JP2002036904A - Axle pedal device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a device which is capable of miniaturizing an axle pedal and simultaneously acquiring a step power hystereisis with a good feeling for operation. SOLUTION: To allow rocking form pause position to maximum step position by step power transmitted from an axle pedal 60, a pedal arm 50 is supported by a pedal shaft 40 and a reset spring (a return spring) 80 which energizes the pedal arm 50 to the pause position is arranged around the pedal shaft 40 and frictional force production mechanism 80 which produces variably frictional force following the movement of the pedal arm 50 is arranged around the pedal shaft 40 and a non contact position sensor 90 which detects the rolling angle of the pedal arm 50 is arranged inside the reset spring 70.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an accelerator pedal device applied to a vehicle or the like employing a drive-by-wire system, and more particularly to an accelerator pedal device provided with a sensor for detecting an amount of depression of an accelerator pedal.

[0002]

2. Description of the Related Art An electronic control throttle system, that is, a drive system, is a method for controlling the combustion state, output, rotation control, and the like of an engine mounted on a vehicle, particularly an automobile, more precisely and more precisely than accelerator control intended by a driver. By-wire systems are known. This electronic control throttle system (drive-by-wire system) converts the amount of depression of the accelerator pedal into an electric signal instead of connecting the accelerator pedal and the throttle valve with an accelerator wire, and based on the converted electric signal. It controls the output of the engine.

In this drive-by-wire system, since there is no accelerator wire, the load itself does not act on the accelerator pedal as a pedal load. Therefore, when the vehicle or the like is driven at a constant speed (holding the accelerator pedal at a fixed position), a mechanism is required to compensate for this load so that the driver does not get tired. Also,
If the acceleration of the vehicle fluctuates due to fluctuations in the output of the engine and the driver easily changes the depression amount of the accelerator pedal due to the influence of the resonance system, longitudinal vibration of the vehicle or the like is caused. Therefore, in order to prevent this vibration and the like, a mechanism that generates a force that resists the depression of the accelerator pedal is required.

[0004] As an accelerator pedal device for coping with the above, for example, one described in Japanese Patent Application Laid-Open No. 11-235936 is known. The accelerator pedal device disclosed in this publication includes a pedal rod (pedal arm) that is swung from a rest position to a maximum depression position by a pedaling force from an accelerator pedal, and a return (return) spring that returns the pedal rod toward the rest position. A movable friction member moved by a pedal rod, a return spring for returning the movable friction member to its original position, a housing (body portion) for slidably guiding the movable friction member, and an amount of depression of an accelerator pedal. It is composed of an accelerator position sensor and the like for detecting. A movable friction member, a housing, and the like constitute a frictional force generating mechanism that generates a predetermined frictional force. According to this frictional force generating mechanism, a constant frictional force acts when the accelerator pedal is depressed and exerts a pedal load on the accelerator pedal, while a constant frictional force that opposes the urging force of the return spring when the accelerator pedal is returned. The force acts to reduce the return force of the accelerator pedal. According to this, since a predetermined operation load (pedal load) acts on the accelerator pedal, it is possible to hold the accelerator pedal at a desired position when traveling at a constant speed, thereby reducing driver fatigue. Can be. Further, by detecting the rotation angle of the pedal rod, that is, the depression amount of the accelerator pedal by the accelerator position sensor, a control signal corresponding to the depression amount is output, and the output control of the engine is performed.

[0005]

By the way, in an accelerator pedal device provided with the above-mentioned frictional force generating mechanism, FIG.
As shown in 6, the accelerator pedal pressure (pedal load)
And the amount of movement (stroke) of the accelerator pedal,
The hysteresis has a constant width from the fully closed position of the throttle (start of depressing the accelerator pedal) to the fully opened position (maximum depressed position). Therefore, as shown in FIG. 16 (a), when the pedaling force (pedal load) required at the fully open side of the throttle is adjusted, the return force is insufficient at the fully closed position, and the accelerator response (acceleration feeling) deteriorates. There is a possibility that the return of the accelerator pedal may be poor. On the other hand, FIG.
As shown in FIG. 6 (b), when the pedaling force (pedal load) required on the fully closed side is adjusted, the driver or the accelerator pedal resonates in response to the vibration of the vehicle, and the drivability is deteriorated, and the stable driving is performed. There was a problem that could not be. Also,
The accelerator position sensor mounted on the accelerator pedal device is of a contact type, and a sensor of another type is required to obtain a high-precision output signal while reducing the size of the entire device.

SUMMARY OF THE INVENTION The present invention has been made in view of the above points, and it is an object of the present invention to provide a pedal force characteristic (hysteresis characteristic) that is optimal for operation of an accelerator pedal while simplifying the structure and reducing the size. It is an object of the present invention to provide an accelerator pedal device that satisfies the above conditions and that can detect the amount of depression with high accuracy, and can contribute to good driving performance of the vehicle.

[0007]

According to the present invention, there is provided an accelerator pedal device comprising: a pedal arm movable from a rest position to a maximum depressed position by a pedaling force transmitted from an accelerator pedal;
A pedal shaft for swingably supporting the pedal arm, a return spring for urging the pedal arm to return to the rest position, and a frictional force generating mechanism for generating a frictional force with the movement of the pedal arm. And a detecting means for detecting a rotation angle of the pedal arm, wherein the detecting means comprises a non-contact type position sensor arranged near the pedal shaft. According to this configuration, when the accelerator pedal is depressed, the pedal arm rotates, and the rotation angle is detected and output by the non-contact position sensor. That is, since the position sensor is a non-contact type, high-precision detection is performed, and since the position sensor is disposed near the pedal shaft, the size of the device is reduced.

In the above configuration, it is possible to adopt a configuration in which the return spring is constituted by a torsion spring disposed around the pedal shaft, and the non-contact type position sensor is disposed inside the return spring. According to this configuration, the space inside the return spring can be effectively used, and the size of the device can be reduced by consolidating around the pedal axis.

In the above configuration, the non-contact type position sensor includes a rotor that is curved in an arc shape and has magnets having different polarities in the direction of extension thereof and moves integrally with the pedal arm. A first stator having a magnetic pole portion arranged to face the second stator and a second stator having two magnetic pole portions arranged to face the magnet piece and the magnetic pole portion of the first stator at a predetermined interval. And a Hall element disposed between the first stator and the second stator. According to this configuration, when the pedal arm rotates (oscillates),
The rotor rotates, and the magnet pieces move relatively to the magnetic pole portion of the first stator and the magnetic pole portion of the second stator. In response to this relative movement, a signal (voltage)
Is output, and the rotation angle of the pedal arm, that is, the depression amount of the accelerator pedal is detected.

In the above configuration, it is possible to adopt a configuration in which a plurality of Hall elements are arranged between the first stator and the second stator. According to this configuration,
By using at least one Hall element as a spare, even when a normally operating Hall element is damaged, it is possible to reliably perform detection. In addition, the output characteristics of the plurality of Hall elements can be set to different gradients, respectively, to improve the resolution of the low opening degree, or to compare the plurality of outputs to improve the reliability of the output signal.

[0011] In the above configuration, the frictional force generating mechanism is moved in an arc shape around a predetermined axis by the load of the pedal arm, and has a first inclined surface having a predetermined angle with respect to the moving direction. A movable friction member, a second movable member having a second inclined surface that is disposed to face the first movable friction member in the movement direction, is moved in an arc shape about a predetermined axis, and can contact the first inclined surface; A dynamic friction member, a sliding guide path comprising a curved surface having a sliding surface for slidably guiding the first movable friction member and the second movable friction member and having an arcuate curvature around a predetermined axis; A return spring that urges the second movable friction member in a direction that antagonizes a stepping load applied to the pedal arm and returns the second movable friction member to the original position;
The return spring may include a torsion spring disposed around the pedal shaft, and the return spring may be disposed inside the return spring. According to this configuration, due to the interaction between the first movable friction member, the second movable friction member, and the return spring, the friction force increases as the accelerator pedal is depressed.
With the return of the accelerator pedal, the frictional force decreases.
In addition, the first movable friction member and the second movable friction member are configured to move in an arc shape, and the torsion spring type return spring and the return spring are sequentially arranged around the pedal shaft. The device can be miniaturized by being collected near the pedal shaft.

In the above configuration, the center of the return spring and the center of the return spring are provided at a position deviated from the center of the pedal shaft, and the non-contact type position sensor has the center of the return spring and the center of the return spring inside the return spring. A configuration that is arranged in a region on the side of the side to be used can be adopted. According to this configuration, a spring having a smaller coil diameter can be employed as the return spring and the return spring, and the apparatus can be further reduced in size.

In the above configuration, the first stator and the second stator
The stator is embedded in a main body that rotatably supports the pedal shaft, the pedal arm is fixed to the pedal shaft, and the rotor is relatively immovable in the direction of rotation of the pedal shaft and the axis of the pedal shaft is fixed. A rolling element for a radial bearing, which is swingably connected to a pedal shaft in a plane including the first stator and the second stator and is rotatably disposed between the main body and the first stator and the second stator in a vicinity of a region where the first stator and the second stator are embedded. , A configuration supported by. According to this configuration, even when the center of rotation of the rotor and the center of the pedal shaft are displaced due to variation in dimensional accuracy or due to an overload during operation, the rolling element and the magnet piece follow the displacement. Maintain a constant distance to the stator. As a result, a highly accurate detection signal is output from the sensor.

[0014]

Embodiments of the present invention will be described below with reference to the accompanying drawings. 1 to 15
1 shows an embodiment of an accelerator pedal device according to the present invention. As shown in FIGS. 1 to 3, an accelerator pedal device according to this embodiment includes a bracket 10 fixed to a vehicle body 1 such as an automobile, a housing 20 formed integrally with the bracket 10 as a main body, A cover 30 covering the housing 20, a pedal shaft 40 rotatably supported by the housing 20 and the cover 30, a pedal arm 50 fixed to the pedal shaft 40 and supported swingably; Exerting accelerator pedal 60
And a return spring 7 arranged around the pedal shaft 40.
0, a frictional force generating mechanism 80 arranged in the area of the free end portion 51 of the pedal arm 50, an accelerator position sensor 90 as a detecting means for detecting the amount of depression of the accelerator pedal 60, and the like. I have.

As shown in FIGS. 2 and 3, the housing 20 has a fitting hole (bearing hole) 21 for fitting and rotatably supporting the pedal shaft 40. An inner annular groove 22 having a radius of curvature centered on point C at a position deviated by a distance D from the center, an outer annular groove 23 also having a radius of curvature centered on point C, and an inner annular groove 22. A sensor space 24 formed at a position deviated upward on the inside, an arc-shaped groove 25 having a radius of curvature centered on point C and the like are formed further outside the outer annular groove 23. Here, since the center of the arc-shaped groove 25 is set to the point C, the groove can be formed as close as possible to the outer annular groove 23, whereby the size of the device can be reduced.
Note that the center of the arc-shaped groove 25 can be made coincident with the center of the pedal shaft 40. In this case, the movement trajectory of the free end portion 51 of the pedal arm 50 matches the curvature of the arc-shaped groove 25. A reliable engagement operation is performed.

As shown in FIG. 2, the arc-shaped groove 25 is formed such that the left side is wider and the right side is narrower from a substantially middle portion, and a step portion 25a is formed at a boundary portion. A locking groove 23a is formed in the outer annular groove 23 so that one end portion 83a of the return spring 83 described later is hooked from a part thereof outward in the radial direction. In order to lock the one end 71 of the return spring 70 in the inner annular groove 22, a locking groove 22 directed radially inward from a part thereof is provided.
a is formed.

As shown in FIG. 4, the return spring 70 is a torsion spring formed of a material such as stainless steel, and is retained by the retaining groove 22a while being housed in the inner annular groove 22 of the housing 20. One end 71 and the other end 72 that is engaged with the engaging hole 52 of the pedal arm 50 (see FIG. 5). Then, the pedal arm 50 depressed from the rest position toward the maximum depressed position side
(Accelerator pedal 60) exerts an urging force for returning it to the original rest position.

As shown in FIGS. 3 and 5, the pedal arm 50 has a fitting hole 50a for fixing the pedal shaft 40 by press-fitting, and is bent at a substantially right angle to act on the frictional force generating mechanism 80. Plate-like long end having a free end portion 51, a hook hole 52 for hooking the other end portion 72 of the return spring 70, a lower connecting portion 53 for connecting a rod 60a holding the accelerator pedal 60, and the like. It is formed as a simple member. By adjusting the depression amount of the accelerator pedal 60, the pedal arm 50 swings around the pedal shaft 40, and the rest position (the position indicated by the solid line in FIG. 1) and the maximum depression position (the position in FIG. 1). (The position shown by the two-dot chain line), and the load applied to the frictional force generating mechanism 80 is adjusted. Further, the free end portion 51 of the pedal arm 50 is arranged so as to abut on a first movable friction member 81 to be described later, so that engagement and disengagement with the first movable friction member 81 are reliably performed. Further, it comes into contact with a rubber member 27 embedded in the housing 20 and stops at the rest position.

An accelerator position sensor 90 as a detecting means is a non-contact type position sensor, and is disposed in a sensor space 24 of the housing 20 formed near a fitting hole (bearing hole) 21 for mounting the pedal shaft 40. Have been. As shown in FIGS. 6 and 7, the accelerator position sensor 90 includes a rotor 100 that rotates integrally with the pedal arm 50, a first stator 110 and a second stator 120 embedded in the housing 20, It is composed of two Hall elements 130 arranged between the stator 110 and the second stator 120, a sensor connector 140 and the like.

As shown in FIGS. 6 to 8, the rotor 100 has an annular portion 101 which is fitted around the pedal shaft 40, and a substantially L-shaped portion.
Arm 102 formed in a character shape, armature 103a
And a curved portion 103 in which magnet pieces 103b having different polarities are embedded. As shown in FIG. 8, the annular portion 101 of the rotor 100 includes a cylindrical surface portion 101 a ′ having an inner diameter larger than the outer diameter of the pedal shaft 40 in the direction in which the arm portion 102 extends (the vertical direction in FIG. 8) and the arm. A deformed hole 101a formed by a two-sided portion 101a '' having the same width as the outer diameter of the pedal shaft 40 in a direction perpendicular to the direction in which the portion 102 extends (the left-right direction in FIG. 8), and a connecting pin (spring pin). Fitting hole 10 into which 105 is fitted
1b are formed. Then, the pedal shaft 40 is inserted into the modified hole 101a, and the connecting pin 105 is inserted into the fitting hole 10a.
The rotor 100 is connected to the pedal shaft 40 by being fitted into the fitting hole 1b and the fitting hole 41 of the pedal shaft 40.
In this connection structure, the rotor 100 is swingable (swingable) in the direction of arrow R in FIG. 8 (that is, in the plane including the axis of the pedal shaft 40), and the rotation direction of the pedal shaft 40. At the same time, it can rotate integrally with the pedal shaft 40 (relatively immovable). The magnet piece 103b embedded in the curved portion 103 has an arc surface 103b having a predetermined radius of curvature about the axis of the pedal shaft 40.
′, And are arranged adjacent to each other in the direction of extension (circumferential direction) thereof.

First stator 110 and second stator 12
6 is buried in the housing (main body part) 20 as shown in FIGS.
The arc surfaces 110a ', 120a', and 120b 'each having a predetermined radius of curvature centered on the axis of the pedal shaft 40 so as to face 03b' at a predetermined interval. The portion having the arc surface 110a 'is the first portion.
The magnetic pole portion 110a of the stator 110 is formed, and the portions having the arc surfaces 120a 'and 120b' form the two magnetic pole portions 120a and 120b of the second stator 120. That is, the magnetic pole portion 110a of the first stator 110
Are arranged so as to face the magnet piece 103b at a predetermined interval, and the magnetic pole portions 120a,
0b is arranged to face the magnetic pole portion 110a and the magnet piece 103b at a predetermined interval.

First stator 110 and second stator 12
The outside of the region where 0 is buried is formed as an arc surface 26 having a predetermined radius of curvature centered on the axis of the pedal shaft 40, and the arc surface 26 (main body portion) and the rotor 100
A steel ball (rolling element) 106 acting as a radial bearing is arranged between the curved surface 103c and the arcuate surface 103c so as to roll freely. Here, a spherical body is adopted as the rolling element, but may be a cylindrical or cylindrical one.

The steel ball 106 and the rotor 10
Due to the swingable (oscillating) connection structure of 0, the center of rotation of the rotor 100 and the center of the pedal shaft 40 may be misaligned due to variations in dimensional accuracy, or may be misaligned due to overload during operation. When the steel ball 106 follows the displacement, the steel piece 106
The distance between the stator 110 and the second stator 120 is maintained constant. As a result, a highly accurate detection signal is output from the accelerator position sensor 90.

First stator 110 and second stator 120
Between the two Hall elements 13 as shown in FIG.
0 is arranged. As shown in FIG. 6, the lead wire 131 of the Hall element 130 is led to the sensor connector 140 via a wiring 132 buried in the housing 20. Therefore, when the rotor 100 rotates, the magnet piece 103b, the first stator 110 and the second stator 12
The position relative to 0 fluctuates, and the magnetic flux passing through the Hall element 130 also fluctuates with this fluctuation, and a voltage corresponding to this change is output as a signal. That is, when the pedal arm 50 swings (rotor 100 rotates), the swing displacement is detected as a change in the magnetic flux passing through the Hall element 130, and the rotation angle of the pedal arm 50 (the accelerator pedal 6).
(A stepping amount of 0) is detected.

The accelerator position sensor 90 having the above configuration has an operating angle of about 40 °, and this operating angle corresponds to the swing angle of the pedal arm 50. When the pedal arm 50 is in the vicinity of the rest position (the throttle valve is at the idle (ID) opening position), when the pedal arm 50 is at the substantially middle stepping position (the throttle valve is at the １ ／ opening position), In each state when the pedal is at the depressed position (the position where the throttle valve is fully open), the rotor 1
Magnetic lines of force shown in FIGS. 9A, 9B, and 9C flow between 00 and the first stator 110 and the second stator 120. In addition, the relationship between the magnetic flux passing through the Hall element 130 and the output at this time is obtained as a linear relationship as shown in FIGS. Here,
Since two Hall elements 130 are employed, one can be activated in the case where the other fails, for example, to provide a fail-safe function. The operating angle of the rotor 100 can be set even if the angle is as narrow as about 10 ° to 20 °. Further, here, two Hall elements 1
Although 30 is employed, the invention is not limited to this, and a plurality of Hall elements can be employed. In this case, the output characteristics of the plurality of Hall elements can be set to different gradients, respectively, to improve the resolution of the low opening, or to compare the plurality of outputs to improve the reliability of the output signal. .

In the accelerator position sensor 90 configured as described above, the first stator 110 and the second stator 120 are embedded in the housing (main body portion) 20, so that the number of parts at the time of assembly is small, and It can be done easily. In addition, since it is disposed inside the return spring 70, the size of the entire apparatus can be reduced.

The frictional force generating mechanism 80 includes a pedal arm 50
The frictional force is generated by the movement of the (accelerator pedal 60). As shown in FIG. 2, the first movable friction member 81 and the first movable friction member 81 are reciprocally mounted in the arc-shaped groove 25 of the housing 20. A second movable friction member 82, a return spring 83 for urging the second movable friction member 82 to return to the original position (to the position shown in FIG. 2), and a first movable friction member 8
It comprises a spring 84 for play load and the like arranged between the first and second movable friction members 82.

Here, the inner wall surface of the arc-shaped groove 25 of the housing 20 acts as a sliding surface, and forms a sliding guide path for slidably guiding the first movable friction member 81 and the second movable friction member 82. are doing. As shown in FIG. 3, a long cutout (slit) 20 a is formed on the lower side of the housing 20, and the pedal shaft 40 fixed to the pedal arm 50 is attached to the fitting hole 21. The lower connecting portion 53 of the pedal arm 50 is exposed to the outside of the housing 20 through the notch 20a while being covered with the cover 30.

The first movable friction member 81 is made of a highly slidable material such as oil-impregnated polyacetal, and has an arc surface 8 having the same curvature as the arc groove 25, as shown in FIG.
1a, 81b, a first inclined surface 81c formed such that an angle between the tangents of the circular arc surfaces 81a, 81b and the normal line is θ, and a first inclined surface 81c formed on the opposite side to the first inclined surface 81c. It is formed by a back surface 81d, a cylindrical hole 81e formed to open to the first inclined surface 81c, and the like.

The second movable friction member 82 is formed of a highly slidable material such as oil-impregnated polyacetal, and has an arc surface 8 having the same curvature as the arc groove 25 as shown in FIG.
2a, 82b, a second inclined surface 82c formed such that the angle between the tangents of the arc surfaces 82a, 82b and the normal line is θ, and formed on the opposite side to the second inclined surface 82c. It is formed by a back surface 82d, a cylindrical hole 82e formed to open on the second inclined surface 82c, and the like.

As shown in FIG. 11, the play load spring 84 is formed of a compression type coil spring, one end of which is housed in the cylindrical hole 81e of the first movable friction member 81, and the other end is formed. The cylindrical hole 8 of the second movable friction member 82
The first movable friction member 81 and the second movable friction member 82 generate an urging force in a direction in which the first movable friction member 81 and the second movable friction member 82 are moved away from each other. The biasing force of the play load spring 84 is set to be smaller or equal to the biasing force of the return spring 83 in the most expanded state in the most compressed state. That is, when the pedal arm 50 moves from the rest position to the maximum depressed position by the play load spring 84, the first movable friction member 81 and the second movable friction member 81 are moved over an initial predetermined area (predetermined section). A play area where no frictional force is generated by cooperation with the movable friction member 82 is set.

As shown in FIG. 12, the return spring 83 is a torsion spring made of a material such as stainless steel, and is engaged with the engaging groove 23a while being housed in the outer annular groove 23 of the housing 20. One end 83a,
And a second end 83b hooked to the rear surface 82d of the second movable friction member 82. Then, the second movable friction member 82
Is returned to the original rest position (toward the position shown in FIG. 2).

As shown in FIG. 2, the first movable friction member 81 and the second movable friction member 82 move in the direction of movement along the arc-shaped groove 25 of the housing 20, that is, the sliding guide path (inner wall surface). , The first inclined surface 81c and the second inclined surface 82
c are opposed to each other so that they can come into contact with each other. That is, when the first movable friction member 81 and the second movable friction member 82 are pressed against each other, the first inclined surface 8
1c and the second inclined surface 82c, the first movable friction member 81 is radially inward (downward) and the second movable friction member 82 is radially outward (upward), that is, the arc-shaped groove 25 is formed. Movable friction members 8 so as to move away from each other in a direction orthogonal to the direction in which the
The first arc surface 81a faces the inner wall surface inside the arc groove 25, and the arc surface 82b of the second movable friction member 82
5 is pressed against the inner wall surface outside.

For example, as shown in FIG. 13, when a load F of the pedal arm 50 acts from the outside (the right side in FIG. 13) of the first movable friction member 81, the first movable friction member 81 and the second movable friction member Since it moves to the left in a state where it abuts without being separated from 82, at the moment of the movement, it opposes this load F from the outside of the second movable friction member 82 (left side in FIG. 13). The biasing force F of the return spring 83 acts as a reaction force.

Therefore, when the accelerator pedal 60 (pedal arm 50) is depressed, the first movable friction member 8
The first and second movable friction members 82 move toward the maximum depression position (toward the left in FIG. 13), and at this time, the first movable friction member 81 is moved downward and the second movable friction member 82 is moved. N = Ftan θ acts as a pressing force that presses upwards so as to keep them away from each other (presses against the inner wall surface of the arc-shaped groove 25). That is, when the accelerator pedal 60 is depressed, the first movable friction member 8
When the first and second movable friction members 82 move toward the maximum depression position (to the left in FIG. 13), the first movable friction members 81 and the second movable friction members 82 and the inner wall surfaces of the arc-shaped groove 25 , The frictional force f1 in the direction opposite to the moving direction (to the right in FIG. 13), where μ is the dynamic friction coefficient of the sliding surface.
= ΜN, that is, f1 = μFtanθ acts.

On the other hand, when the accelerator pedal 60 (pedal arm 50) is returned to the rest position before depressing,
The first movable friction member 81 and the second movable friction member 82 are moved toward the rest position (to the right in FIG. 13) by the urging force F of the return spring 83, and at this time, as described above, N = Ftan θ acts as a pressing force for pressing the first movable friction member 81 downward and the second movable friction member 82 upward. That is, when the depression of the accelerator pedal 60 is released and the first movable friction member 81 and the second movable friction member 82 move toward the rest position (to the right in FIG. 13), the first movable friction member 81 Between the second movable friction member 82 and the inner wall surface of the arc-shaped groove 25, assuming that the dynamic friction coefficient of the sliding surface is μ,
A friction force f2 = −μN, that is, f2 = −μFtanθ acts in a direction opposite to the moving direction (to the left in FIG. 13).

Explaining this force relationship, the pedal arm 5
0 load F and the urging force (reaction force) F of the return spring 83
Is expressed as a function of the depression amount (x) of the accelerator pedal 60, the frictional force f1 from the rest position to the maximum depression position is represented by f1 = μF (x) tan θ. Therefore, at the time of the rest position (x = 0), a frictional force of f1 (0) = μF (0) tan θ acts, while the maximum depression position (x = ma)
At the time point when x) is reached, a frictional force of f1 (max) = μF (max) tan θ acts. At this time, since the relationship f1 (max)> f1 (0) is satisfied, the frictional force f1 generated linearly depends on the movement amount (x) when the pedal arm 50 moves toward the maximum depression position. Will increase.

On the other hand, the frictional force f2 when the accelerator pedal 60, that is, the pedal arm 50 moves from the maximum depression position to the rest position is represented by f2 = -μF1 (x) tan θ. Therefore, the maximum depression position (x = ma
At the time point x), a frictional force of f2 (max) = − μF (max) tan θ acts, while at the time point of reaching the rest position (x = 0), f2 (0) = − μF (0) tan θ The frictional force will act. At this time, since | f2 (max) |> | f2 (0) |, the frictional force f2 generated when the pedal arm 50 moves toward the rest position according to the amount of movement (x) thereof Will decrease linearly. That is, a frictional force as shown in FIG. 14 is obtained.

As is clear from the above description, the first
The friction generated when the pedal arm 50 moves toward the maximum depression position due to the movable friction member 81, the second movable friction member 82, the arc-shaped groove 25 as a sliding guide path of the housing 20, the return spring 83, and the like. The frictional force that generates the frictional force such that the force f1 is increased according to the amount of movement and the frictional force f2 generated when the pedal arm 50 moves toward the rest position is reduced according to the amount of movement. A generating mechanism is configured.

Further, when the frictional forces f1 and f2 obtained by the frictional force generating mechanism 80 are superimposed on the urging force of the return spring 70, the urging force of the play load spring 84, and the urging force of the return spring 83, The pedaling force (pedal load) characteristic of the accelerator pedal 60 is obtained as a hysteresis as shown in FIG. That is,
In the forward path toward the maximum depressed position and the return path to return to the rest position, the hysteresis is small (narrow) at the rest position, the response and the operation feeling are good, and the margin for the poor return of the accelerator pedal 60 is provided. Can be increased. On the other hand, the hysteresis is large (wide) on the maximum depression position side, and the controllability of the vehicle (engine) is improved.

Next, the operation of the accelerator pedal device will be described with reference to FIG. First, when the accelerator pedal 60 is not depressed, the pedal arm 50 is turned on.
(And the accelerator pedal 60) are at the rest position (the position corresponding to the fully closed state of the throttle valve). At this time, the urging force of the return spring 70 and the play load spring 84 acts on the pedal arm 50, and the free end 51 of the pedal arm 50 contacts the rubber member 27 embedded in the housing 20, as shown in FIG. , Stopped at rest position.

The second movable friction member 82 is urged by the urging force of the return spring 83 so that the upper end of the second inclined surface 82c abuts on the step 25a of the arc-shaped groove 25 and moves to the rest position. Has stopped. Further, the first movable friction member 81 is urged by the play load spring 84 to separate from the second movable friction member 82, and the rear surface 81b thereof abuts on the free end portion 51 of the pedal arm 50, so that the first movable friction member 81 is at the rest position. Has stopped.

When the accelerator pedal 60 is depressed from this state of the rest position and the pedal arm 50 starts to move toward the maximum depressed position, the first allowable force F applied from the free end 51 of the pedal arm 50 causes the first allowable force. The dynamic friction member 81 starts moving while compressing the play load spring 84 (to the left in FIG. 2), and at the point when it moves by a predetermined distance, that is, at a point P1 in FIG. 15, the second movable friction member 82
Abut. In this movement stroke, the first movable friction member 81 slides in the arc-shaped groove 25 of the housing 20.
The frictional force due to this sliding is set to be as small as possible.

Further, when the accelerator pedal 60 is depressed, the first movable friction member 81 and the second movable friction member 82
Starts moving leftward in FIG. 2, and the wedge action of the first inclined surface 81c of the first movable friction member 81 and the second inclined surface 82c of the second movable friction member 82 causes the first movable friction member 81 to move. Friction force f1 starts to act rightward in FIG. 2 between the arc surface 81a, the arc surface 82b of the second movable friction member 82, and the inner wall surface of the arc groove 25. And the pedaling force of the accelerator pedal 60 increases along the line of f1 + F0,
When reaching the maximum depression position P2, the depression force is f1
(Max) + F0 (max), which indicates the maximum value. When moving toward the maximum depressed position, the first
A part of the outer arc surface 81b of the movable friction member 81 is separated from the inner wall surface outside the arc groove 25,
Because it is pressed against the inner wall surface inside the arc-shaped groove 25 by the wedge action, it can move stably.

Next, when the accelerator pedal 60 is located at the maximum depression position and the pedaling force is reduced and then returned, the second movable friction member 82 and the first movable friction member 81 are actuated by the urging force F of the return spring 83. Start moving toward the rest position (toward the right in FIG. 2). At the same time
By the wedge action of the second inclined surface 82c of the second movable friction member 82 and the first inclined surface 81c of the first movable friction member 81,
A friction force f2 starts to act leftward in FIG. 2 between the arc surface 82b of the second movable friction member 82, the arc surface 81a of the first movable friction member 81, and the inner wall surface of the arc groove 25. Here, the frictional force f2 at point P3 in FIG.
x) + F0 (max). And the accelerator pedal 60
Is reduced along the line of f2 + F0, and the upper end of the second inclined surface 82c of the second movable friction member 82 is stepped with the step 25a.
At the time when the frictional force f2 stops (at point P4 in FIG. 15). Then, through P5 in FIG. 15, the accelerator pedal 60 reaches the rest position.

When the depression and return operations of the accelerator pedal 60 are performed, the pedaling force changes along the hysteresis shown in FIG. By the way, even if the second movable friction member 82 or the first movable friction member 81 is stuck in the arc-shaped groove 25 and cannot return, the free end portion 51 of the pedal arm 50 is kept in contact with the first movable friction member 81.
Therefore, the accelerator pedal 60 and the pedal arm 50 are always returned to the rest position by the urging force of the return spring 70. Therefore, a fail-safe function when detecting the operation state of the accelerator pedal 60 by the accelerator position sensor 90 is secured.

As described above, according to the accelerator pedal device of this embodiment, the first movable friction member 81, the second movable friction member 82, the arcuate groove 25 of the housing 20, and the like have a simple structure. By appropriately selecting the angle θ between the first inclined surface 81c and the second inclined surface 82c, the hysteresis characteristic of the pedaling force (pedal load) can be set freely, and the operation feeling of the accelerator pedal 60 can be improved. Thus, an accelerator pedal device with easy accelerator control can be obtained. Further, it is possible to easily prevent the occurrence of vibration or abnormal noise in the vehicle. Furthermore, since the structure is simple, the assembling is easy and the manufacturing cost can be reduced.

In the above-described embodiment, the non-contact type position sensor 90 as the detecting means is connected to the arc-shaped curved portion 1.
03 and a semicircular first stator 11
Although the configuration constituted by the 0 and the second stator 120 and the like is shown, the configuration is not limited to this, and it can be arranged around the pedal shaft 40, and in particular, can be arranged inside the torsion spring type return spring 70. If so, other shapes can be employed. Further, in the above embodiment, the swingable (swingable) structure is shown as the connecting structure of the rotor 100, but the present invention is not limited to this, and the armature and the magnet piece are integrated with the pedal shaft 40. And a stator may be provided in the housing 20 so as to face the magnet piece.
In this case, since the pedal shaft and the magnet piece are integrally formed, there is no relative displacement, and a change in output depends on a change in the distance between the magnet piece and the stator. As long as the amount of wear of the part can be regulated within a predetermined range,
A predetermined sensor accuracy is ensured.

[0049]

As described above, according to the accelerator pedal device of the present invention, a non-contact position sensor is employed as the detecting means for detecting the rotation angle of the pedal arm.
By arranging this non-contact position sensor near the pedal axle, it is excellent in outfitting, the device can be miniaturized, and
A highly accurate and reliable sensor output can be obtained.
In particular, by using a torsion spring as the return spring and arranging it around the pedal shaft and arranging the non-contact type position sensor inside this return spring, the space inside the return spring can be used effectively. In addition, the size of the device can be reduced by consolidating around the pedal axis. In addition, the return spring constituting the frictional force generating mechanism is a torsion spring, and by arranging the return spring outside the return spring, the components are concentrated in the vicinity of the pedal shaft, and the size of the device can be reduced. In particular, at a position offset from the pedal axis,
The return spring and the center of the return spring are provided, and the non-contact type position sensor is disposed inside the return spring and in a region where the center of the return spring and the return spring are located. Can be set as small as possible, and the size of the apparatus can be further reduced.

[Brief description of the drawings]

FIG. 1 is a side view showing an embodiment of an accelerator pedal device according to the present invention.

FIG. 2 is a cross-sectional view of the accelerator pedal device shown in FIG.

FIG. 3 is a sectional view of the accelerator pedal device shown in FIG. 1;

4A and 4B show a return spring, wherein FIG. 4A is a plan view and FIG. 4B is a side view.

FIG. 5 is a plan view showing a pedal arm.

FIG. 6 is a sectional view showing a non-contact type accelerator position sensor.

7 is a cross-sectional view taken along a line AA in FIG.

8A and 8B show a connection structure of a rotor constituting a part of an accelerator position sensor, in which FIG. 8A is a cross-sectional view cut parallel to a pedal axis, and FIG. 8B is a cross-sectional view cut perpendicular to a pedal axis. It is.

FIGS. 9A, 9B, and 9C show flows of lines of magnetic force in an accelerator position sensor at respective operating positions.

10A is a graph showing the relationship between the amount of depression (opening) of an accelerator pedal and the magnetic flux passing through the Hall element, and FIG. 10B is a graph showing the output of the Hall element.

FIG. 11 is an exploded perspective view showing a first movable friction member, a second movable friction member, and a play load spring.

12A and 12B show a return spring, wherein FIG. 12A is a plan view and FIG. 12B is a side view.

FIG. 13 is a diagram illustrating the operation of the frictional force generating mechanism.

FIG. 14 is a graph showing a frictional force generated by a frictional force generating mechanism.

FIG. 15 is a graph showing pedaling force characteristics of an accelerator pedal.

FIGS. 16A and 16B are graphs showing pedaling force characteristics in a conventional accelerator pedal device.

[Explanation of symbols]

Reference Signs List 20 housing (main body part) 21 fitting hole (bearing hole) 22 inner annular groove 23 outer annular groove 24 sensor space 25 arc-shaped groove (sliding guide path) 26 arc-shaped surface 27 rubber member 30 cover 40 pedal shaft 50 pedal Arm 51 Free end portion 60 Accelerator pedal 70 Return spring 80 Friction force generating mechanism 81 First movable friction member 81c First inclined surface 82 Second movable friction member 82c Second inclined surface 83 Return spring 84 Play load spring 90 Accelerator position sensor (Non-contact type position sensor) 100 Rotor 103a Armature 103b Magnet piece 105 Connecting pin 106 Steel ball (rolling element) 110 First stator 110a Magnetic pole part 120 Second stator 120a, 120b Magnetic pole part 130 Hall element 140 Sensor connector

Claims (7)

[Claims] 1. A pedal arm movable from a rest position to a maximum depressed position by a pedaling force transmitted from an accelerator pedal, a pedal shaft for swingably supporting the pedal arm, and returning the pedal arm toward the rest position. An accelerator pedal device comprising: a return spring that biases as much as possible; a frictional force generating mechanism that generates a frictional force along with the movement of the pedal arm; and detecting means that detects a rotation angle of the pedal arm. The accelerator pedal device, wherein the detecting means comprises a non-contact type position sensor arranged near the pedal shaft. 2. The return spring according to claim 1, wherein the return spring comprises a torsion spring disposed around the pedal shaft, and the non-contact type position sensor is disposed inside the return spring. 2. The accelerator pedal device according to 1. 3. The rotor according to claim 1, wherein the non-contact position sensor includes a rotor curved with an arc and having different polarities in the direction of extension thereof and moving integrally with the pedal arm. A first stator having a magnetic pole portion disposed so as to face the second stator, and a second stator having two magnetic pole portions disposed so as to face the magnet piece and the magnetic pole portion at a predetermined interval, The first
3. The accelerator pedal device according to claim 1, further comprising a hall element disposed between the stator and the second stator. 4. The accelerator pedal device according to claim 3, wherein a plurality of the hall elements are arranged between the first stator and the second stator. 5. The first frictional force generating mechanism has a first inclined surface which is moved in an arc shape about a predetermined axis by a load of the pedal arm, and has a first inclined surface at a predetermined angle with respect to the moving direction. A movable friction member, and a second inclined surface which is disposed to face the first movable friction member in the moving direction, is moved in an arc shape around the predetermined axis, and which can contact the first inclined surface. And a curved path having a sliding surface for slidably guiding the first movable friction member and the second movable friction member and having an arcuate curvature centered on the predetermined axis. A return spring that urges the second movable friction member in a direction that antagonizes a stepping load applied to the pedal arm and returns the second movable friction member to the original position; and the return spring includes the pedal shaft. Around Consists arranged torsion springs, said return spring, said return is disposed inside the spring, the accelerator pedal device according to 4 or to claims 2, characterized in. 6. The return spring and a center of the return spring are provided at a position deviated from a center of the pedal shaft. The non-contact type position sensor is provided inside the return spring and the return spring and the return spring. 6. The accelerator pedal device according to claim 5, wherein the accelerator pedal device is disposed in a region where the center of the vehicle is located. 7. The first stator and the second stator are embedded in a main body that rotatably supports the pedal shaft, the pedal arm is fixed to the pedal shaft, and the rotor is the pedal shaft. In a region in which the first stator and the second stator are embedded so as to be relatively immovable in the direction of rotation and swingably in a plane including the axis of the pedal shaft, and in which the first stator and the second stator are embedded. The accelerator pedal device according to any one of claims 3 to 6, wherein the accelerator pedal device is supported by a rolling element for a radial bearing that is rotatably arranged between the main body and the main body.