 14 and the inertia body 15, and a joint pin 19 having one end passing through the through hole 4k. Mated and supported
The other end of the main pawl 17 which is located in the second concave fitting portion 4h and is disposed on the right guide flange portion 4b and forms a locking member
A pawl spring 18 housed in the first concave fitting portion 4g of the reel shaft 4 and contracted between the reel shaft 4 and the main pawl 17, and a joint pin 19 penetrating through the axial hole 4k of the reel shaft 4. The backup pin is connected to one end of the joint pin 19 so as to be relatively non-rotatable, and the other end is located on the third concave fitting portion 4n and is disposed on the left side guide flange portion 4c so as to form a locking portion. A lock gear second cover 21 fitted and supported on the pawl 20 and the right side wall 2a of the frame 2 to cover the lock gear first cover 13, the lock gear 14, the inertia body 15, the main pawl 17, the joint pin 19 and the deceleration sensing means 7. It is composed of

Further, as shown in FIG. 1, the seat belt retractor 1 is provided with a webbing guide 22 for moving and guiding the webbing 3 in accordance with the amount of the webbing 3 pulled out and taken up.

As shown in FIG. 10, the lock gear first cover 13 has a relatively large annular projection 13a, and a predetermined number of teeth 13c, 13c,
.. (Six in the illustrated example) are formed at equal intervals over the entire circumference. When the lock gear first cover 13 is fixed to the right side wall 2a, the teeth 13c are formed on the right side wall 2a.
And the number of teeth 13c is set to a common divisor of the teeth 2f (in the illustrated example, the number of teeth 2f is 30 and the number of teeth 13c is 6).
Pieces). The number of the teeth 13c does not necessarily need to be set to a common divisor of the teeth 2f, and can be set to any number smaller than the number of the teeth 2f, and the teeth 13c need not necessarily be provided at equal intervals in the circumferential direction. Alternatively, they can be provided at irregular intervals. However, as shown in the figure, it is desirable to provide the teeth 13c at equal intervals in the circumferential direction by the common divisor of the teeth 2f.

These teeth 13c are formed in a triangular mountain shape. In this case, the surface facing the webbing withdrawing direction α is a substantially vertical surface, whereas the surface facing the webbing winding direction β. Has a relatively gentle slope. The lock gear first cover 13 is provided with two locking projections 13d and 13e. The first lock gear cover 13 is removably attached to the right side wall 2a of the frame 2 by fitting these locking projections 13d, 13e into locking holes 2m, 2n formed in the right side wall 2a.

Further, in the upper part of the lock gear first cover 13, a horizontal elongated guide hole 13f is formed. Further, a housing portion 13g of the deceleration sensing means 7 is provided below the lock gear first cover 13 so as to open on the surface on the opposite side of the drawing. The deceleration sensing means 7 is accommodated and fixed in the accommodation portion 13g.

As shown in FIG. 11, the lock gear 14 comprises a circular flat plate portion 14a and an annular flange 14b formed on the outer peripheral end of the flat plate portion 14a. A predetermined number of teeth 14c, 14c,... Are formed at equal intervals on the outer peripheral surface of the flange 14b. These teeth 14c are formed in a triangular mountain shape, and in this case, the surface facing the webbing withdrawing direction α is a relatively gentle slope, whereas the surface facing the webbing winding direction β is used. Is almost vertical.

Right guide flange portion 4b of flat plate portion 14a
A spring receiving member 14d for supporting one end of the control spring 16 is provided upright on a surface opposite to the opposing surface, and a spring guide 14e is provided on the spring receiving member 14d.
It stands upright in parallel with 4a. Further, a shaft 14f is provided upright on the flat plate portion 14a, and an inertial body 15 is swingably supported on the shaft 14f as described later. An arc-shaped retaining member 14g is erected adjacent to the shaft 14f. When the inertial body 15 is fitted on the shaft 14f, the inertia body 15 is normally supported by the retaining member 14g so as to be swingable without coming off from the shaft 14f, and the inertial body 15 is pulled out from the shaft 14f by the inertial body 15. When a slight external force is applied to the shaft 14f, the shaft 14f can easily come out. Furthermore,
A first stopper 14h and a second stopper 14i are erected on the flat plate portion 14a, and a cylindrical rotating shaft 14j is erected in the center of the flat plate portion 14a in the axial direction.
The first rotary shaft 4d of the reel shaft 4 passes through the hole of the cylindrical rotary shaft 14j, and the rotary shaft 14j is rotatable about the first rotary shaft 4d.

Further, the flat plate portion 14a has
First, second and third cam holes 14 of a predetermined shape penetrating through
k, 14m, and 14n are respectively formed. The first cam hole 14k is formed as an arc centered on the rotation shaft 14j.

On the other hand, a spring receiving member 14p for supporting one end of the pawl spring 18 is provided upright on the surface of the flat plate portion 14a facing the right guide flange portion 4b (the surface not surrounded by the annular flange 14b). A spring guide portion 14q is provided on the spring receiving member 14p so as to be parallel to the flat plate portion 14a.

As shown in FIG. 12, the inertial body 15 is formed in a substantially semicircular shape from a flat plate, and a hole 15a is formed in the center thereof.
Are drilled. A locking claw 15b is provided at one end.
Is formed, and the other end of the control spring 16 is supported and guided at the other end by a spring receiving portion 15c.
And a spring guide 15d. As shown in FIG. 3, the inertia body 15 is swingably movable by fitting a hole 15a into a shaft 14f of the lock gear 14.
4 supported.

As shown in FIG. 3, the control spring 16
The lock gear 14 and both guide portions 14 of the inertia body 15 are supported in a state where the inertia body 15 is swingably supported by the shaft 14f.
e, 15d, and is contracted between the spring receiving member 14d and the spring receiving portion 15c. Therefore, due to the spring force of the control spring 16, the inertia body 15 is always urged in the webbing withdrawing direction α with respect to the lock gear 14, and is normally in a position in contact with the first stopper 14h as shown by a solid line. Will be retained. In addition, the inertial body 15
Is rotated against the lock gear 14 in the webbing take-up direction β against the spring force of the control spring 15, and comes to a position in contact with the second stopper 14i as shown by a two-dot chain line.

As shown in FIGS. 3 and 4, when the seat belt retractor 1 is assembled, the lock gear 1
The teeth 13 c of the cover 13 are located inside the annular flange 14 b of the lock gear 14 and between the flange 14 b and the inertial body 15. When the inertial body 15 is in the normal state,
Is held at a position in contact with the first stopper 14h indicated by a solid line, so that the locking claw 15b is held at a non-engagement position away from the teeth 13c. When the inertial body 15 is at a position where it comes into contact with the second stopper 14i shown by a two-dot chain line in FIG. 3, the locking claw 15b is at a position where it can be engaged with the teeth 13c.

When the lock gear 14 rotates in the webbing withdrawing direction α when the locking claw 15b is at the engageable position, the locking claw 15b engages with the teeth 13c and the lock gear 14
Is prevented from rotating further in the webbing withdrawing direction α. When the lock gear 14 rotates in the webbing winding direction β while the locking claw 15b is at the engageable position, the locking claw 1
5b moves against the control spring 16 along the gentle slope of the teeth 13c and jumps over the teeth 13c, so that the lock gear 14 is rotatable in the webbing winding direction β.

As shown in FIG. 13, the main pawl 17 is formed substantially in the shape of a fan, and a through hole 17a is formed at a key portion of the fan.
Is formed. A claw 17c is formed at the end of the fan opposite to the hook, and a tooth 17d is formed at the tip of the claw 17c so as to engage with the teeth 2f of the right side wall 2a of the frame 2. I have.

Then, as shown in FIG.
7b is fitted into a joint pin 19 penetrating through the through hole 14k, and the main pawl 17 is disengaged from the right guide flange portion 4b of the reel shaft 4 around the joint pin 19 with a non-engaged position indicated by a two-dot chain line and a dotted line. It is provided so as to be swingable between the engagement positions indicated by. Main Paul 17
In the disengaged position, the tooth 17d at the tip is located completely inward from the outer peripheral surface of the guide flange portion 4b and the frame 2
At the engagement position, the teeth 17d project outward from the outer peripheral surface of the guide flange portion 4b and engage with the teeth 2f.

A load transmitting portion 17e is formed at the end of the claw portion 17c opposite to the tooth 17d. The load transmitting portion 17e is formed by an arc composed of a circle concentric with the through hole 17a and the boss portion 17b. When the main pawl 17 is attached to the right guide flange portion 4b, the load transmitting portion 17e comes into contact with the load receiving surface 4i of the right guide flange portion 4b. In this case, since the load transmitting portion 17e and the load receiving surface 4i are both formed by the same concentric arc, the load transmitting portion 17e
Is the load transmitting portion 17e regardless of the position of the main pawl 17.
Are always in contact with the load receiving surface 4i of the reel shaft 4. Thus, the load applied to the claw portion 17c of the main pawl 17 is caused by the load transmitting portion 17e abutting the load receiving surface 4i of the reel shaft 4 in a planar manner.
7e to the load receiving surface 4i and the reel shaft 4
Will be supported by. In such a load supporting structure, the tooth 17d, which is the load point, and the load transmitting portion 17
Since e is relatively close to the main pawl 17, the bending hardly acts on the main pawl 17, and almost only the compression acts. In addition, the load transmitting portion 17e and the load receiving surface 4i
And the surface of the reel shaft 4
And the stress generated by dispersing the load becomes relatively small. Therefore, the strength of the main pawl 17 may be smaller than that of the conventional main pawl, and the main pawl 17 can be formed of a relatively light material such as resin.

Further, the load transmitting portion 17 of the main pawl 17
A cylindrical cam follower 17f protrudes from the surface opposite to the side e, and the cam follower 17f
Is inserted into the third cam hole 14n of the third cam hole 1n.
4n. In addition, tooth 1
7d surface side of the load transmitting portion 17e (that is, the main pawl 1
A web-like large-position misalignment prevention flange 17g is formed on the edge of the side 7 facing the reel shaft 4).

The pawl spring 18 is accommodated in the first concave fitting portion 4g of the reel shaft 4 and the lock gear 1
4 is fitted to the spring guide portion 14q, and is contracted between the wall surface of the first concave fitting portion 4g and the spring receiving portion 14p. Therefore, the pawl spring 18 is connected to the main pawl 1
7 with respect to the reel shaft 4 the webbing withdrawal direction α
Is always energized. Therefore, the main pawl 17 is normally set to the non-engagement position by the urging force of the pawl spring 18.

As shown in FIG.
The main body 19a is formed in a circular cross section, and an arm 19b extending perpendicular to the main body 19a is formed at the right end of the main body 19a in FIG. This arm 1
At the tip of 9b, a cam follower 19c having a circular cross section is provided. This cam follower 19c is a lock gear 14
The second cam hole 1m is fitted into the second cam hole 14m.
You will be guided to 4m. A shaft section 19d having a rectangular cross section is formed at the other end of the main body 19a.
The shaft portion 19d is adapted to be fitted into a hole formed at one end of the backup pawl 20, which will be described later, so as not to rotate relatively. Accordingly, when the cam follower 19c is guided by the second cam hole 14m and the arm 19b rotates, the main body 1
The rotation of the main body 19a is transmitted to the backup pawl 20, and the backup pawl 20 is
It turns according to the movement of the cam follower 19c guided by the cam hole 14m.

As shown in FIG. 15, the backup pawl 20 is formed in a substantially sector shape, and a boss portion 20b having a through-hole 20a having a rectangular cross section is formed at a key portion of the sector. A claw portion 20c is formed at the end of the fan opposite to the hook, and a tooth 20d is formed at the tip of the claw portion 20c so as to engage with the teeth 2g of the left side wall 2b of the frame 2. I have. Then, as shown in FIG.
The shaft portion 19d of the joint pin 19 is fitted into the through-hole 20a of b in such a manner that it cannot rotate relatively, and the backup pawl 20 is fixed to the joint pin 19 by the screw 23. Therefore, the backup pawl 20 is swingably provided about the joint pin 19 with respect to the left guide flange portion 4c of the reel shaft 4 between a non-engagement position indicated by a two-dot chain line and an engagement position indicated by a dotted line. ing. In the disengaged position of the backup pawl 20, the tooth 20 at the tip thereof is
d is located completely inward from the outer peripheral surface of the guide flange portion 4c so as not to engage with the teeth 2g of the left side wall 2b of the frame 2. In the engaged position, the teeth 20d are located outside the outer peripheral surface of the guide flange portion 4c. At the position for engaging the teeth 2g.

A load transmitting portion 20 e is formed at an end of the claw portion 20 c opposite to the tooth 20 d. The load transmitting portion 20e is formed by an arc composed of a circle concentric with the through hole 20a and the boss portion 20b. When the backup pawl 20 is attached to the left guide flange 4c, the load transmitting section 20e comes into contact with the load receiving surface 4p of the left guide flange 4c. In this case, since the load transmitting portion 20e and the load receiving surface 4p are both formed by the same concentric arc, the load transmitting portion 20e is always in contact with the load receiving surface 4p regardless of the position of the backup pawl 20. As described above, the load applied to the claw portion 20c of the backup pawl 20 is transmitted from the load transmitting portion 20e to the load receiving surface 4p by the load transmitting portion 20e abutting on the load receiving surface 4p in a planar manner. Become supported. Also in this backup pawl 20, the generated stress is relatively small similarly to the case of the main pawl 17, and the backup pawl 20 can be formed of a relatively light material such as resin. Further, a web-like large misalignment preventing flange 20g is formed on the edge of the tooth 20d on the side of the load transmitting portion 20e (ie, the side facing the reel shaft 4 of the backup pawl 20).

The web-like large-position misalignment preventing flanges 17g, 20g of the main pawl 17 and the backup pawl 20 are formed by the teeth 17d, 20d of the main pawl 17 and the backup pawl 20, respectively, on the right and the left side walls 2a, 2b. When meshed with 2f and 2g, as shown in FIG. 16, they are located inside the right and left side walls 2a and 2b. That is, the teeth 17d and 20d are located inside the teeth 2f and 2g, as indicated by the two-dot chain line in FIGS. 17 (a) and (b). Therefore, the teeth 17d, 20d of the main pawl 17 and the backup pawl 20 and the right and left side walls 2a,
When the main pawl 17 and the backup pawl 20 apply a load to the frame 2 in an oblique direction as shown by arrows γ and δ in FIGS. , Η, the main pawl 17 and the backup pawl 20 move away from the right and left flange portions 2b, 2c (axial directions of the reel shaft 4), respectively, to form the teeth 17d, 20d and the teeth 2f, 2g.
Even if the meshing position of the right and left side shifts greatly, the large position shift prevention flanges 17g and 20g are not provided with the right and left side walls 2a and 2b.
f and 2g (that is, the side surfaces of 2f and 2g) from the reel shaft 4 side, so that the teeth 17d and 20d and the teeth 2d
The position of engagement with f and 2g is prevented from being largely shifted,
The teeth 17d and 20d and the teeth 2f and 2g mesh stably and reliably.

As shown in FIG. 18, the deceleration sensing means 7
Is a case 7a, a lever 7b swingably supported by the case 7a, and housed in the case 7a, which is normally in a state shown by a solid line, and has two points when a deceleration exceeding a predetermined level occurs in the vehicle. And an inertial body 7c swinging at the position of the chain line.

The case 7a is held by the supporting member 7f by fitting the engaging projections 7d and 7e into the concave fitting portions of the guide members 7g and 7h of the supporting member 7f. This support member 7f is fixed to the right side wall 2a. The rear end of the lever 7b is rotatably supported by the case 7a, and a locking claw 7i that can engage with the teeth 14c of the lock gear 14 is provided at the front end of the lever 7b.

The inertial body 7c is mounted on the mounting portion 7j of the case 7a. In the normal state, the inertial body 7c stands vertically with respect to the mounting portion 7j as shown by a solid line, and
b is held at a substantially horizontal position indicated by a solid line, and the lever 7
In this solid line position b, the lever 7b is in the non-engagement position where the locking claw 7i is not engaged with the teeth 14c of the lock gear 14.

When a predetermined amount of deceleration acts on the vehicle, the inertial body 7c tilts until the upper outer peripheral surface substantially abuts against the inner surface of the front wall of the case 7a as shown by a two-dot chain line. Since the lever 7b is pushed upward by the inclination of the inertial body 7c, the lever 7b rotates to the position indicated by the two-dot chain line. At the position of the two-dot chain line of the lever 7b, the lever 7b
Is an engagement position where the locking claw 7i is engaged with the teeth 14c of the lock gear 14.

As shown in FIG. 1, the webbing guide 22
Is disposed between the side walls 2a and 2b of the frame 2 and has a body 22 having a hole 22a in the center through which the webbing 3 penetrates.
b, and projecting in the longitudinal direction from both ends of the main body 22b, and are slidably fitted into guide holes 11a formed in the cover 11 of the power spring 8 and guide holes 13h formed in the first cover 13 of the lock gear. Protruding shafts 22c and 22d having an elliptical cross section.

The webbing guide 22 has two guide holes 11a and 13h according to the webbing take-up position which changes depending on the webbing 3 take-up amount of the reel shaft 4.
, And always guides the webbing 3 along the axial direction of the hole 22a. Thereby, the webbing guide 22
The guide angle of the webbing 3 with respect to the webbing 3 becomes substantially constant, so that the webbing 3 can be wound up and pulled out smoothly, and the webbing 3 is protected from being rubbed against the webbing guide 22.

Since the protruding shafts 22c and 22d are formed in an oval cross section, the webbing guide 22 does not rotate around the protruding shafts 22c and 22d and tilt when the webbing 3 is wound and pulled out. Therefore, the webbing guide 22 can slide smoothly along the guide holes 11a and 13h, and the winding and pulling out of the webbing 3 become further smooth. Further, when the webbing guide 22 slides, the right and left end walls 22 of the main body 22a are moved.
g, 22h are guided by the inner surfaces of both the cover 11 of the frame 2 and the first cover 13 of the lock gear.
The rotation of the webbing guide 22 around the vertical axis is also prevented. Therefore, the webbing guide 22 is provided in the guide hole 1.
It is possible to slide more smoothly along 1a and 13h.

Next, the operation of the main pawl 17 and the backup pawl 20 will be described in detail with reference to FIGS. 19 and 20, the upper part (I) explains the operation of the main pawl 17, and the lower part (I)
I) explains the operation of the backup pawl 20. FIG. 19 and FIG. 20 are schematic views, in which the teeth 2f, the locking claws 17d, and the three cam holes 14k, 14m, and 14n are described on the same plane on the main pawl 17 side. 4 also shows the state of the main pawl 17 and the backup pawl 20 as viewed from the right side in FIG.

In FIG. 19, the pawl spring 18
(Not shown in FIG. 19; see FIG. 2 etc.)
The reel shaft 4 (FIG. 19 only shows a through hole 4k through which the main body 19a of the joint pin 19 penetrates and the main pawl 17 provided on the reel shaft 4) is provided with a lock gear 14 (also the cam holes 14k and 14m in FIG. 19). , 1
Webbing winding direction β relative to 4n)
, The reel shaft 4 is relatively rotated with respect to the lock gear 14 in the webbing winding direction β until the main body 19a comes into contact with the upper end edge of the cam hole 14k. State.

In this normal state, the cam follower 19c of the joint pin 19 contacts the upper edge of the cam hole 14m, and the cam follower 17f of the main pawl 17 contacts the upper edge of the cam hole 14n. Then, the locking pawl 17d of the main pawl 17 is largely separated from the teeth 2f of the right side wall 2a, and the main pawl 17 is in a non-engaging position where the locking pawl 17d does not engage with the teeth 2f. On the other hand, the cam follower 19c, 1
In accordance with the rotation angle of the joint pin 19 determined by the respective contact positions of the 7f with the upper edges of the cam holes 14k and 14n, the backup pawl 20 becomes the position shown in FIG. That is, the locking pawl 20d of the backup pawl 20 is largely separated from the teeth 2g of the left side wall 2b, and the backup pawl 20 is also at a non-engaging position where the locking claw 20d does not engage with the teeth 2g.

The reel shaft 4 has its first rotating shaft 4d
(Not shown in FIG. 19: see FIG. 8) relative to the lock gear 14 in the webbing withdrawing direction α, that is, the through hole 4k through which the main body 19a passes is centered on the first rotation shaft 4d. When the lock gear 14 rotates relative to the first to third cam holes 14k, 14m, and 14n in the α direction, the main body 19a and the boss 17b of the main pawl 17 are respectively moved to the first position as shown in FIG. The first cam hole 14k is slightly moved downward relative to the first cam hole 14k.

At the same time, the cam follower 17f is slightly guided downward by the third cam hole 14n. In this case, the boss 17b moves slightly leftward in the drawing due to the cam shape of the first cam hole 14k, and the third cam hole 14n
The cam follower 17f moves slightly to the left due to the cam shape of FIG. 7, but since the amount of movement of the cam follower 17f to the left is slightly larger than the amount of movement of the boss portion 17b to the left, the main pawl 17 moves in the β direction. To slightly rotate. Thereby, the locking claw 17d approaches the tooth 2f.

At the same time, the cam follower 19c moves downward while being guided by the second cam hole 14m. In this case, the cam shape of the second cam hole 14m determines the cam follower 19c.
Also moves to the right, the arm 19b slightly rotates in the α direction about the main body 19a. The rotation of the arm 19b in the α direction also slightly rotates the main body 19a in the α direction. However, since the reel shaft 4 rotates in the α direction, the main body 19a is rotated.
And the arm 19b hardly rotates relative to the reel shaft 4. Therefore, the backup pawl 20 is held at the non-engaged position as shown in FIG.

As shown in FIG. 6C, when the reel shaft 4 further rotates in the α direction relative to the lock gear 14, the main body 19a and the boss portion 17b move further downward along the first cam hole 14k. And move to the left. At the same time, the cam follower 17f is guided by the third cam hole 14n and moves slightly further downward. Since the further movement amount of the cam follower 17f to the left is slightly larger than the further movement amount of the boss portion 17b to the left, the main pawl 17 further slightly rotates in the β direction, and the locking claw 17d is moved to the tooth 2f. Start to engage.

At the same time, the cam follower 19c is guided by the second cam hole 14m and moves slightly downward and leftward. In that case, by the cam shape of the second cam hole 14m,
Since the cam follower 19c also moves slightly downward and to the left, the arm 19b hardly rotates. However, since the reel shaft 4 is further rotated in the α direction, the main body 19a
And the arm 19b relatively rotates in the β direction with respect to the reel shaft 4. As a result, the backup pawl 20 slightly rotates relative to the reel shaft 4 in the β direction, and the locking claw 20d approaches the teeth 2g.

When the reel shaft 4 is further rotated relative to the lock gear 14 in the direction α as shown in FIG. 4D, the main pawl 17 is further slightly rotated in the direction β relative to the reel shaft 4. Moves, and the locking claw 17d moves to the teeth 2f.
Is largely engaged. Similarly, the backup pawl 20 further slightly rotates in the β direction, and the locking pawl 20d
Begin to engage the teeth 2g. In this way, the engagement of the locking pawl 20d of the backup pawl 20 with the tooth 2g is started slightly later than the engagement of the locking pawl 17d of the main pawl 17 with the tooth 2f.

As shown in FIG. 20E, when the reel shaft 4 is further rotated relative to the lock gear 14 in the α direction, the main pawl 17 and the backup pawl 20 are similarly moved with respect to the reel shaft 4 respectively. Further, the amount of engagement of the locking claw 17d with the teeth 2f and the amount of engagement of the locking claw 20d with the teeth 2g increase.

As shown in FIG. 11F, the relative rotation of the reel shaft 4 in the α direction causes the locking pawl 17d to be substantially engaged with the teeth 2f. The amount of engagement with 2g further increases.

As shown in FIG. 10G, the relative rotation of the reel shaft 4 in the α direction causes the locking pawl 17d to be completely engaged with the teeth 2f, so that the main pawl 17 is moved to the right side. It completely engages the teeth 2f of the wall 2a. On the other hand, the locking claw 20d is in a state of being substantially engaged with the tooth 2f.

As shown in FIG. 7H, the further relative rotation of the reel shaft 4 in the α direction keeps the engagement between the locking pawl 17d and the teeth 2f and the backup pawl 20. Completely engage the teeth 2g of the left side wall 2b.

As described above, in this embodiment, when the reel shaft 4 is relatively rotated in the α direction with respect to the lock gear 14, the locking pawl 17d of the main pawl 17 is first engaged with the teeth 2f of the right side wall 2a. After the start of the engagement, the locking pawl 20d of the backup pawl 20 starts engaging with the teeth 2g of the left side wall 2b with a delay, and after the engaging claw 17d has completely engaged with the teeth 2f, the locking claw 20d is delayed with the teeth. The engagement is completed at 2 g.
Thereby, a poor engagement does not occur in at least one of the engagement between the main pawl 17 and the teeth 2f and the engagement between the backup pawl 20 and the teeth 2g, so that the engagement is reliably performed. Become.

Next, the operation of the thus configured retractor of this embodiment will be described. [Normal state in which deceleration of a predetermined value or more does not act on the vehicle] In this state, since the inertia body 7c of the deceleration sensing means 7 does not tilt forward, the lever 7b is at the solid line position shown in FIG. 7i is at a non-engagement position away from the teeth 14c of the lock gear 14. Similarly, the locking claw 1 of the inertial body 15
5b, main pawl 17 and backup pawl 20
Are also in the disengaged position as shown in FIGS. 3 and 5, respectively.

Therefore, in this state, the operation of the urging force applying means 5 is mainly performed on the seat belt retractor 1. That is, the reel shaft 4 is urged in the webbing winding direction β by the spring force of the power spring 8 of the urging force applying means 5, and the webbing 3 is wound.
In this state, the webbing winding amount is the maximum,
Therefore, the webbing guide 22 is at the rightmost position of the stroke of the webbing guide 22 in FIG.

In this state, the tongue (not shown) attached to the webbing 3 is separated from the buckle member (not shown). Therefore, the webbing 3 is wound by the spring force of the power spring 8 as described above.

(State when Webbing is Pulled Out) When the occupant pulls out the webbing 3 to put on the seat belt, the reel shaft 4 and the bush 9 rotate in the webbing pulling direction α. Therefore, the power spring 8 is tightened. At this time, the winding amount of the webbing 3 of the reel shaft 4 decreases in accordance with the drawing amount of the webbing 3, and the webbing withdrawing position of the webbing 3 from the seat belt retractor 1 is reduced as the winding amount of the webbing 3 decreases as shown in FIG. , The webbing guide 22 also moves to the left in FIG.

(State when the hand is released from the webbing after the tongue and the buckle member are connected) At the time when the occupant connects the tongue and the buckle member, the webbing 3 is longer than the drawn-out length in the normal wearing state. Since the webbing 3 is excessively pulled out, when the occupant releases the webbing 3 after the joining operation, the webbing 3 is taken up by the spring force of the power spring 8 until the webbing 3 fits the occupant's body.
At this time, the spring force of the power spring 8 is appropriately determined so that the webbing 3 does not give a feeling of pressure to the occupant. In the winding of the webbing by the power spring 8, the webbing withdrawal position of the webbing 3 from the seat belt retractor 1 changes rightward in FIG. 3, and accordingly, the webbing guide 22 also moves rightward in FIG.

While the vehicle is running, the seat belt retractor 1 keeps this state unless a deceleration of a predetermined value or more acts on the vehicle. However, when the occupant moves forward normally, the webbing 3 is freely pulled out. Therefore, the occupant can freely adjust the sitting posture and the like. Even in the normal forward movement of the occupant, the webbing withdrawal position of the webbing 3 from the seat belt retractor 1 changes to the left, and accordingly, the webbing guide 22 also moves to the left in FIG.

[State when deceleration of a predetermined value or more acts on the vehicle] When a deceleration of a predetermined value or more acts on the vehicle due to sudden braking or the like during running of the vehicle, the seat belt lock operating means 6 and the deceleration sensing means 7 work together. First, as the first stage, the inertia body 7c of the deceleration sensing means 7 moves forward (the position shown by the two-dot chain line in FIG. 3) by inertia, so that the lever 7b rotates upward and the two-dot chain line in FIG. The position indicated by. For this reason, the locking claw 7i of the lever 7b is at the engagement position where the locking claw 7i engages with the teeth 14c of the lock gear 14. On the other hand, the webbing 3 is pulled out because the occupant tries to move forward due to the deceleration of the vehicle equal to or more than the predetermined value, and the webbing 3 is pulled out. try to.

However, since the teeth 14c of the lock gear 14 immediately engage with the locking claws 7e, the lock gear 14 immediately stops rotating in the pull-out direction α. As a result, only the reel shaft 4 continues to rotate in the pull-out direction α, so that the reel shaft 4 relatively rotates in the α direction with respect to the lock gear 14.

As a result of the relative rotation of the reel shaft 4 in the α direction, the main pawl 17 rotates relative to the reel shaft 4 in the β direction as shown in FIGS. After a short delay, the backup pawl 20 rotates relative to the reel shaft 4 in the β direction and engages with the teeth 2g. As a result, the rotation of the reel shaft 4 in the webbing withdrawing direction α is prevented. As a result, withdrawal of the webbing 3 caused by the occupant trying to move forward due to inertia is reliably prevented. This ensures that the occupant is restrained and protected. At this time, since the webbing 3 is hardly pulled out, the webbing guide 22 hardly moves.

[State when webbing is suddenly pulled out] In this state, webbing 3 is suddenly pulled out, and reel shaft 4, lock gear 14 and inertia body 15 are suddenly moved in webbing pulling direction α. Try to rotate. However, since the spring force of the control spring 16 is not so large, the control spring 1
6 shrinks, and the inertial body 15 causes an inertia delay. That is,
The inertial body 15 not only revolves in the webbing withdrawing direction α together with the lock gear 14 but also rotates relative to the lock gear 14 in the β direction.

The rotation of the inertia body 15 causes the locking claw 15b to move to the engagement position where it comes into contact with the second stopper 14i as shown by the two-dot chain line in FIG.
With the teeth 13c. Therefore, the revolution of the inertial body 15,
The rotation of the lock gear 14 in the webbing withdrawing direction α is prevented. Therefore, only the reel shaft 4 rotates in the webbing withdrawing direction α. As a result, the reel shaft 4 rotates relative to the lock gear 14 in the α direction as described above.

Due to the relative rotation of the reel shaft 4 in the α direction, the main pawl 17 rotates and engages with the teeth 2f in the same manner as described above, and thereafter the backup pawl 20 engages with the teeth 2f with a delay. As a result, the rotation of the reel shaft 4 in the webbing withdrawing direction α is prevented.
As a result, withdrawal of the webbing 3 caused by the occupant trying to move forward due to inertia is reliably prevented. This ensures that the occupant is restrained and protected. Also in this case, since the webbing 3 is hardly pulled out, the webbing guide 22 hardly moves.

FIG. 21 shows another embodiment of the present invention.
It is a perspective view similar to 6. Note that the same reference numerals are given to components corresponding to those in the above-described embodiment, and description thereof will be omitted.

In the above-described embodiment, the present invention is applied to a frame lock type retractor. In this embodiment, a pawl 24 is rotatably provided on the right side wall 2a of the frame 2 as shown in FIG. When the teeth 24a of the pawl 24 mesh with the teeth 25a of the disc-shaped flange 25 fixed to one end of the reel shaft 4, rotation of the reel shaft 4 in the pull-out direction α of the webbing 3 is prevented. The present invention is applied to the retractor 1.

That is, a large positional deviation preventing flange 24b is provided at the tip of the tooth 24a of the pawl 24. The large displacement prevention flange 24b of this embodiment is
Is engaged between the right side wall 2a and the disc-shaped flange 25 when the teeth 24a of the disc-shaped flange 25 mesh with the teeth 25a of the disc-shaped flange 25. Therefore, the pawl 24 is located on the right side wall 2a.
Even if it tries to move in the direction away from the position, since it contacts the large position deviation prevention flange 24b and the teeth 25a, the engagement position between the pawl 24 and the invention 25a is prevented from being largely shifted. As described above, in this embodiment, it is possible to obtain substantially the same effects as those of the above-described embodiment.

[0084]

As is clear from the above description, according to the seat belt retractor of the present invention, when the plurality of teeth of the pawl mesh with the teeth provided on one of the reel shaft and the frame, the pawl is engaged. When a load acts on the teeth provided on one of the reel shaft and the frame in an oblique direction, the meshing position between the plurality of teeth of the pawl and the teeth provided on one of the reel shaft and the frame may be reduced. Even if it is going to shift greatly, the pawl is prevented from moving largely in the axial direction of the reel shaft by the web-like large position shift prevention flange,
A plurality of teeth of the pawl can be stably and reliably meshed with teeth provided on one of the reel shaft and the frame.

[Brief description of the drawings]

FIG. 1 is an exploded perspective view showing an embodiment of a seat belt retractor according to the present invention in an exploded perspective view, and showing a left portion thereof.

FIG. 2 is an exploded perspective view showing a right portion of the embodiment shown in FIG.

FIG. 3 is a left side view of the seat belt retractor with a cover removed, showing an assembled state of the seat belt retractor of the embodiment.

FIG. 4 is a sectional view showing an assembled state of the seat belt retractor of the embodiment, taken along line IV-IV in FIG. 3;

FIG. 5 is a partial cross-sectional view taken along line VV in FIG. 4 showing an assembled state of the seat belt retractor of the embodiment.

FIG. 6 is a right side view of a frame used in this embodiment.

FIG. 7 is a left side view of a frame used in this embodiment.

FIG. 8 is a front view of a reel shaft used in this embodiment.

9A and 9B show a reel shaft used in this embodiment, wherein FIG. 9A is a right side view thereof, and FIG. 9B is a left side view thereof.

FIG. 10 is a left side view showing a lock gear first cover used in this embodiment.

FIG. 11 is a view showing a lock gear used in this embodiment.

FIG. 12 is a diagram showing an inertial body used in this embodiment.

13A and 13B show a main pawl used in this embodiment, wherein FIG. 13A is a left side view, FIG. 13B is a front view thereof,
(C) is a right side view thereof.

14A and 14B show a joint pin used in this embodiment, wherein FIG. 14A is a front view thereof, and FIG.
Sectional view along the line XIVB, (c) is a left side view thereof.

15A and 15B show a backup pawl used in this embodiment, wherein FIG. 15A is a left side view, FIG. 15B is a front view thereof,
(C) is a right side view thereof.

FIG. 16 is a perspective view showing an operation state of this embodiment.

FIG. 17 is a partially enlarged sectional view of FIG. 4;

FIG. 18 is a partially cutaway view of the deceleration sensing means used in this embodiment.

FIG. 19 is an explanatory diagram illustrating a part of the operation of the main pawl and the backup pawl in this embodiment.

FIG. 20 is an explanatory diagram illustrating another part of the operation of the main pawl and the backup pawl in this embodiment.

FIG. 21 is a perspective view similar to FIG. 16, showing another embodiment of the present invention.

FIG. 22 is a front view partially showing a cross section of a conventional seat belt retractor.

FIG. 23 is a diagram illustrating the operation of a main pawl in a conventional seat belt retractor.

FIG. 24 is a diagram illustrating the operation of a backup pawl in a conventional seat belt retractor.

25A and 25B show a conventional main pawl, wherein FIG. 25A is a front view, and FIG. 25B is a right side view.

26A and 26B show a conventional backup pawl, wherein FIG. 26A is a front view, and FIG. 26B is a right side view.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Seat belt retractor, 2 ... Frame, 2a ... Right side wall, 2b ... Left side wall, 2d, 2e ... Through-hole, 2f, 2g ...
Teeth, 3 ... webbing, 4 ... reel shaft, 4a ... webbing winding section, 4b ... right guide flange section, 4c ...
Left guide flange part, 4i, 4p ... load receiving surface, 4j,
4q: load receiving portion, 4k: through hole, 4m, 4r: retaining flange, 4n: third concave fitting portion, 5: urging force applying means, 6: seat belt lock operating means, 7: deceleration sensing means, 13: lock gear first cover, 13c: teeth, 15
... Inertial body, 16 ... Control spring, 17 ... Main pawl, 17d ... Main pawl teeth, 17g ... Large displacement prevention flange, 18 ... Paul spring, 19 ... Joint pin, 20 ... Backup pawl, 20d ... Backup pawl teeth , 20g ... Large displacement prevention flange, 2
DESCRIPTION OF SYMBOLS 1 ... Lock gear 2nd cover, 22 ... Webbing guide

──────────────────────────────────────────────────続 き Continued on front page (58) Field surveyed (Int.Cl. ⁷ , DB name) B60R 22/36-22/40

Claims (2)

(57) [Claims] A reel shaft for winding the webbing; a frame rotatably supporting both ends of the reel shaft; and a frame disposed between the frame and the reel shaft to allow the reel shaft to rotate normally. A locking means which is activated when necessary to prevent the reel shaft from rotating at least in the webbing withdrawal direction; a deceleration sensing means which is activated when a deceleration equal to or more than a predetermined value is applied to the vehicle; Wherein the lock means comprises: a plurality of teeth provided on one of the reel shaft and the frame; a plurality of teeth provided on one of the reel shaft and the frame; provided on the other of the frame and is held during normal the teeth in the non-actuated position does not mesh Both consists of a pawl which moves to the operating position to prevent at least a webbing pull-out direction of rotation of the reel shaft and meshes with the teeth during the required, said pawl is in said reel shaft and said frame
Two or more of the teeth provided on any one
A plurality of teeth meshable with a fixed number of teeth, a plurality of teeth of the pawl , the reel shaft, and the
The meshing position with the teeth provided on either side of the frame
Large displacement prevention means for preventing serial deviating largely in the axial direction of the reel shaft is provided on said pawl, before
The large displacement prevention means is provided between the plurality of teeth of the pawl.
And a web-shaped flange for preventing large displacement, the web-shaped flange for preventing large displacement is provided with a plurality of pawls.
Number of teeth and any of the reel shaft and the frame
At the time of engagement with the teeth provided on one of the
And the teeth provided on one of the frames
The meshing position of the reel shaft is
A seat belt retractor adapted to prevent a large deviation in the axial direction . 2. A web-like large misalignment preventing flange.
Is the reel shaft and the frame of the pawl.
The reel provided on the side facing one of the other
Provided on one of the shaft and the frame
The reel shaft and the front of the pawl on the sides of the teeth
Made from either the other side of the serial frame to abut
Seat belt retractor according to claim 1, wherein the are.