JPH0481343A - Lock lever pivoting structure - Google Patents

Abstract

PURPOSE:To enhance of a lock lever with respect to releasing force by improving a pivoting structure of a lock lever rotatably pivoted between a lock position where a locked member is restricted against spring force and an unlock position, and reducing a resisting moment without damaging strength of a pivot. CONSTITUTION:A support rod 2, to a top end of which a buckle 1 of a seat belt device is fixed, is supported at its lower part by a support plate, which is liftably inserted in a frame 8. A lock device 32 for locking the support plate ordinarily at a lifting limit is provided between the support plate and the frame 8. In a pivoting structure of a lock lever 34 in the lock device 32, a semi- cylindrical recessed part 56 of a small diameter is provided in an outside circumferential surface of a pivot 45 and a fulcrum roller 57 is fitted into the recessed part 56. In this fulcrum roller 57, a circular arc shape projection 57a, being a part thereof, is bearingsupported by a bearing surface 58 of a pivot hole 49. In order to prevent abutting on an inside surface of the pivot hole 49 until the lock lever 34 turns by a specified angle, a gap (s) is provided usually between an outside circumferential surface of the pivot 45 and the inside circumferential surface of the pivot hole 49.

Description

Detailed Description of the Invention A0 Object of the Invention (1) Industrial Application Field The present invention relates to a lock lever shaft support structure, specifically, to a locking position that restrains a member to be locked against a spring force acting thereon. and an unlocked position for releasing the locked member.
The lock lever and the pivot fixed to one side of the frame,
This invention relates to an improvement in fitting into a shaft hole provided on the other side.

(2) Conventional technology FIG. 20 shows an example of a conventional lock lever shaft support structure.

In the figure, the frame 8 includes a locked member 33 that is biased to rotate in a certain direction by a spring force S, and a lock lever that can hold the locked member 33 in a predetermined position against the spring force S. and 34 are respectively pivoted by pivots 39 and 45. The locked state of the locked member 33 by the lock lever 34 is determined by the pair of protrusions 43 and 4 at the tip of the locked member 33.
4, the lock lever 340 and the roller 48 are engaged, and the pivot shaft 45 of the lock lever 34 and the roller 48 are arranged on the line of action of the force acting on the lock lever 34 from the locked member 33. . The pivot 4 is rotated so that the lock lever 34 can rotate between a locked position in which the roller 48 is engaged between the protrusions 43 and 44 and an unlocked position in which the roller 48 is disengaged from the protrusions 44 and 45.
The pivot shafts 45 provided on one and the other of the frame 5 and the frame 8 are fitted into the shaft hole 49 with substantially no gap.

(3) Problems to be Solved by the Invention In the conventional structure described above, in order to rotate the lock lever 34 to the unlocked position by applying a release force R to the tip of the lock lever 34, the release force R is applied to the lock lever 34. It is necessary to make the applied release moment R-a greater than at least the resistance moment f-r due to the frictional resistance f around the pivot shaft 45.

Therefore, when the effective arm length a of the lock lever 34 is kept constant, if the radius r of the pivot shaft 45 is made as small as possible, the lock lever 34 can be rotated with a relatively small release force R. This is effective in increasing the responsiveness to the release force R of. However, there are limits to reducing the diameter of the pivot 45 in terms of strength.

The present invention has been made in view of the above circumstances, and has a lock lever shaft support structure that can reduce the resistance moment without impairing the strength of the pivot shaft and increase the responsiveness to the release force of the lock lever. The purpose is to provide

B1 Structure of the Invention (1) Means for Solving the Problems In order to achieve the above object, the present invention provides a structure in which the spring force is applied to one and the other of the outer circumferential surface of the pivot shaft and the inner circumferential surface of the shaft hole. A circular arc-shaped projection having a smaller diameter than the pivot shaft and a support surface are respectively provided, which rotatably abut each other on the line of action of the force acting on the lock lever from the locked member, and the lock lever is mounted at the center of the circular arc-shaped projection. - is characterized in that a gap is provided between the outer circumferential surface of the pivot shaft and the shaft hole to allow rotation of a predetermined angle.

(2) Effect According to the above configuration, the rotation center of the lock lever is the center of the arcuate projection, so the radius of the projection is smaller than the radius of the pivot and the frictional resistance between the projection and the inner surface of the shaft hole. The product of is the resistance moment when rotating the lock lever. Therefore, this resistance moment is smaller than that of the conventional structure, and the lock lever can be rotated with a correspondingly smaller release force. Moreover, since the pivot can be given a sufficiently large cross-sectional area, sufficient strength can be ensured.

(3) Examples Embodiments of the present invention will be described below with reference to the drawings.

1 to 14 show a first embodiment of the present invention. First, in FIGS. 1 and 2, a buckle 1 for connecting a seatbelt connection fitting is fixed to the upper end of a support rod 2. As shown in FIGS. The support rod 2 is constructed in a flexible manner, the main elements being a metal cable 3 folded back into a U-shape at the lower part, and a synthetic resin tube 4 covering the cable 3.

A circular cable terminal 5 is fitted into the lower folded portion of the cable 3, and a support plate 6 is caulked thereto.

As shown in FIGS. 2A to 4, the support plate 6 has upstanding walls 6a and 6b on both front and rear sides and on the lower side.

The left and right upright walls 6a and 6b have their upper ends constricted so as to cooperate with the cable terminal 5 to clamp the cable 3, and the lower upright wall 6C has a wire 7 as a cable. The upper terminal 7a of is connected.

The support plate 6 is inserted into a sheath-like frame 8 so as to be movable up and down, and when the support plate 6 is lowered, the support rod 2 is drawn into the frame 8, and the seat belt connected to the buckle 1 is tensioned. .

In order to guide the lifting and lowering of the support plate 6, a retaining pin 9 protruding from one side of the cable terminal 5 is slidably engaged with a vertically long guide groove 10 formed on one side wall of the frame 8. .

The frame 8 is divided into a channel-shaped frame main body 8a and a side plate 8b that closes the open side of the frame main body 8a. Both 8a and 8b are bonded to each other by penetrating through and caulking.

Referring again to FIGS. 1 and 2, a pair of front and rear mounting flanges 12 and 13 are integrally provided at the lower part of the frame body 8a, and the bolt holes 14 and 14 of these mounting flanges 12 and 13 are integrally provided.
The frame 8 is fixed to an anchor portion of a seat or floorboard inside the vehicle by bolts 15° 15 inserted through the frame 8.

A synthetic resin cover 16 is attached to the frame 8 to cover it.

In FIGS. 1, 2, and 5, a guide pulley 17 is provided at the lower part of the sheath-like part of the frame 8, and a mounting collar 13 is provided at the rear part.
Drive pulleys 18 are each supported by a shaft, and a wire 7 connected to the support plate 6 is connected to a lower terminal 7b to a drive boob IJ18 via a guide boob IJ17.

The drive pulley 18 is integrally equipped with a pulley shaft 18a, and this pulley shaft 18a has a shaft hole 19 drilled in the rear mounting collar 13 and a boss 20a of a cup-shaped spring case 20 attached to the mounting collar 13. Both ends are rotatably supported by.

The spring case 20 houses a mainspring spring 21 that surrounds the pulley shaft 18a, and its inner end is connected to the pulley shaft 18a.
a, and the outer end is locked to the spring case 20, respectively. This spiral spring 21 is stored with force so that the drive pulley 18 can exert a force in the direction in which the wire 7 is wound up, that is, in the direction in which the support rod 2 is lowered.

In FIGS. 2 to 4, a one-way movement blocking device 23 is provided between the support plate 6 and the frame body 8a, which allows the support plate 6 to descend but prevents it from rising. This device 23 includes a swing claw 24 pivotally supported on the support plate 6, a large number of locking teeth 25, 25, etc. formed in tandem on the frame body 8a, and engagement between these locking teeth. The spring 26 urges the swing claw 24 in the direction shown in FIG.

As clearly shown in FIG. 2A, the swinging claw 24 consists of a wide claw portion 24a extending substantially vertically, and a protrusion 24b bent from the lower end of the claw portion 24a and extending substantially horizontally. The lower end of the claw portion 24a is swingably supported by the step portion 27 of the support plate 6, and the protrusion 24b extends until it passes through the through hole 28 of the support plate 6 and further through the guide groove 10.

In this way, the swinging pawl 24 can be moved to the support plate 6 without using a pivot.
is supported by

The spring 26 is attached to the bottomed hole 2 formed in the cable terminal 5.
9 and urges the claw portion 24a in the direction of engagement with the locking teeth 25, 25, . . . By artificially pushing down the protrusion 24b that protrudes outside the guide groove 10,
The claw portion 24a is moved against the force of the spring 26 by the locking teeth 25, 25.
It is possible to separate from...

The cover 16 is provided with a working window 30 at a portion corresponding to the guide groove 10, and the protrusion 24 is inserted through this working window 30.
0 work window 30 where the above operation of b is performed
is normally closed by a lid 31.

The locking teeth 25, 25... are formed by partially cutting and raising the side wall of the frame 8 into a sawtooth shape with the tooth tips facing downward. Therefore, when the claw portion 24a of the swinging claw 24 comes into contact with the tooth tip of each locking tooth 25, the support plate 6 is prevented from rising, and the swinging claw 24 slides on the slope of each locking tooth 25 to support the support plate 6. Lowering of the plate 6 is allowed.

In FIG. 6, between the support plate 6 and the frame 8,
During normal times, the support plate 6 is locked at the upper limit, but a locking device 32 is provided to release the lock in an emergency such as during braking or a collision. This device 32 includes a rotating latch 33, a lock lever 34, a lock spring 35, a release lever 36, a weight 37, and a return spring 38 as locked members.

The rotating latch 33 has an upper short arm 40 and a lower long arm 41.
It is formed into a bell crank shape, and is pivotally supported on the outer surface of the side plate 8b of the frame 8 by a pivot 39. Further, the short arm 40 is formed into a bifurcated shape with a long upper arm 40a and a short lower arm 40b.

The engagement pin 9 is detachably held by the lower arms 40a and 40b. A non-operating position B of the rotary latch 33 that releases the retaining pin 9 is regulated by a stopper 42 formed on the frame 8.

On the other hand, the long arm 41 is provided with a pair of upper and lower locking projections 43, 44 projecting forward at its lower end, and its lower end surface is a cam surface 41a.

The lock lever 34 is attached to a pivot shaft 45 below the rotary latch 33.
A pair of lever plates 46. are pivotably supported on the outer surface of the side plate 8b and are opposed to each other with the long arm 41 in between.
46. ! : It consists of a pin 47 that integrally connects both lever plates 46, 46 to each other, and a roller 48 with a ball bearing fitted in this pin 47 between both lever plates 46, 46. A lock lever configured like this
34 has high rigidity, and the support rigidity of the pin 47 supported at two points is also high, so even if a large external force is applied, the roller 48 supported by this pin 47 can always maintain a proper posture.

Now, as shown in Figures 10 to 12, lock lever 3
The shaft support structure of No. 4 will be explained. The pivot 45 is fixed to the frame 8 by caulking a small shaft 45a at one end. A shaft hole 49 of the lock lever 34 is fitted into the pivot shaft 45, and a flange 45b is formed at the other end of the pivot shaft 45 to prevent it from coming off.

A roller 48 is provided on the outer circumferential surface of the pivot 45 with its center sandwiched therebetween.
A semi-cylindrical recess 5 having a sufficiently smaller diameter than the pivot 45 on the opposite side.
6 is provided, and a fulcrum roller 57 is rotatably fitted into this recess 56. A portion of the fulcrum roller 57 protrudes from the outer peripheral surface of the pivot shaft 45 to form an arcuate projection 57a, and this projection 57a is supported by the support surface 58 of the shaft hole 49.

The shaft hole 49 is formed to have a diameter sufficiently larger than that of the pivot shaft 45, and the outer circumference of the shaft hole 45 is normally set so that the lock lever 34 does not come into contact with the inner surface of the shaft hole 49 until the lock lever 34 rotates by a predetermined angle around the center of the fulcrum roller 57. A gap g is provided between the surface and the inner peripheral surface of the shaft hole 49.

The roller 48 of the lock lever 34 is adapted to releasably engage between the locking protrusions 43 and 44 of the rotary latch 33. Thus, the engagement surface 44a of the lower engagement protrusion 44 is
When the rotary latch 33 is at the predetermined operating position A, it is formed into an arcuate surface centered on the fulcrum roller 57. still,
In the illustrated example, the pivot shaft 45 of the lock lever 34 is disposed away from the retaining surface 44a on the opposite side to the direction of rotation of the rotary latch 33 to the non-operating position B.

As shown in FIGS. 7 and 9, the pin 47 projects long from one lever plate 46 and projects into a notch 50 provided in the side plate 8b of the frame 8. As shown in FIGS.

This notch 50 controls the locked position WC and unlocked position fD of the lock lever 34 by receiving the pin 47 with its upper and lower end walls.
In the locking position C, the roller 48 engages between the retaining protrusions 43 and 44 to hold the rotary latch 33 in the operating position A, and the locking lever 34 is in the unlocked position (when the roller 48 is adapted to separate from both engaging protrusions 43 and 44.

This lock lever 34 is normally biased and held at the lock position C by a lock spring 35.

The release lever 36 is swingably supported by a bracket 51 protruding from the front surface of the frame 8 about a pivot 52 . The lever 36 is formed into a bell crank shape by a horizontal arm 36a facing the side surface of the portion of the pin 47 that protrudes outside the lever plate 46, and a vertical arm 36b extending downward from the base end of the horizontal arm 36a. A cylindrical weight 37 is pivotally supported at the lower end of the vertical arm 36b.

The bracket 51 is provided with a pair of stoppers 53 and 54 that receive the weight 37 and regulate the holding position E and release position F of the release lever 36.
At the holding position E of No. 6, the horizontal arm 36a is spaced a certain distance from the circumferential surface of the pin 47! (See FIG. 6A), and in the release position F, the horizontal arm 36a rotates the lock lever 34 to the unlocked position via a pin 47.

The release lever 36 is normally biased and held at the holding position F by a return spring 38.

In FIG. 1, reference numeral 55 is a stopper formed on the frame 8 to regulate the lower limit of the support plate 6.

Next, mainly Fig. 1, Fig. 10, Fig. 13 and Fig. 14
The operation of this embodiment will be explained with reference to the drawings.

FIG. 1 shows the normal state in which the support rod 2 of the buckle 1 is pulled up to its upper limit. In this state, release lever 3
6 is held in the holding position by a return spring 38. Also, the lock lever 34 is moved to the locked position C by the lock spring 35.
Accordingly, the roller 48 of the lock lever 34
is engaged between the locking protrusions 43 and 44 of the rotary latch 33 to hold the rotary latch 33 in the operating position A. This rotary latch 33 holds the retaining pin 9 between the upper and lower arms 40a and 40b of the short arm 40, and locks the support rod 2 at its upper limit.

Therefore, the wire 7 connected to the support plate 6 has
A tension state is provided by the driving force of the drive pulley 18 by the mainspring spring 21.

In this case, in FIG. 1, a clockwise moment acts on the rotating latch 33 from the engagement pin 9 to the short arm 40 due to the force of the mainspring spring 21, but this moment causes the engagement of the long arm 41. The pressing force applied from the surface 44a to the roller 48 of the lock lever 34 is applied to the lock lever 34 because the retaining surface 44a is an arcuate surface centered on the fulcrum roller 57 of the pivot shaft 45 as described above. roller 5
It acts as a simple tensile force whose line of action is a straight line passing through the center of roller 7 and roller 48, and the force is received by pivot shaft 45 via fulcrum roller 57. Therefore, the set load of the lock spring 350 can be set to a relatively small value that simply holds the lock lever 34 in the lock position C without being affected by external disturbances such as vibrations. Further, since the pivot shaft 45 can be given a sufficiently large cross-sectional area as in the conventional case, it can sufficiently withstand the tensile force.

Further, by adjusting the lever ratio between the short arm 40 and the long arm 41 of the rotary latch 33, the tensile force acting on the lock lever 34 from the rotary latch 33 can be suppressed to a minimum, thereby reducing the load on the pivot shaft 45.

In this state, even when the occupant inserts and connects the seatbelt connecting fitting pulled out from the retractor into the buckle 1 in order to put on the seatbelt, the support rod 2 remains at the upper limit position.

While driving the vehicle, if the vehicle decelerates above a certain value due to sudden braking or a collision, the weight 37 senses this and returns the release lever 36 to the release position F against the force of the spring 38. Rotate it toward the camera.

The horizontal arm 36a of the release lever 36 and the lock lever
Since a gap 1 is initially provided between the release lever 34 and the pin 47, the rotation of the release lever 36 is accelerated without any resistance from the lock lever 34 while the gap 2 is being closed. Therefore, when the horizontal arm 36a hits the bin 47, it exerts a relatively large impact force, and this hammer action allows the lock lever 34 to resist the frictional resistance existing around the fulcrum roller 57 of the pivot shaft 45 and the force of the lock spring 35. The roller 48 is reliably rotated to the unlocked position, and the roller 48 smoothly rolls out from the engagement surface 44a of the lower engagement projection 44.

In particular, since the rotation center of the lock lever 34 is the center of the fulcrum roller 57, the radius r' of the fulcrum roller 57, which is smaller than the radius r of the pivot shaft 450, and the outer peripheral surface of the fulcrum roller 57 and the shaft hole 4
9 The product fr' with the frictional resistance f between the inner peripheral surfaces is the lock lever
34 is the resistance moment when rotating to the unlocked position. Therefore, this moment of resistance f-r'
is smaller than the resistance moment fr of the conventional structure, and the lock lever 34 can be rotated with a correspondingly smaller release force, improving the responsiveness of the lock lever 34 to the release force.

Then, when the roller 48 comes off the engagement surface 44a,
Since the lock lever 34 no longer has the locking function for the rotating latch 33, the rotating latch 33 is moved as shown in FIG. The lock lever 34 is rapidly rotated toward the non-operating position B while being pushed to the non-locking position.

Incidentally, the turning force of the lock lever 34 to the unlocked position by the rotation latch 33 is extremely strong, and also acts to separate the roller 48 from the release lever 36, so that the fulcrum roller 57 and the support surface 58
There is no problem even if the pivot 45 and the inner surface of the shaft hole 49 come into contact with each other, and the rotary latch 33 is not resisted by the repulsive force of the return spring 3B of the release lever 36 or the inertial force of the weight 37. It can be quickly rotated to the non-operating position B.

From this, the rotation angle between the holding position E and the release position F of the release lever 36 is such that the release lever 36 rotates the lock lever 34 to the point where the roller 48 disengages from the engagement surface 44a. It will be appreciated that it may be set to a minimum angle.

When the rotary latch 33 rotates to the non-operating position B, the energy of the mainspring spring 21 is released all at once, and the drive pulley 18 rapidly winds up the wire 7 to draw the support rod 2 into the frame 8, and the buckle 1 is quickly pulled out. lower to. At the same time, the retaining pin 9 moves the rotary latch 33 to the inoperative position B.
It separates from the short arm 40 while rotating it.

In this case, since the wire 7 is kept under tension since the rotary latch 33 is in the operating position A, there is no time delay in transmitting the driving force to the support rod 2 of the drive boo 1J18.

On the other hand, since the retractor (not shown) is locked by a known action and prevents the seat belt from being pulled out, the lowering of the buckle 1 applies tension to the seat belt.

In this way, slack in the seat belt due to stretching of the seat belt itself or tightening by the tractor is immediately removed, and the restraining force of the seat belt is accurately exerted on the occupant.

When the support plate 6 is lowered, in the one-way movement prevention device 23, the swing claw 24 slides on the slope of each locking tooth 25 and lowers together with the support plate 6, but then the forward movement load of the occupant is applied to the seat belt. When the buckle 1 is about to be pulled up, the swinging pawl 24 engages with the tips of the opposing locking teeth 25, restraining the buckle 1 from being pulled up, and maintains the tensioned state of the seatbelt. be able to.

When there is no deceleration from the vehicle, as shown in Figure 14,
The release lever 36 is returned to the holding position by the force of the return spring 38, and the lock lever 34 is accordingly returned to the lock position C by the force of the lock spring 35 while leaving the rotary latch 33 in the non-operating position B.

To pull up the buckle l to its upper limit again, remove the lid 31 and use a suitable tool such as a screwdriver to push the protrusion 24b of the swinging claw 24 through the working window 30 of the cover 16.
4a is released from the locking teeth 25, 25... and in this state, the buckle 1 is pulled up. During this time, the wire 7 is pulled up by the support plate 6, so the wire 7 is pulled out from the drive pulley 18, rotates the boot IJ18, and causes the spiral spring 21 to store force again. on the other hand,
The retaining pin 9 rising together with the support plate 6 pushes up the upper arm 40a of the short arm 40 of the rotary latch 33 and
3 in the counterclockwise direction in FIG.
reaches the initial operating position A. During this time, the cam surface 41a at the tip of the long arm 41 once pushes down the roller 48 of the lock lever 34 against the force of the lock spring 35, and the cam surface 41a
When the latch passes through the roller 48, the roller 48 engages between the engagement protrusions 43 and 44 of the long arm 41 by the force of the lock spring 35, and the rotary latch 33 is held at the initial operating position KA.

FIG. 15 shows a second embodiment of the present invention, which has the same structure as the previous embodiment except that a semi-cylindrical concave surface is formed on the inner surface of the shaft hole 49 as a support surface 58 for the fulcrum roller 57. 16 and 17, in which parts corresponding to those in the previous embodiment are denoted by the same reference numerals, show a third embodiment of the present invention. This is the opposite of the second embodiment, and in the figure, the same reference numerals are given to the parts corresponding to those of the second embodiment.

FIG. 18 shows a fourth embodiment of the present invention, in which a fulcrum roller 57 is rotatably mounted on a pivot shaft 45 fixed to a lock lever 34, and a support surface 58 for the fulcrum roller 57 is shown.
The frame 8 is provided with a shaft hole 49 on the inner circumferential surface thereof. The rest of the structure is the same as that of the first embodiment, so the same reference numerals are given to the parts corresponding to those of the first embodiment in the drawings.

FIG. 19 shows a fifth embodiment of the present invention.

This is the same as the fourth embodiment except that a fulcrum roller 57 is rotatably mounted on the inner wall of the shaft hole 49 of the frame 80, and a semi-cylindrical support surface 58 for supporting the roller is formed on a pivot 45 fixed to the lock lever 34. Since they have the same configuration, parts corresponding to those of the fourth embodiment in the figures are given the same reference numerals.

In each of the above embodiments, the arcuate protrusion 57a may be formed integrally with the pivot shaft 45 or the inner wall of the shaft hole 49, but it is preferable to form it with a rotatable fulcrum roller 57 as in the illustrated example. However, since the frictional resistance f between the arcuate protrusion 57a and the bearing surface 58 is small, this is effective in further reducing the resistance moment f-r' of the lock lever 34.

C0 Effects of the Invention As described above, according to the present invention, on the line of action of the force acting on the lock lever from the locked member due to the spring force, one and the other of the outer circumferential surface of the shaft and the inner circumferential surface of the shaft hole. An arcuate protrusion and a bearing surface having a diameter smaller than that of the pivot shaft are provided, and the support surface is rotatably abutted against each other. Since it is provided between the shaft hole and the shaft hole, it provides the specified strength to the shaft.
, the resistance moment when the lock lever is rotated can be reduced, and the responsiveness of the lock lever to the release force can be improved.

[Brief explanation of the drawing]

1 to 14 show a first embodiment of the present invention, and FIG. 1 is a partially cutaway side view of an automobile seat belt tensioning device equipped with a lock lever shaft support structure of the present invention;
Figure 2 is a sectional view taken along the line ■-■ in Figure 1, Figure 2A is an exploded perspective view of the main parts of Figure 2, and Figure 3 is an enlarged sectional view taken along the line ■-■ in Figure 2. and FIG. 5 shows the lines IV-IV and V- in FIG.
V line enlarged sectional view, Fig. 6 is an enlarged view of the main part of Fig. 1, Fig. 6A
The figure is a side view showing the relationship between the lock lever and the release lever, Figure 7 is a partial side view of the frame in Figure 6, and Figures 8 and 9 are cross sections taken along the ■-■ line and IX-IX line in Figure 6. Figure 10 is an enlarged view of the main part of Figure 6, Figure 11 is an enlarged view of the main part of Figure 1.
Figure 0 is a sectional view taken along the line XI-XI, Figure 12 is a perspective view of the pivot of the lock lever, Figures 13 and 14 are explanatory views of the action, and Figure 15 shows the second embodiment of the present invention. FIG. 16 is an enlarged view similar to FIG. 10, showing a third embodiment of the present invention; FIG. 17 is a sectional view taken along the line X--X in FIG. 16; Fig. 18 shows a fourth embodiment of the present invention and is an enlarged view similar to Fig. 10, Fig. 19 shows a fifth embodiment of the invention and is an enlarged view similar to Fig. 10; The figure is an explanatory diagram of a conventional structure. 8...Frame, 33...Rotary latch as a locked member, 34...Lock lever 145...[11
, 49... shaft hole, 57... fulcrum roller, 57a...
・Arc-shaped projection, 58...Supporting surface, g...Gap Patent applicant Honda Lock Co., Ltd.

Claims (1)

[Scope of Claims] A lock that can rotate between a locked position in which a locked member (33) is restrained against a spring force acting thereon and an unlocked position in which the locked member (33) is released. Lever (3
4) on the frame (8), a pivot (34) fixed to one of the lock lever (34) and the frame (8) is used.
45) fitted into the shaft hole (49) provided on the other side,
In the lock lever shaft support structure, the locked member (
The pivot shafts (45) are rotatably abutted against each other on the line of action (L) of the force acting on the lock lever (34) from
) and a bearing surface (58) each having a smaller diameter, and a gap (g) that allows the lock lever (34) to rotate by a predetermined angle around the center of the arcuate projection (57a). ) is provided between the outer peripheral surface of the pivot shaft (45) and the shaft hole (49).