JPH0214533Y2 - - Google Patents

Description

[Detailed description of the invention] [Purpose of the invention] (Field of industrial application) The present invention relates to a safety device for a stick-type handbrake for vehicles.

(Prior Art) As is well known, a stick-type handbrake for a vehicle is equipped with a plunger with a handle attached to one end, which is slidable in the axial direction relative to the vehicle body and rotatable around the axis. A brake actuation wire is connected to the end directly or indirectly through a lever, etc., so that the brake is actuated by the driver holding the handle and pulling the plunger, and the plunger is pulled against the brake reaction force. A locking mechanism that holds the plunger in the pulled-out position and releases this holding action by rotating the plunger in one direction (generally, a locking mechanism that includes a ratchet arranged in an axial direction on the surface of the plunger and a mechanism that is pivotally supported by the vehicle body and engages with the ratchet) (consisting of a spring-loaded pole)
It will be attached.

(Problem to be solved by the invention) In such a stick-type handbrake, if the handle is fixed on one end of the plunger, there is a possibility that the driver, etc. may accidentally touch the handle while the brake is applied. When the handle is rotated in one direction, the plunger also rotates and the locking mechanism releases the plunger from holding its position.
There is an inconvenience that the plunger is pulled back by the brake reaction force and the braking action is released, and therefore the braking action must be performed again.

Various structures are already known as safety devices to eliminate such inconveniences. One type of safety device is one that prevents the plunger from being rotated by causing the handle to spin idly on the plunger when the driver accidentally touches the handle and applies rotational force to the handle. It is being In this type of vehicle, it is desirable that there be no limit to the angle at which the steering wheel can turn freely in order to minimize the risk described above, and it also makes it easier to operate the brake when applying and releasing the brake, as well as to prevent the locking. In order to ensure the operation of the mechanism, it is usually desirable for the handle to be held in a specified positional relationship with the plunger, and furthermore, when the brake action is released, the handle and plunger are reliably connected so that they rotate together. It is also desirable that the handle has good durability and that there is no need to enlarge the grip portion of the handle. However, there is no conventional device that can satisfy all of these demands.

Therefore, the technical problem of the present invention is to satisfy all of the above-mentioned demands in the above-mentioned type of device.

[Structure of the idea]

(Means for Solving the Problems) The measures taken to solve the above-mentioned technical problems are that, in the stick-type handbrake for the vehicle, a handle protrudes from a part near one end of the grip part at right angles to the grip part. A sleeve and a bottomed cylindrical guide member with the sleeve fitted into the opening are fixed to either the handle shaft or one end of the plunger, and the other end is fixed to the handle shaft. The lock member is inserted into the guide member by slidingly passing through the bottom wall of the guide member in the axial direction, and is integrally coupled with a lock member that is slidably and rotatably fitted inside the guide member, and the lock member and the sleeve The opposing end surface has a plurality of troughs and a plurality of ridges for maintaining the rotational position of the handle relative to the plunger at a plurality of predetermined positions by the force of a compression spring interposed between the lock member and the bottom wall of the guide member. The cam surfaces are shaped so that a straight line on the rotating cam that passes through the center of the rotating cam surface is a continuous surface perpendicular to the central axis of the rotating cam, regardless of the direction; The end surface of the lock member facing the bottom wall of the guide member is provided with a plurality of notches and protrusions that engage when the handle is pulled only when the handle occupies the normal position among the prescribed positions with respect to the plunger. The plunger is formed asymmetrically with respect to the axis thereof, and the distance between the notch and the protrusion is set to be larger than the axial dimension of the rotary cam surface when the handle occupies the prescribed position with respect to the plunger.

(Operation and Effects of the Invention) In the present invention having such a configuration, under normal conditions, the rotational position of the handle relative to the plunger is kept at the normal position because the spring and the rotating cam surface of the locking member are engaged by the force of the compression spring. The grip portion of the handle is substantially horizontal, and one end and the other end thereof are located on the index finger side and little finger side of the driver's hand, respectively, which are held on the grip portion.

When the driver puts his hand on the grip of the steering wheel and pulls it to apply the parking brake, the bottom wall of the guide member and the end surface of the lock member come into contact with each other due to relative sliding between the lock member and the guide member, and this contact occurs. The plunger is also pulled together with the handle by the contact, and the parking brake activation cable is pulled to apply the parking brake, and the locking mechanism holds the plunger in the extended position to maintain the parking brake applied state. If the driver accidentally touches the steering wheel while the parking brake is applied and rotational force is applied, the plunger to which the brake reaction force is applied will have a relatively large resistance exerted by the lock mechanism, so the sleeve and lock will Slippage occurs between the rotating cam surfaces of the members, causing only the handle to rotate idly, preventing rotation of the plunger and preventing release of the parking brake action. Since the handle can be rotated freely many times, the risk of the parking brake being released inadvertently is extremely low. When the parking brake idles in this way, the handle moves toward the driver by the axial dimension of the rotating cam. Because the handlebar is shortened, when the handlebar hits something as it moves toward the driver, its movement is restricted, and this prevents sliding between the rotating cam surfaces, causing the plunger to rotate together with the handlebar. There is little possibility that the phenomenon of the rotating cam surface will occur, and any direction that passes through the center of the rotating cam surface with a straight line on the rotating cam surface is a continuous line perpendicular to the central axis of the rotating cam. By forming a surface, the locking member and sleeve always make line contact or approximate surface contact at two symmetrical points with respect to the axis, so the surface pressure on the rotating cam surface is low, resulting in less wear and durability. In addition, since an unbalanced load does not act on the handle, the frictional force between the lock member and the guide member does not become abnormally large, and the problem of idle rotation of the handle can be solved. If the rotating cam surface simply has a plurality of valleys and a plurality of peaks corresponding to the valleys, the locking member and the sleeve will not contact each other when both rotating cam surfaces are in contact, especially at the top of the peak. There is point contact at two symmetrical points with respect to the axis, and the surface pressure acting on the cam surface increases, making it easy to wear and reduce durability.

In addition, the rotating cam surface is formed so that a straight line on the rotating cam surface that passes through the center of the rotating cam surface becomes a continuous surface perpendicular to the central axis of the rotating cam, regardless of the direction. The radius of the roundness at the top of the surface can be set to a desired value to ensure a nimble turning of the steering wheel. In other words, since the surface pressure on the rotating cam surface can be lowered and durability can be improved, the radius of the roundness at the top of the mountain on the rotating cam surface can be set to a small value to an arbitrary value without worrying about an increase in surface pressure. After setting the rotation cam surface, the spring force resists the frictional force between the lock member and the sleeve so that the set axial dimension of the rotating cam surface is obtained and the lock member and sleeve are shifted from the specified positions. What is necessary is to determine the angles of the troughs and peaks of the rotary cam surface that coincide at the specified position so that the rotating cam surface can return to the specified position. Therefore, since the radius of the roundness at the top of the mountain on the rotating cam surface can be set as small as desired, the spring force will not cause the two rotating cam surfaces to slide along the rotating cam surface when they are in contact at the top of the mountain. The range in which this phenomenon can occur can be reduced, and the steering wheel can be turned easily. If the rotating cam surface simply has a plurality of valleys and a plurality of peaks corresponding to the valleys, the radius of the roundness of the top portion of the peak of the rotating cam surface is:
The axial dimension of the rotating cam surface is determined by the angles of the valleys and crests of the rotating cam surface that match the diameters of the locking member and sleeve at the specified positions.
As the radius becomes larger, the range in which the two rotary cam surfaces may contact each other at the top of the mountain and not rotate under the force of the spring is large, and a nimble idling operation of the handle cannot be obtained. To release the parking brake, first place your finger on the grip of the handle and pull it toward you until you feel a brake reaction force, then rotate the handle in a predetermined direction. At this time, if the rotational position of the handle relative to the plunger is at the correct position, the multiple protrusions of the locking member will engage with the multiple notches on the bottom wall of the guide member during the process of pulling the handle, and the handle and plunger will rotate together. Since the plunger is connected in such a way that when the handle is rotated, the plunger rotates and the locking mechanism releases the position of the plunger, so if the plunger and handle are returned while being pulled by the brake reaction force, the parking brake action is released. Additionally, if the rotational position of the handle relative to the plunger is other than the normal position, the protrusion on the locking member will not engage with the notch on the bottom wall of the guide member even when the handle is pulled, and the plunger will not rotate even when the handle is turned. As a result, the driver moves the steering wheel to its normal position and then operates it again to release the parking brake. Further, since the sleeve, guide member, locking member and compression spring are arranged outside the grip portion of the handle, the grip portion of the handle does not become bulky and impair operability.

〔Example〕

Hereinafter, one embodiment of the present invention will be described based on the drawings.

In FIG. 1, reference numeral 10 denotes a handbrake, and a plunger 12 with a handle 11 attached to one end is supported by a support 13 fixed to the vehicle body so as to be slidable in its axial direction and rotatable around its axis. At the other end of the plunger 12 is a support 1.
One end of a brake actuating wire 14 wound around a roller 15 pivotally connected to the handle 11 is connected, and the brake is actuated by holding the handle 11 and pulling the plunger 12 to the right in the drawing.
A ratchet 1 is installed on the surface of the plunger 12 as a lock mechanism to hold the plunger 12 in the pulled out position against the brake reaction force when the brake is applied.
2a are arranged in a row in the axial direction, and a pawl 16 corresponding to the ratchet 12a is pivotally connected to the support 13, and the pawl 16 is urged toward the surface of the plunger 12 by a spring 17. Thus, when the plunger 12 is pulled out to the right, the pawl 16 engages with the ratchet 12a to restrict the return of the plunger 12 and maintain the action of the plunger.
The engagement with 2a is released by rotating the plunger 12 in the direction of the arrow, and the braking action is released by returning the plunger according to the pulling back action of the plunger due to the brake reaction force while the plunger 12 is kept rotating. When this brake action is released, when the plunger 12 returns to near the return position, the pin 18 fixed to the plunger 12 engages with the cam surface 13a of the support 13, and this engagement causes the plunger 12 to move so that the ratchet 12a and the pawl 16 Forced into opposing rotational positions.

Next, a structure for preventing the plunger 12 from rotating even if a rotational force is accidentally applied to the handle 11 will be explained with reference to FIGS. 2 to 8. The handle consists of a grip part 11a made of synthetic resin and a grip part 11a made of synthetic resin.
It consists of an inner core metal 11b and a handle shaft portion 11c fixed to the core metal 11b. Handle shaft part 1
1c is perpendicular to the grip portion 11a and protrudes from a portion near one end (the upper end in FIG. 2) of the grip portion 11a. A sleeve 19 and a cylindrical guide member 20 with a bottom, into which the sleeve 19 fits into the opening, are provided at the tip of the handle shaft portion 11c.
It is fixed by a pin 21 press-fitted into a radial hole of the handle shaft portion 11c, the sleeve 19, and the guide member 20. One end of the plunger 12 is slidably and rotatably penetrated through the bottom wall 20a of the guide member 20 in the axial direction and inserted into the guide member 20, and is slidably fitted inside the guide member 20. It is integrally connected to the cylindrical locking member 22 which is fitted together. This connection is effected by a pin 25 press-fitted into a radial hole in the plunger 12 and locking member 22. A compression spring 23 is provided between the lock member 22 and the bottom wall 20a of the guide member 20.
is interposed via a washer 24 made of a material with low frictional engagement, and when the handle 11 is pulled to the right in FIG. 2 against the compression spring 23, the two protrusions 22b of the locking member 22 is guide member 2
The guide member 20 and the lock member 22 are engaged with the two notches 20b of the bottom wall 20a of the guide member 20, and the guide member 20 and the lock member 22 rotate together.
2c and the bottom wall 20a of the guide member 20 come into contact with each other, and the rightward movement of the guide member 20 in FIG. 2 is transmitted to the lock member 22. Figures 7a-7c and 8
As shown in the figure, the opposite end surfaces 22a and 19a of the lock member 22 and the sleeve 19 are formed as rotating cam surfaces having a W-shaped unfolded shape and two valleys and two peaks. The rotating cam surface 2 of the locking member 22 is
2a is pressed by the rotating cam surface 19a of the spring 19, and the handle 11 resists the rotational force caused by its own weight and vibrations while the vehicle is running, and shifts by 180 degrees from the normal position shown in FIGS. 1 to 3 or from this first position. It is designed to be held in a different predetermined position. These rotating cam surfaces 19a, 22a are
Any straight line on a that passes through the center of the rotary cam surfaces 19a, 22a is perpendicular to the central axis of each rotary cam surface 19a, 22a, regardless of the direction.
That is, as shown in FIGS. 7a to 7c as a representative example of the sleeve 19, the rotary cam surface 19a passes through the axis and points at any arbitrary point (for example, point a, point b, point c, point d).
The straight line passing through the point) is perpendicular to the axis. Note that the rotating cam surface 22a is the same as the rotating cam surface 19.
It is similarly formed to match a. Second
The distance between the protrusion 22b of the lock member 22 and the notch 20b of the guide member 20 in the figure is the sliding amount A of the guide member 20 (rotary cam surface 1
9a, 22a) is larger than the value (A
+α).

Note that the rotation cam surface 19 is compressed by the compression spring 23.
The transmission torque generated between the sleeve 19 and the locking member 22 by pressing a and 22a, the locking member 22, the handle shaft portion 11c, and the guide member 20
The transmission torque generated between these members due to the friction of the sliding parts of the washer 24 and the compression spring 23
The sum of the transmitted torque generated by the friction of both ends of the spring 22 and the contact portion with the guide member 20 is greater than the torque of the plunger 12 required to disengage the pawl 16 and the ratchet 12a in FIG. Of course it is small.

Further, the two protrusions 22b of the locking member 22 and the two notches 20b of the guide member 20 are provided asymmetrically with respect to the axis, so that when the rotational direction position of the handle 11 with respect to the plunger 12 is at the specified position, Even if the handle 11 is pulled, the protrusion 22b and the notch 20a do not engage with each other.

With the structure as described above, when the driver holds the handle 11 and pulls it to the right in FIG. Slide to the right in Figure 2 and lock member 2.
2 contact portion 22c and the bottom wall 20a of the guide member 20
are in contact with each other, whereby the tensile force applied to the handle 11 is transferred from the guide member 20 to the lock member 2.
2 and the pin 25, and the plunger 12 is also slid to the right in FIG. 2, so that the brake is applied.

When the handle 11 is released after applying the brake, the force of the compression spring 23 returns to the state shown in FIG. 2. Therefore, even if, for example, a part of the driver's body touches the steering wheel 11 and a large rotational force is applied to the steering wheel 11, the rotating cam surface 22a is pressed against the rotating cam surface 19a by the force of the compression spring 23, etc. Since the generated torque transmitted between the plunger 12 and the handle shaft portion 11c is smaller than the torque required to disengage the pawl 16 and the ratchet 12a shown in FIG.
The sleeve 10 and the guide member 20 simply rotate idly, and the plunger 12 does not rotate, so that the braking action is maintained. At this time, the handle 11 moves toward the driver by the axial dimension of the rotating cam surfaces 19a, 22a, but the rotating cam surfaces 19a, 22a
Since the rotating cam surfaces 19a and 22a have a plurality of valleys and a plurality of peaks, and the axial dimensions of the rotating cam surfaces 19a and 22a are shortened, there is no possibility that the handle 11 will hit something in the process of moving toward the driver and restrict its movement. This reduces the possibility that the plunger 12 will rotate together with the handle 11 because sliding between the rotating cam surfaces 19a and 22a becomes impossible, and the rotating cam surfaces 19a and 22a are The straight line on each rotating cam surface 19a, 22a that passes through the center of the rotating cam surface 19a, 22a is a continuous surface perpendicular to the central axis of each rotating cam surface 19a, 22a, regardless of the direction. Due to this, the locking member 22 and the sleeve 19 always make line contact or approximate surface contact at two symmetrical points with respect to the axis, resulting in less wear on the rotating cam surfaces 9a, 22a and good durability, as well as a handle. 11, so the frictional force between the lock member 22 and the guide member 20 does not become abnormally large.
The handle 11 rotates freely. In other words, when the rotating cam surfaces 19a, 22a are simply made to have a plurality of valleys and a plurality of peaks that match the valleys,
When both rotating cam surfaces are in contact, especially at the top of the mountain, the locking member and the sleeve come into point contact at two symmetrical points with respect to the axis, and the surface pressure acting on the cam surfaces increases, easily causing wear and durability. However, according to this embodiment, such a problem does not occur.

In addition, the rotating cam surfaces 19a and 22a are connected to each rotating cam 1.
The rotating cam surfaces 19a, 2 are aligned with straight lines on 9a, 22a.
By forming a continuous surface perpendicular to the center axis of each rotary cam 19a, 22a in any direction that passes through the center of the rotary cam 2a, the roundness of the top portion of the mountain of the rotary cam surface 19a, 22a is improved. The radius of the handle can be set as small as desired to ensure nimble turning of the handle. That is, the rotating cam surface 19a,
Since the surface pressure of the rotating cam surfaces 19a and 22a can be lowered and durability can be improved, the radius of the roundness of the top portions of the crests of the rotating cam surfaces 19a and 22a can be set to a small value to an arbitrary value without worrying about an increase in the surface pressure. After setting, the lock member 22 and the sleeve 19 are moved by the force of the compression spring 23 so that the set axial dimensions of the rotating cam surfaces 19a, 22a are obtained and the lock member 22 and the sleeve 19 are deviated from the specified positions. A rotary cam surface 19 that coincides with the specified position so as to be able to return to the specified position against the frictional force between the
What is necessary is to determine the angles of the valleys and peaks of a and 22a. Therefore, since the radius of the roundness at the top of the mountain of the rotating cam surfaces 19a, 22a can be set to be small to an arbitrary value, the force of the compression spring 23 can be reduced when both the rotating cam surfaces 19a, 22a are in contact at the top of the mountain. The range in which the phenomenon of non-sliding along the rotating cam surfaces 19a, 22a can occur can be reduced, and nimble idling of the handle can be ensured. In other words, if the rotating cam surfaces 19a, 22a simply have a plurality of valleys and a plurality of peaks corresponding to the valleys, the radius of the roundness of the top portion of the peak of the rotating cam surface is the axis of the rotating cam surface. Since the directional dimensions are determined by the angles of the valleys and peaks of the rotating cam surface that match the diameters of the locking member and sleeve at the specified position, the radius becomes large and both rotating cam surfaces are at the top of the mountain. Although there is a large range in which a phenomenon in which the handle does not rotate under the force of the compression spring when the two parts are in contact with each other is large, and a nimble idling operation of the handle cannot be obtained, this does not occur according to the present embodiment.

To release the brake action, pull the handle 11 to engage the protrusion 22b of the lock member 22 with the notch 20b of the guide member 20, and then rotate the handle 11 to release the plunger 12.
rotates, and the pole 16 and ratchet 12 in Fig.
Since the engagement with a is disengaged, the plunger 12 can be slid back due to the brake reaction force, and therefore the brake action is released.

In implementing the present invention, the sleeve and guide member may be integrally engaged with the plunger, and the lock member may be integrally engaged with the handle shaft.

[Brief explanation of the drawing]

Fig. 1 is a diagram showing the entire embodiment of the present invention, Fig. 2 is an enlarged cross-sectional view taken along the - line in Fig. 1, Fig. 3 is a cross-sectional view taken along the - line in Fig. 2, and Fig. 4 is a cross-sectional view taken along the - line in Fig. 1. 2, FIG. 5 is a sectional view taken along the line - in FIG. 2, FIG. 6 is a view taken along the arrow in FIG. 2, FIG. 7a is a diagram showing the external appearance of the sleeve, and FIG. 7b 7a is a view taken in the direction of the arrow in FIG. 7a, FIG. 7c is a view taken in the direction of the arrow in FIG. 7a, and FIG. 8 is a view showing the appearance of the lock member. 10...stick-type handbrake, 11...
Handle, 11a...Grip part, 11c...Handle shaft part, 12...Plunger, 12a...Ratchet, 14...Brake actuation wire, 1
6... Pole, 19... Sleeve, 20... Guide member, 20a... Bottom wall, 20b... Notch, 2
2...Lock member, 22b...Protrusion, 23...Compression spring, 19a, 22a...Rotating cam surface.

Claims (1)

[Claim for Utility Model Registration] A plunger with a handle attached to one end is attached to the vehicle body so that it can slide in the axial direction and rotate around the axis, and a brake actuation wire is connected directly or A locking mechanism that is indirectly connected and holds the plunger in the pulled-out position against the brake reaction force when the driver holds the handle and pulls the plunger to activate the brake, and releases this holding by rotating the plunger in one direction. In the stick-type handbrake for a vehicle, the handle is provided with a handle shaft portion protruding from a portion near one end of the grip portion at right angles to the grip portion, and a sleeve is attached to either the handle shaft portion or one end of the plunger. and a bottomed cylindrical guide member having the sleeve fitted into the opening are fixed, and the other is inserted into the inner side of the guide member by penetrating the bottom wall of the guide member so as to be slidable in the axial direction. and is integrally coupled with a lock member slidably and rotatably fitted inside the guide member, and a lock member is provided between the lock member and the bottom wall of the guide member on opposing end surfaces of the lock member and the sleeve. A rotary cam surface is formed that has a plurality of valleys and a plurality of peaks that hold the rotational position of the handle relative to the plunger at a plurality of predetermined positions by the force of an interposed compression spring, and these rotary cam surfaces A straight line on the surface passing through the center of the rotating cam surface is formed so as to form a continuous surface perpendicular to the central axis of the rotating cam in any direction, and facing the bottom wall of the guide member and this bottom wall. The end face of the locking member is provided with a plurality of notches and protrusions of the plunger that engage when the handle is pulled only when the handle occupies a normal position among the prescribed positions with respect to the plunger. The notch is formed asymmetrically with respect to the axis, and the distance between the notch and the protrusion is set to be larger than the axial dimension of the rotary cam surface when the handle occupies the specified position with respect to the plunger. A safety device for stick-type handbrakes for vehicles.