JP2002087106A - Hysteresis generating device for accelerator pedal - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a hysteresis generating device causing stable friction force and rotation of a rotary shaft to cause improvement of an operation feeling and stable action. SOLUTION: The hysteresis generating device 10, comprising a case 1, a rotary shaft 12 supported to freely rotate by this case 1, a friction member 13 having a friction surface sliding in a bottom member 15 provided in a bottom part of the case and integrally turning with the rotary shaft, and a spring 14 consisting of a twist coil spring engaging one end with the case the other end with the friction member or the rotary shaft to energize it in a return direction of a pedal to additionally press the friction member 13 to the side of a bottom surface 17 of the case 11, is provided with a cam surface 28, 28 pressing one end of a coil part of the spring 14 by turning in a prescribed direction of the rotary shaft 12 in the friction member 13 and the bottom member 15.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an accelerator pedal hysteresis generator. More specifically, the present invention relates to a hysteresis generating device that provides a difference between a force when an accelerator pedal of an automobile is depressed and a force for supporting the pedal at a predetermined depressed position, thereby improving an operational feeling.

[0002]

2. Description of the Related Art Japanese Patent Application Laid-Open No. 9-48259 discloses FIG.
As shown in FIG. 4, a case 101, a rotating shaft 102 that rotates when the accelerator pedal is depressed, a rotating body 103 that rotates in contact with the rotating shaft, and biases the rotating body in the return direction. Spring 104 and a resistance applying member (friction plate) 1 that applies frictional resistance to the reciprocating rotation of the rotating body 103 in both directions.
A hysteresis generator 107 including a spring 05 and a disc spring 106 for urging the resistance applying body 105 toward the rotating body 103 is described.

[0003] Since this applies substantially the same resistance between the resistance applying member 105 and the rotating body 103 regardless of the rotating direction of the rotating body, FIG. 15 is a graph showing the relationship between the amount of rotation and the stepping force. As described above, a difference H that is twice the frictional force is generated between the depression force F1 when the accelerator pedal is depressed and the depression force F2 when the accelerator pedal is returned. That is, hysteresis can be given to the pedal depression / return cycle. Thus, the resistance at the time of depressing the pedal is not impaired, and the depressing force when the depressing amount is kept constant can be reduced.

The above-mentioned hysteresis generator 107 has a constant frictional force irrespective of the rotational position of the pedal. However, Japanese Patent No. 2890768 discloses that the hysteresis generator 107 has a structure as shown in FIG.
A disk (friction plate) 111 having the friction portion 110 provided in an arc shape from the center to the outer periphery, and a contact portion 112 contacting the friction portion 110
A hysteresis generator has been proposed in which a disk (rotating plate) 113 provided in the radial direction is provided to face the disk. In this device, the position where the frictional force is generated is shifted in the radial direction according to the turning position of the pedal, so that the resistance force based on the friction changes. Thus, as shown in FIG. 17, there is a characteristic that the difference H between the resistance F1 when depressing and the resistance F2 when returning is gradually increased in accordance with the amount of depression of the pedal. Thereby, the operational feeling is further improved.

On the other hand, Japanese Patent Application Laid-Open No. 11-350985 discloses that an accelerator pedal 11 is provided between a bracket 115 and a boss of an accelerator pedal 116 as shown in FIG.
6, a hysteresis generator 118 is provided which has a chevron-shaped cam mechanism 117 for displacing the accelerator pedal to one side in accordance with an increase in the depression angle of the pedal 6 and generates frictional resistance between the inclined surfaces 117a and 117b of the cam mechanism 117. I have. Further, as shown in FIG. 18b, the return spring of the accelerator pedal 116 and the friction surface (inclined surface 117a,
117b) that a single torsion coil spring 119 is also used as a spring for biasing each other.

In this device, when the depression amount of the accelerator pedal increases, the inclined surfaces 117a and 117b ride on each other, and the axial pressing force of the torsion coil spring increases, thereby increasing the frictional force between the inclined surfaces. Thus, a hysteresis curve similar to that in FIG. 17 can be obtained.

[0007]

SUMMARY OF THE INVENTION FIG.
-48259 discloses a hysteresis generator 107,
Although the structure is simple and sufficient frictional resistance can be given, the operational feeling is not good because the resistance is constant when the pedal depression amount is large or small. On the other hand, in the hysteresis generator having the disks 111 and 112 shown in FIG. 16, the size of the hysteresis changes according to the amount of depression of the pedal, so that the operation feeling is improved. There is a problem that it is difficult to generate stable frictional resistance. Also,
The hysteresis generator 118 in FIG. 18 uses the inclined surfaces 117a and 117b of the mountain-shaped projections as friction surfaces, and therefore it is difficult to obtain a stable friction force.

The present invention solves the above-mentioned problems of the conventional hysteresis generator, and can generate a stable frictional force. In addition, the frictional resistance increases in accordance with an increase in the pedal depressing force. It is an object of the present invention to provide a hysteresis generator that improves feeling and provides stable operation.

According to a first aspect of the present invention, there is provided a hysteresis generator comprising: a rotating shaft which rotates in accordance with rotation of an accelerator pedal; a case which supports the rotating shaft; and a friction surface which slides on an inner surface of the case. A friction member that rotates integrally with the rotation shaft, one end of which is engaged with the case, and the other end of which is engaged with the friction member or the rotation shaft, for urging the rotation shaft in a pedal return direction. And a second spring that presses the friction member against the inner surface of the case, the friction member is configured to be movable in the axial direction, and the first spring is configured to move in the direction in which the pedal of the rotary shaft is depressed. It is characterized in that a pressure increasing mechanism for increasing the urging force of the second spring by rotation is provided.

[0010] In such a hysteresis generating device, it is preferable that the first spring and the second spring are constituted by torsion coil springs serving both of them. Further, it is preferable that the pressure increasing mechanism is provided with a conversion mechanism interposed between the rotating shaft and the spring and pressing one end of the second spring toward the friction member as the rotating shaft rotates. 3).
Such a conversion mechanism can be constituted by a cam mechanism (Claim 4), and can also be constituted by a screw mechanism having a screw and a nut (Claim 5). The friction member may be provided with a sliding contact piece that slides on the inner peripheral surface of the case, and the second spring may urge the sliding contact piece outward in the radial direction (claim 6).

In the hysteresis generator of the present invention, the friction member has a friction surface that slides on the inner surface of the case, so that a stable friction force is exhibited. When the pedal depression angle increases, the pressure increasing mechanism
The urging force of the second spring increases, and the friction member is strongly pressed against the case. The frictional force between the solids is basically proportional to the product of the coefficient of friction and the contact force between the two (Newtonian friction), so that the frictional resistance increases. Thus, the device of the present invention can achieve the stabilization of the frictional force while maintaining the basic operation of the conventional device.

The hysteresis generator in which the first spring and the second spring are constituted by one torsion coil spring requires only a small number of parts. Further, when the angle of the wire with respect to the plane perpendicular to the axis is large, the urging force in the axial direction increases as the urging force in the torsional direction increases, so that the torsion coil spring itself acts as a pressure increasing mechanism.
Therefore, the pressure increasing effect is further improved.

A hysteresis generating device, wherein the pressure increasing mechanism includes a conversion mechanism interposed between the rotation shaft and the spring and for pushing one end of the second spring toward the friction member with rotation of the rotation shaft. According to a third aspect, when the rotation shaft rotates, the second spring is pushed toward the friction member. As a result, the contact pressure between the friction member and the inner surface of the case increases, and the friction force increases. When the conversion mechanism is constituted by a cam mechanism (claim 4), the mechanism is simple. Further, since the cam mechanism is provided separately from the friction member, the cam mechanism can reduce the friction as much as possible. Thereby, the cam action and the friction action are stabilized. When the conversion mechanism is constituted by a screw mechanism (claim 5), the rotational force can be easily converted into the axial pressing force, and the rotation of the rotary shaft is stabilized.

A hysteresis generating device wherein a sliding contact piece sliding on the inner peripheral surface of the case is provided on the friction member, and the sliding contact piece is urged radially outward by the second spring. In (2), the spring action of the sliding contact piece itself can be used as the second spring. Thereby, the number of parts can be reduced.

[0015]

Embodiments of the present invention will now be described with reference to the drawings. FIG. 1 is a longitudinal sectional view showing an embodiment of a system for generating a system (hereinafter simply referred to as a generator) of the present invention, FIG. 2 is a sectional view taken along the line II-II of FIG. 1, and FIG. FIG. 4 is a graph showing a hysteresis curve of the generator of FIG. 1, FIG. 5 is a longitudinal sectional view showing still another embodiment of the generator of the present invention, and FIG. 7 and 8 are longitudinal sectional views showing another embodiment of the generator of the present invention, and FIG. 9 is a longitudinal sectional view showing still another embodiment of the generator of the present invention. 10 is a sectional view taken along line XX of FIG. 9, FIG.
FIGS. 1, 12, and 13 are longitudinal sectional views showing still another embodiment of the generator of the present invention.

A generator 10 shown in FIG. 1 includes a cylindrical case 11, a rotating shaft 12 rotatably provided in the case, a friction member 13 rotating integrally with the rotating shaft,
Spring 14 interposed between case 11 and friction member
It is composed of The case 11 is a cylindrical main body 1 having a bottom.
1a and a lid member 11b for closing the opening thereof,
Further, a bottom member 15 that is in sliding contact with the friction member is fixed to the bottom of the main body 11a. Thus, the case 11 has a cylindrical shape with walls at both ends. On the inner surface side of the bottom member 15, a fan-shaped stopper 18 as shown in FIG. 2 is provided so as to protrude in the axial direction.

An end 21 of the rotary shaft 12 is rotatably and axially slidably supported by a bottom member 15, and the other end is rotatably and axially slidably supported by a lid member 11a. I have. Further, the other end is a lid member 1.
A male screw 22 for connecting the pedal is formed around the projecting portion. Reference numeral 23 denotes a screw hole for a set screw.

The friction member 13 is a disk-shaped member having a step 25 in the middle, and as shown in FIG. 2, a fan-shaped hole 26 engaged with the stopper 18 with play in the rotational direction.
It has. The hole 26 engages with the stopper 18 to regulate the rotation of the pedal in the return direction (clockwise direction in FIG. 2). A step portion 25 provided on the other surface of the friction member 13 is a portion with which the final winding of the spring 14 is engaged. A stop groove 27a is formed.

The spring 14 is a torsion coil spring (recoil spring) having a coil portion 14a disposed around the rotary shaft 12, and arms 14b and 14c bent from both ends and extending inward. One arm 14b of the spring 14 is engaged with the locking groove 27a of the friction member 13 as described above.
Are locked so that torque can be transmitted. Spring 14
The other arm 14c is provided with a locking hole or locking groove 2 formed in a boss 11c provided on the lid member 11b of the case 11.
7b. The spring 14 is attached to the case 11 in a state where initial deflection is applied in a direction (in the direction of the arrow P on the lid member side) slightly wound from a natural state and compressed in the axial direction. In this embodiment, since one end of the spring 14 is locked to the lid member 11b, when the lid member 11b is attached to the main body 11a, it may be attached by twisting counterclockwise and pushing. By mounting in this manner, the urging force of the spring 14 moves in the direction in which the coil of the spring 14 is
Act in the direction to be rotated in the direction. However, the friction member 13 is stopped at a predetermined position by the engagement between the stopper 18 and the fan-shaped hole 26.

Further, in the present embodiment, the friction member 13
And the bottom member 15 are in contact with each other, that is, the friction surface
The inclined surfaces (cam surfaces) 28 are inclined. The inclination direction of the inclined surfaces 28, 28 is a direction in which, when the rotating shaft 12 is rotated in the stepping direction of the pedal, a thrust in a direction of separating the friction member 13 and the bottom member 15 from each other is generated. Although a pair of inclined surfaces may be provided, in the present embodiment, since the rotation angle of the pedal is small, a plurality of pairs, for example, about 4 to 8 pairs are radially provided. The friction member 13 is fixed to the rotating shaft 12 by welding or a screw. However, integral molding may be used. The container body 1
2a, a circular opening 29a as shown in FIG.
A fitting hole 29 having a rectangular notch 29b is formed on both side edges of the bottom member 15, and a fitting projection that fits with the fitting hole 29 is formed in the bottom member 15, Thereby, the bottom member 15 is firmly fixed to the main body 11a.

Reference numeral 30 in FIG. 1 denotes a bush made of synthetic resin or metal, interposed between the rotating shaft 12 and the lid member 11b. However, when the lid member 11b is formed of a synthetic resin and the rotating shaft 12 is formed of a metal, such a bush 30 can be omitted.

The generator 10 configured as described above can be provided on the portion of the support shaft 32 of the accelerator pedal 31 as shown in FIG. The accelerator pedal 31 is a publicly known one comprising a support shaft 32 connected to one end of the rotating shaft 12 of the generator 10, a lever 33 fixed to the shaft, and a foot plate 34 fixed to the other end of the lever. is there. In addition,
As described above, the spring 14 of the generator 10 can be used as a spring for returning the pedal, but another spring for returning may be used. Further, instead of directly connecting the lever 33 and the rotating shaft 12, another link or cable may be interposed.

In the generator 10 configured as described above, one end of the spring 14 is engaged with the case 11 and the other end is engaged with the friction member 13. (The direction in which the spring 14 unwinds). This urging force is the initial urging force f1 in FIG. Further, the friction member 13 is pressed against the bottom member 15 by the urging force of the spring 14 extending in the axial direction. Thus, when the friction member 13 rotates, a friction force R1 corresponding to the product of the urging force and the friction coefficient is generated in a direction that resists the rotation direction. Therefore, when the rotary shaft 12 is rotated in the direction of the arrow Q by depressing the pedal from this state, a force (F1 = f1 + R1) against the urging force f in the rotation direction of the spring 14 and the frictional force R is required.

When the rotation angle increases, the spring 14 is twisted in the direction in which the winding is wound, and the spring 1 is accordingly turned.
4 becomes large, and the urging force f in the direction of arrow P becomes large. Further, the friction member 13 is
Since the inclined surfaces 28 and 28 rotate in the direction in which they ride on each other, the friction member 13 compresses the spring 14. Therefore, the biasing force of the spring 14 in the axial direction also increases, and the inclined surface (friction surface)
The frictional force R between 28 and 28 also increases almost linearly with it.

On the other hand, once the pedal is depressed to a predetermined angle and then the depression force is reduced, the difference between the urging force f2 in the direction of arrow P by the spring 14 and the frictional force R2 acting in the direction opposite to the rotation at that time. A force corresponding to (F2 = f2-R2) acts. Therefore, the force F2 for maintaining the pedal in that position is:
A force (F2 = f2-R2) smaller than the force at the time of stepping (F1 = f1 + R1) is sufficient. Since the urging force in the rotation direction and the axial direction by the spring 14 increases as the rotation angle of the rotation shaft 12 increases, the force F2 to be maintained also increases almost linearly. Further, the difference between the force F1 at the time of stepping on and the force F2 at the time of maintaining the pressure linearly increases with an increase in the amount of stepping. Therefore, it is possible to obtain a favorable operation feeling while maintaining the depression force and the maintenance force according to the increase in the depression amount.

Further, in the generator 10, inclined surfaces (friction surfaces) 28 of the disk-shaped friction members 13 are arranged radially.
And a frictional force is generated between the radially arranged inclined surfaces 28 of the bottom member 15 of the case 11, so that stable frictional resistance can be obtained.

In the above embodiment, the cam mechanism is connected to the friction member 1.
3 and the case 11 (the bottom member 15).
Although the friction surface also serves as a friction surface, one end of the spring 14 can be used as a cam element and the friction surface can be separated from the cam surface. FIG. 5 shows a generator 10a having such a cam mechanism.
1 shows an embodiment of the present invention.

In the generator 10 a shown in FIG. 5, a disc-shaped cam member 36 is fixed to the rotating shaft 12 separately from the friction member 13. The cam member 36 has an inclined surface (inclined surface) that contacts one end of the coil portion 14 a of the spring 14. The bottom surface 17 of the case 11 is a friction surface that comes into sliding contact with the friction member 13. In addition, as in the case of FIG.
Can be provided with a separate bottom member 15. In the vicinity of the bottom surface 17, a stopper 18 as shown in FIG. 6 is provided so as to protrude inward in the radial direction.

The tip 21 of the rotary shaft 12 is rotatably supported on the bottom of the case 11, and the other end is a lid 11b.
Projecting from. A coaxial hole 22a for connecting a pedal and a lock pin hole 23a are formed in the protruding portion. Further, in this embodiment, a flange 24 is provided on the free end side of the rotating shaft 12 to be rotatably engaged with the lid 11b for retaining.

The friction member 13 is a disk-shaped member.
As shown in FIG. 7, the projection 26a is provided to protrude outward in the radial direction. The projection 26a is provided on the stopper 18 of the case 11
To define the stop position in the return direction (counterclockwise) of the pedal. The central portion of the friction member 13 is axially movable with respect to the rotation shaft 12 and is provided with a slide key or a serration 37 so as to rotate in the rotation direction.
And so on. One surface of the friction member 13 is the case 1
1 is a friction surface 38 that is in sliding contact with the bottom surface 17. Friction surface 38
A locking hole 39 for locking one end of the spring 14 so that torque can be transmitted is formed on the surface on the opposite side. The winding direction of the spring 14 is opposite to that in FIG.

The tip of one arm 14b of the spring 14 or the end of the coil 14a is in contact with the friction member 13 so as to restrain the spring 14 from expanding in the axial direction. The tip of the other arm 14c is bent and engaged in a groove 40 formed in the inner peripheral surface of the case 11 so as to be slidable in the axial direction and to restrict movement in the rotation direction. The other end of the coil portion 14a is in contact with the cam member 36. The spring 14 is mounted in the case in a state where initial deflection is applied in a slightly unwinding direction (the arrow P direction when viewed from the lid member) from a natural state. Therefore, the spring 14 at the time of attachment
Is the direction in which the wire of the spring 14 is wound, that is, the direction in which the friction member 13 is to be rotated in the direction of the arrow P. However, the friction member 13 includes the protrusion 26a and the stopper 18
Is stopped at a predetermined position by the engagement of.

The cam member 36 is a disk-shaped member.
One surface is in contact with the flange 24 of the rotating shaft 12. On the other surface, a helical inclined surface 28 that contacts the end of the coil portion 14a of the spring 14 is formed. The angle of the helix is preferably adjusted to the angle of the coil portion 14a. The cam member 36 is fixed to the rotating shaft 12 by welding or a screw. Note that the rotating shaft 12 and the cam member 36 may be integrally formed.

The generator 10a thus configured is
It has substantially the same operation and effect as the generator of FIG. 1, and the hysteresis curve shown in FIG. 4 is obtained. Further, in the generator 10a, since a frictional force is generated between the friction surface 38 of the disc-shaped friction member 13 and the bottom surface 17 of the case 11, stable frictional resistance can be obtained, and the rotating shaft Since the shaft 12 does not move in the axial direction, the rotating shaft 12 performs a stable rotation operation.

In the generators 10 and 10a shown in FIGS. 1 and 5, the inclined surfaces (cam mechanism) of the friction member 13 and the cam member 15 are provided.
Converts the force in the rotation direction of the rotary shaft 12 into the force in the axial direction, but other conversion mechanisms may be used. 7 and 8, the screw mechanism is employed as such a conversion mechanism.

In the generator 10b shown in FIG. 7, a male screw 41 of a left-hand thread is formed at the base of the rotating shaft 12. A nut 42 having a female screw screwed with the male screw 41 is attached to the lid 11b of the case 11 so as to be movable in the axial direction and not to rotate. Such an attachment can be configured by, for example, fitting a slide pin 43 fixed to the lid 11b slidably into a hole formed in the nut 42. For other configurations, such as a friction member 13 and a spring 14, which are attached so as to be movable in the axial direction and co-rotate with respect to the rotating shaft 12, the generator 10 shown in FIG.
Substantially the same as a. However, the initial deflection of the spring 14 is reversed from that in FIG. That is, in FIG.
Reference numeral 4 gives an initial biasing force in a direction in which it expands somewhat from its natural state, but in the case of FIG. 7, it is attached in a state of being bent in the winding direction.

In the generator 10b, when the rotating shaft 12 is rotated in the direction indicated by the arrow Q, the nut 42 is moved in the direction indicated by the arrow S by screwing the male screw 41 and the nut 42 together. Thereby, the nut 42 presses the coil portion 14 a of the spring 14 in the direction of the arrow S, and the contact force between the friction member 13 and the bottom surface 17 of the case 11 increases. Thereby, the frictional force against the rotation of the rotating shaft 12 increases as in the case of the generator 10 of FIG. Since the spring 14 bends in the direction in which it is wound, the arrow P
The biasing force in the direction increases. Thereby, a hysteresis curve similar to that of FIG. 4 is obtained.

That is, in the generator 10b shown in FIG. 7, when the pedal is depressed, the spring 1
4 bends so as to be involved. Therefore, the number of turns increases,
The axial biasing force is somewhat increased. Thereby, the frictional force is further increased as compared with the case of FIG.

In the generator 10c of FIG. 8, a female screw 44 is formed on the lid 11b of the case 11,
Is formed with a male screw 41 to be screwed with the female screw.
Further, the rotary shaft 12 is formed with a flange 46 that is in sliding contact with the end of the coil portion 14a of the spring 14. When the rotating shaft 12 is rotated in the direction of arrow Q, the rotating shaft 12 moves to the left in FIG. 8, and accordingly, the flange 46 presses the right end of the coil portion 14a of the spring 14 to the left. As a result, the biasing force of the spring 14 in the axial direction increases, and the friction member 1
The frictional force between 3 and case 11 increases. Other points are the same as those in FIG.

In the generator 10d of FIG. 9, a female screw 44 is formed on the lid 11b of the case 11 as in the case of FIG. 8, and a male screw 41 screwed to the rotary shaft 12 with the female screw.
Are formed. One end of a spring 14 formed of a torsion coil spring is engaged with the case 11 and the other end thereof is engaged with the rotary shaft 12, thereby urging the rotary shaft 12 in the pedal return direction (arrow P direction). Further, an inner peripheral surface 47 on the inner side (left side in the drawing) of the case 11 is tapered so that the inner peripheral surface 47 becomes narrower toward the inner side, and the friction member 13 is fixed to the rotating shaft 12.

As shown in FIG. 10, the friction member 13 comprises a boss 48, a plurality of connecting pieces 49 extending outward from the boss 48, and a friction piece 50 having one end connected to the connecting piece. It is configured. In this embodiment, the friction pieces 50 are a pair of friction pieces 50a and 50b extending in opposite directions from the two connection pieces 49, respectively, and two pairs of the connection pieces are provided. As shown in FIG. 7, each friction piece 50 is formed in a tapered shape that is in sliding contact with the tapered inner peripheral surface 47. Further, the friction member 13 is made of an elastic material, for example, a synthetic resin.

In the generator 10d constructed as described above, the friction piece 50 is urged radially outward by the elasticity of itself and the connecting piece 49. When the rotating shaft 12 is rotated in the direction of arrow Q, the spring 14 is bent to increase the resistance in the rotating direction, and the rotating shaft 12 is moved to the inner side of the case 11 by the action of the screw. Thereby, the friction piece 50 and the connecting piece 49 come into sliding contact with the narrow inner side of the inner peripheral surface 47 of the case 11. Therefore, the friction piece 50 and the connection piece 4
9 is pressed inward in the radial direction, the contact pressure between the inner surface of the case 11 and the friction piece 50 increases, and the frictional force also increases. Accordingly, a hysteresis curve similar to that of the above-described embodiment as shown in FIG. 4 is obtained.

In this embodiment, as shown in FIG. 10, one end of the friction piece 50 is connected to the boss 48 via the connecting piece 49.
When the rotating shaft 12 is rotated in the direction of the arrow P, the friction piece 50a extending in the direction of the arrow Q bends relatively freely, so that it is difficult to exert a friction effect. However, the friction piece 50b extending in the direction of the arrow P sufficiently exerts a friction action. On the other hand, when rotating the rotary shaft 12 in the direction of the arrow Q, the friction piece 50a extending in the direction of the arrow Q mainly exerts a frictional force, contrary to the above. As described above, in this embodiment, since different friction pieces exert a frictional action according to the rotation direction, by changing the friction coefficient or elasticity of the friction pieces, different resistances are exerted according to the rotation direction. It can be configured as follows.

In the generator 10d of FIG. 9, one end of the spring 14 is connected to the rotary shaft 12, but it can be engaged with the friction member 13 as in the case of FIG.

In the generator 10e shown in FIG. 11, one end of a spring 14 composed of a torsion coil spring is locked to the friction member 13, and the other end is locked to the case 11, particularly the lid 11b. The angle (torsion angle) θ of the wire with respect to a plane orthogonal to the axis of the spring 14 is large. The magnitude of the twist angle is, for example, about 15 to 80 degrees, and preferably 30 to 60 degrees. The relationship between the winding direction of the spring 14 and the rotating direction of the rotating shaft 12 is such that the spring 14 is wound when the rotating shaft 12 is rotated in the pedal stepping direction.

In the generator 10e, when the rotating shaft 12 is rotated in the pedal stepping direction, the spring 14 is bent so as to be involved, so that the number of windings is increased and the axial urging force is considerably increased. . Therefore, a mechanism for converting the rotation of the rotation shaft 12 into the axial movement of the end of the spring 14 is not required separately, and the spring 14 itself can exhibit such a conversion action. However, since only one spring 14 exerts a large force to bias the rotating shaft 12 in the radial direction (radial direction), it is preferable to provide a plurality of springs 14 at equal intervals in the circumferential direction. Thereby, the biasing force of the spring 14 is balanced.

The generator 10f shown in FIG.
It is almost the same as the generator 10 of FIG. Also in this case, the spring 14 is assembled after giving the initial deflection in the winding direction, and therefore, the rotating shaft 12 is always urged in the unwinding direction. Therefore, when the pedal is depressed, the spring 14 is twisted in the winding direction, and the urging force to expand in the axial direction increases. for that reason,
This also has the same effect as the above embodiment.
Further, in this embodiment, the interval between the windings of the coil portion 14a of the spring 14 is small and almost in a close contact state, so that the spring is in close contact at the time of winding and the axial reaction force increases.
Further, a frictional force is generated between adjacent windings of the spring 14. As a result, the greater the pedal depression angle, the greater the difference between the depression force and the maintained force.

In the generator 10g shown in FIG.
Are provided with friction members 13a, 13b on the distal end side and the proximal end side, respectively. Further, one friction member (right side in this embodiment) 13 b is provided so as to be movable in the axial direction with respect to the rotating shaft 12 and to co-rotate therewith. Further, a pair of springs 14d and 14e, which are formed of torsion coil springs and have opposite twisting directions, are interposed between each of the friction members 13a and 13b and the case 11. In this embodiment, the spring 14 in which both the springs 14 d and 14 e are formed continuously and integrally is adopted, and the bent connecting portion 52 is locked to the inner peripheral surface of the case 11.

In the generator 10g, the friction member 13
Since a and 13b are two pieces and the friction surface is two places,
Large friction force can be obtained. The spring 14 composed of the deformed torsion coil spring in FIG.
As in the case of (2), a plurality of coils may be arranged at equal intervals in the circumferential direction, whereby the torsional elasticity and the axial biasing action are stabilized. Further, the interval between the coil portions of the spring 14 may be reduced as shown in FIG.

[Brief description of the drawings]

FIG. 1 is a longitudinal sectional view showing one embodiment of a system for generating a system of the present invention.

FIG. 2 is a sectional view taken along line II-II of FIG.

FIG. 3 is a plan view showing an example of attaching the generator of FIG. 1 to an accelerator pedal.

FIG. 4 is a graph showing a hysteresis curve of the generator of FIG.

FIG. 5 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 6 is a sectional view taken along line VI-VI of FIG. 5;

FIG. 7 is a longitudinal sectional view showing another embodiment of the generator of the present invention.

FIG. 8 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 9 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 10 is a sectional view taken along line XX of FIG. 9;

FIG. 11 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 12 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 13 is a longitudinal sectional view showing still another embodiment of the generator of the present invention.

FIG. 14 is a sectional view showing an example of a conventional generator.

FIG. 15 is a graph showing a hysteresis curve of the generator of FIG.

FIG. 16 is a main part front view showing another example of the conventional generator.

FIG. 17 is a graph showing a hysteresis curve of the generator of FIG.

FIG. 18a is a perspective view of a main part showing still another example of a conventional generator, and FIG. 18b is a partial cross-sectional side view of the generator.

[Explanation of symbols]

 Reference Signs List 10 generator 11 case 11a main body 11b lid 12 rotating shaft 13 friction member 14 spring 14a coil portion 14b, 14c arm portion 15 bottom member 17 bottom surface 18 stopper 22 male screw 23 screw hole 25 step portion 26 fan-shaped hole 27a, 27b Stop groove 28 Cam surface 31 Accelerator pedal 32 Shaft 33 Lever 34 Foot plate f Spring biasing force R Friction force F Resistance force 10a Generator 36 Cam member 21 Tip 22a Hole 23a Lock pin hole 24 Flange 26a Projection 37 Serration 38 Friction surface 39 Engagement hole 40 Groove 10b Generator 41 Male screw 42 Nut 43 Slide pin 10c Generator 44 Female screw 46 Flange 10d Generator 48 Boss 49 Connecting piece 50 Friction piece 10e Generator 10f Generator 10g Generator 13a, 13b Member 14d, 14e spring

Claims (6)

[Claims] A rotating shaft that rotates in accordance with rotation of an accelerator pedal, a case that supports the rotating shaft, and a friction surface that slides on an inner surface of the case, and that rotates integrally with the rotating shaft. A friction member that moves, one end of which is engaged with the case, the other end of which is engaged with a friction member or a rotating shaft, and a first spring for biasing the rotating shaft in a pedal return direction; A second spring that presses against the inner surface of the case,
While the friction member is configured to be movable in the axial direction,
The rotation of the rotary shaft in the direction in which the pedal is depressed causes the second
A hysteresis generator for an accelerator pedal including a pressure increasing mechanism for increasing a biasing force of a spring. 2. The hysteresis generator according to claim 1, wherein the first spring is a torsion coil spring that also serves as a second spring. 3. The pressure-increasing mechanism includes a conversion mechanism interposed between a rotation shaft and a spring, the conversion mechanism pressing one end of a second spring toward a friction member as the rotation shaft rotates. 2. The hysteresis generator according to 1. 4. The conversion mechanism according to claim 3, wherein the conversion mechanism is a cam mechanism.
The hysteresis generator as described. 5. The device according to claim 3, wherein the conversion mechanism is a screw mechanism.
The hysteresis generator as described. 6. The friction member includes a sliding contact piece that slides on an inner peripheral surface of the case, and the second spring urges the sliding contact piece radially outward. 2. The hysteresis generator according to 1.