JPS5819303B2 - Jidou Belt Makiage Kyoujisouchi - Google Patents

Description

[Detailed description of the invention] The present invention is a rapid locking function for automobile safety belts.

The present invention relates to an automatic belt winding and clamping device having the following features.

A three-point automatic safety belt used today is shown in FIG. 1 in a car.

Automatic belt hoisting devices (hereinafter simply referred to as automatic devices), such as those used in today's three-point automatic safety belts for vehicle occupants, have a belt fixing point and a belt direction change point.
The belt, which is stretched around the passenger between B and C (see Figure 1), is continuously wound onto the hoisting frame (located at the point) with a pullback force Fw.
The several-layer belt is constantly attached to the passenger's upper body between points A and B, but the passenger cannot bend his body forward or move freely against this pulling force FW. is possible.

According to five known requirements that this automatic device must satisfy, the retraction force Fw must be between 0.2 and 0.5 Kp.

Furthermore, the locking action of the safety belt is activated in the following cases: 1. When a vehicle deceleration of a p > 0.4 g occurs in any horizontal direction; 22. The belt moves away from the reel of the automatic device aGB > 0.5
should occur when pulled with a belt acceleration of g, where aF=vehicle deceleration aGB''belt acceleration g=9.81 town's2 - acceleration of gravity.

Devices are already known which serve to clamp the belt towards the bobbin.

However, this device has the major disadvantage that the belt rests on the brake surface of the lever under continuous winding tension, which causes wear and tear, and hence the disadvantage that the retracting force is abnormally high.

Furthermore, this known device does not allow a sufficiently reliable clamping effect to be achieved.

Moreover, the installation of the parts requires a considerable amount of space due to their location.

These known devices are unable to hold the belt firmly in all positions based on vehicle deceleration or belt acceleration.

A number of devices have been proposed for clamping the belt behind the hoist by a wedging action, but these devices have the disadvantage that once the belt has been clamped, it can no longer be released.

Furthermore, during the clamping process, relative movement occurs between the belt and the clamping surface, resulting in tearing of the belt.

The object of the present invention is to improve the automatic belt clamping device mentioned at the beginning in the following way: the belt is reliably clamped, the belt is released again when the load is removed after clamping, and the belt and the clamping device are not connected to each other during the clamping operation. The object of the present invention is to eliminate the risk of the belt being torn in a direction transverse to the normal force direction due to relative movement between the surfaces.

According to the present invention, the above problem is solved by the following configuration.

That is, a direction change device serving as a first direction change point of the belt and a direction change device serving as a second direction change point of the belt are provided between the clamps with the pivot as the center of rotational movement, and the two direction change devices are provided. providing one of a pair of clamping surfaces located between the clamping bars and facing each other across the belt; and providing the clamping bar with a spring for releasing the clamping action of the clamping surfaces; and the clamping coefficient μK of the clamping surface, at least the length b from the axis to the center of the clamping surface
and the length a from the pivot to the second deflection device b/
This is solved by setting a.

A possible embodiment of the movement described above is to pivot the clamping lever so that the clamping surface on the lever side is arranged perpendicular to the tangent for the movement about this pivot point.

For a constant clamping factor μ at the optimum leverage ratio b/a mentioned above, the clamping normal force should be kept as small as possible so as not to prevent the belt from being held tightly between the clamping surfaces.

By keeping the normal forces as small as possible in this way, the belt fabric is protected.

According to the invention, the benefits are even greater by supporting both clamping surfaces in a tiltable manner.

In addition to this clamping movement, this also achieves the objective of clamping with as pure a vertical force as possible.

This is achieved, for example, by pivoting the clamping surface on the clamp or the housing and supporting it in a tiltable manner.

In this case, the pivoting and tilting axis should be arranged parallel to the pincer pivoting axis and essentially transverse to the direction of belt withdrawal.

A further advantageous embodiment of the invention provides a bobbin locking device which is sensitive to motor vehicle acceleration and is known per se, acting on the gripper.

For this purpose, it is possible to increase the belt withdrawal force, for example by locking the reel, so that the gripper can be moved into the gripping position against the force of its return spring. It is made to produce a pinching effect.

After this belt clamping action has taken place, the clamping normal force only depends on the belt withdrawal force, so that the bobbin locking device can be momentarily relieved.

Other advantages, features, applications, etc. of the invention will become apparent from the following detailed description with reference to the figures.

The belt 1 emerges from a bobbin 2 under spring tension, is deflected by a deflection device 3, and is guided across a pivoting pincer 4 having a pivot 7 to a deflection device 5, from where it is directed upwardly into this deflection device. Leave the automatic device.

The deflection devices 3 and 5 can be constructed as rollers or simple steel bends.

The pivoting pincer 4 is brought into its rest position (first position) with a constant spring characteristic and spring tension by one or more springs 6.
(Fig.), allowing the belt to be freely wound up and unwinded.

The clamping action is produced by tilting the clamping lever 4 upwards about the pivot 7 against the force of the spring 6 and tightening the belt 1 between the clamping surfaces 8.

One of the two clamping surfaces 8 can be mounted in such a way that it can be tilted around a pivot 8a and thus transversely to the direction of belt withdrawal (FIG. 6).

The length from the pivot 7 to the direction change device 5 is a, and the pivot 7
The length from to the clamping surface 8 is b, and the direction changing device 5
With this lever ratio, as the tensile force F5 of the belt 1 acts on the rotating clamping lever 4, a large clamping force F8 corresponding to the lever ratio is generated at the center point of the clamping surface (in this case, for example, the lever ratio b:a-= If the ratio is 1:4, F8=4F5).

Assuming that there is no frictional force in the deflection device 5, the clamping normal force F8 must be F8 in order to obtain a complete clamping action.
Considering the leverage ratio compared to 5, it must be the following size, that is, the size should be such that the relationship of deterrent force (frictional force) FR - F5 occurs considering the clamping coefficient (friction coefficient) μK. There must be.

This means that F8·μ is ≧F5, or in the example above, that when a complete clamping action is to take place, μ is greater than 0.25 for a leverage ratio of 1:4. It means that there must be.

FIG. 4 shows an example of a reel locking device configured to initiate a clamping action after the vehicle deceleration in any direction reaches 0.4 g.

A small pendulum 9 with a pivot 9a presses a claw member 10 with a pivot 10a against a gear 11 attached to the shaft of the winding frame 2, thereby locking the shaft of the winding frame 2.

All actuating members for these operations can be small and light.

The reason for this is that these actuating members provide only a slight restraining force which overcomes the spring force of the return spring 6 of the turning clamping arm 4 so that the winding clamping arm 4 is in the clamping position.

Thereafter, F8 increases as F5 increases, ensuring clamping of the belt so that the locking device can be momentarily released.

With reference to FIG. 2, the clamping action at belt accelerations greater than 0.5 g will be explained.

The return spring 6 of the clamping arm 4 has its spring characteristics and spring tension, and the clamping arm resists the force of the spring 6 due to the friction in the direction changing devices 3 and 5, the pullback force Fw (Fig. 1), and the inertia of the winding frame. It is configured to tilt and move to the clamping position.

The clamping device 23 does not have a winding frame 2 but a separate housing 21.
If it is located inside (FIG. 5), the clamping device 23 can be mounted anywhere on the B-pillar of the motor vehicle, most preferably together with the turning ring.

The length of belt extension for this purpose changes, making it possible to effectively utilize the forward positional deviation that is most often expected by the occupant in the event of an accident.

All of the above advantages can also be obtained in combination with an automatic band winding device of known construction.

Embodiments of the invention include the following.

(1) In the scope of the claims, one of the two clamping surfaces 8 is supported so as to be tiltable across the direction in which the belt is pulled out.

(2. In the scope of the claims, a device comprising a reel locking device 2, 10, 11 sensitive to automobile acceleration, and configured such that the reel locking device acts on the clamping lever 4.

(3) A device in which the gear 11 is fixed to the winding frame 2 in accordance with item (2) O above.

(4) In the scope of the claims, a device in which the clamping device 23 consisting of the clamping lever 4, the return spring 6, and the direction changing devices 3, 5 is housed in a separate housing 21.

[Brief explanation of drawings]

Figure 1 is a diagram showing the state in which the automatic clamping device is attached to a three-point automatic safety belt, and Figure 2 is a partial cross-sectional view of the first embodiment of the automatic clamping device, showing the clamping surface, clamping rod, and winding frame. Fig. 3 shows the arrangement of the two parts in one housing.
Figure 4 is an enlarged view showing the upper part of the figure, Figure 4 is a diagram showing the mechanism for causing the locking action of the winding frame via the automobile acceleration sensing device, Figure 5
The figure shows an embodiment in which the automatic clamping device is installed in a housing separated from the winding frame, and FIG. 6 is a sectional view showing another embodiment of the automatic clamping device in which the clamping surface is pivotally mounted. 1...Belt, 2...Reel frame, 3, 5...
... Direction change device, 4 ... Articulation clamping lever, 6 ... Spring, 7° 8a, 9a, 10a ...
...Pivot, 8...Pinching surface, 10...
Claw member, 11-... Gear, 21... Housing, 23... Clamping device.

Claims (1)

[Claims] 1. In an automatic belt hoisting and clamping device having a quick locking function for automobile safety belts, a direction changing device 3 serving as a first direction change point of the belt 1 and a belt 1 are attached to a clamping lever 4 whose rotational movement is centered around a pivot shaft 7. A direction changing device 5 serving as a second direction changing point is provided, and a pair of clamping surfaces 8, 8 are located between the two direction changing devices 3, 5 and face each other with the belt 1 sandwiched between the clamping rod 4. one of the clamping surfaces 8 is provided;
The clamping lever 4 is provided with a spring 6 for releasing the clamping action of the clamping surfaces 8, 8, and the clamping coefficient μK of the clamping surface β is
At least the length b from the pivot 7 to the center of the clamping surfaces 8, 8
and the length a from the pivot shaft 7 to the second direction changing device 5, the ratio of which is b/a.