JP2000158970A - Reaction controller for accelerator pedal - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an accelerator pedal reaction controller capable of easily switching an increase characteristic of a pedal reaction force at an early stage of pedal pressing even in operation. SOLUTION: In this accelerator pedal reaction controller, one end of a coil spring 19 is locked to a lock point A provided near a peripheral part of a turning plate 17 interlocking with an accelerator pedal 12, while the other end of the coil spring 19 is locked to a lock point B provided on a nearly circular circumference of a wheel type gear 22 constituting a worm gear mechanism 21 attached to a vehicle main body such that the coil spring 19 is stretched. A shaft of the wheel type gear 22 is provided such that a rotation shaft center Og of the wheel type gear 22 lies on a tangent line L1 contacting with a moving track arc S of the lock point A at the lock point A position in the case of no pressing of the accelerator pedal 12. Thereby, rotation of the wheel type gear 22 changes a tension of the coil spring 19 to allow easy adjustment of a reaction force against the pressing of the accelerator pedal 22 with a simple structure.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to an apparatus used in an industrial vehicle or the like to control a characteristic of increasing an accelerator pedal reaction force by a spring urging force and a locking structure thereof.

[0002]

2. Description of the Related Art Conventionally, traveling speed control of most vehicles is performed by depressing an accelerator pedal. In particular, in an industrial vehicle such as a forklift which also performs a pickup operation and a loading operation of a load, an accurate position is determined. In order to perform such operations, a configuration capable of severe accelerator control is required.

[0003] In a battery-driven vehicle, which has been developed in recent years, accurate running drive control by current control is possible, so that speed control that is almost faithful to accelerator pedal depression information is possible.

However, as described above, in the use of an industrial vehicle, a moving operation at a very low speed (hereinafter referred to as an inching operation) is frequently performed. The characteristics of the reaction force have a great influence on the vehicle operation performance.

FIG. 7 is a side view of an example of an accelerator pedal mechanism conventionally used in a battery-powered vehicle. In this figure, a toe board 1 is provided on a floor plate of a vehicle cab, and has a finite length opening 1a, and a locking plate 1b having a locking groove 1c cut down on the lower surface thereof. The accelerator pedal 2 is pivotally mounted on the toe board 1 so as to be rotatable about a shaft 2a.

The arm 5 has an L-shape rotatable about a base shaft 5a. The base shaft 5a rotatably penetrates through a support cylinder 4 parallel to the toe board 1 and below the opening 1a. Has a free end passing through the opening 1a, and a roller 6 is axially provided at the tip thereof so as to slidably contact the back surface of the accelerator pedal 2.

A torsion spring 8 is fitted in a gap between the inner diameter of the support cylinder 4 and the base shaft 5a, and one end of the spring is fixed on the base shaft 5a and the other end is fixed to the inner diameter of the support cylinder 4 respectively. I have.

A pivot plate 7 is vertically mounted on a shaft portion (a front side on the drawing sheet) in which the base shaft 5a protrudes through the support cylinder 4, and a part thereof penetrates through the opening 1a. A protruding restricting portion 7a is formed.

A locking point A is set near the outer edge of the rotating plate 7 at a position substantially opposite the base shaft 5a of the restricting portion 7a. The coil spring 9 is located between the locking point B set in the locking groove 1c on the plate 1b.
Is stretched.

The torsion spring 8 and the coil spring 9
The two springs are such that the biasing force (torsion or tension) is linearly proportional to torsion or elongation.

Here, as a relative positional relationship between the locking point A and the locking point B, which are points to be particularly noted, the coil spring 9 at the time when the rotating plate 7 has rotated to some extent counterclockwise (arrow R in the drawing). The position of the locking point A at the initial stage of depressing the pedal is set so that the position of the locking point A coincides with the tangent to the arc of the movement locus of the locking point A.

A potentiometer 10 (indicated by a broken line) is provided at the tip of the base shaft 5a which projects through the support cylinder 4.

In this configuration, the accelerator pedal 2
, The rotation angle of the base shaft 5a is output to the potentiometer 10 as the accelerator depression amount while simultaneously providing an increased reaction force due to the urging forces of the two springs.

Of the increased reaction force, the reaction force due to the urging force of the torsion spring 8 inside the support cylinder 4 increases almost linearly in proportion to the depression angle of the accelerator pedal 2 and further applies the urging force of the coil spring 9. Thus, a reaction force characteristic as shown by a curve in FIG. 8 is obtained with respect to the depression angle of the accelerator pedal 2.

As shown by the curve in the figure, the characteristic in which the rate of increase in the reaction force is particularly small at the initial stage of depression of the pedal 2 means that the accelerator operation in the inching operation is a light operation in which the pedal force is particularly suppressed. That is.

Here, the torsion spring 8 and the coil spring 9 themselves have a property in which the urging force has a linear proportional relationship to the torsion and elongation, but the reaction force is locally reduced when the accelerator pedal 2 is depressed. This characteristic is due to the relative positional relationship between the locking point A and the locking point B in the tensioning configuration of the coil spring 9 as described below.

FIGS. 9A, 9B and 9C show the pivot plate 7 which rotates counterclockwise about the base shaft 5 as the pedal 2 is depressed, and the locking point A formed on the pivot plate 7. It is a figure which shows the state of the relative positional relationship with three locking points B with respect to it.

FIG. 9B is a view showing a state in which the other spring engagement point B is located on a tangent line which contacts the movement locus of the spring engagement point A on the rotating plate 7 at the engagement point A. 9A and 9C respectively show a state in which the rotary plate 7 is returned to the clockwise direction to some extent after the state in FIG. 9B and a state in which the rotary plate 7 is advanced to the counterclockwise to some extent. is there.

First, the state shown in FIG. 9B is a state in which the rate of increase in the extension of the coil spring 9 (ie, the rate of increase in the tension) with respect to the rate of increase in the rotation angle of the rotary plate 7 (ie, the rate of increase in the depression of the pedal) is greatest. That is, it can be said that when the pedal 2 is started to be depressed from this state, the rate of increase of the reaction force is the largest.

On the other hand, in the state shown in FIG. 9A, the pedal 2 is depressed to rotate the rotary plate 7 in the counterclockwise direction.
(A state in which the coil spring 9 coincides with a tangent to the arc of the movement locus of the locking point A), so that the rate of increase of the elongation with respect to the rate of increase of the rotation angle gradually increases. When the state further proceeds to the state shown in FIG. 9B and enters the state shown in FIG. 9C, the ratio of the rate of increase of the elongation to the rate of increase of the rotation angle gradually decreases as the rotating plate 7 is rotated counterclockwise. State.

FIG. 10 is a graph showing the relationship between the counterclockwise rotation of the rotating plate 7 and the increase in the reaction force generated only by the coil spring 9 in the range including the state transition from FIG. 9A to FIG. 9C. is there. In the figure, θa, θb, θ
c corresponds to the rotation angle of the rotary plate 7 corresponding to the states of FIGS. 9a, 9b, and 9c, respectively. As can be seen from this figure, with the rotation of the rotating plate 7, the reaction force also continues to increase its absolute value, and the rate of increase of the reaction force further changes so that the time point in the state of FIG. .

In the above-described conventional accelerator pedal mechanism, the relative positional relationship between the locking points AB at the initial stage of depression of the pedal 2 is in the state shown in FIG. 9A, and by adjusting the ratio with the tension of the torsion spring 8, In particular, the configuration is such that the characteristic of increasing the reaction force by only the coil spring 9 is in the monotonically increasing range between θa and θb in FIG.

[0023]

In the conventional accelerator pedal mechanism having the above-described reaction force characteristics, the reaction force at the initial stage of depression is relatively light as described above. On the other hand, the delicate accelerator operation can be easily performed, but on the other hand, the stability is inevitably lowered, and there is a demerit that an unexpected sudden start is easily caused in a normal driving.

On the other hand, for example, when the accelerator reaction force at the initial stage of stepping on is set relatively large, a stable stepping can be performed, but a large stepping force is required. There is a disadvantage that the feet are easily fatigued.

Here, in the Japanese market, the former configuration in which the inching operation is performed by a light reaction force is accepted, while in the European market, the latter inching operation configuration by the stable reaction force is adopted. In fact, there is a situation in which vehicles having the respective configurations are mixed. For this reason, there is a problem that the operator who needs to operate both vehicles has to feel uncomfortable with the accelerator operation every time they change, and the selection of both settings is also dependent on the personal preference of the driver Therefore, there has been a long-awaited need for a configuration in which both settings can be easily switched arbitrarily.

Therefore, in view of the above problems, the present invention easily switches the characteristic of increasing the pedal reaction force at the initial stage of pedal depression, which is an important factor in the operation performance of an industrial vehicle, particularly in inching operation performance, even during operation. An object of the present invention is to provide an accelerator pedal reaction force control device that can perform the control.

[0027]

Means for Solving the Problems The present invention is configured as follows to solve the above problems.

First, the present invention is applied to an accelerator pedal reaction force control device for controlling an accelerator reaction force when an accelerator pedal is depressed. In particular, the present invention is interlocked with the operation of depressing the accelerator pedal and reaches a rotation position corresponding to the depression angle. A first rotating member that rotates, a second rotating member that is rotatable in the same plane or substantially the same plane as the rotating plane of the first rotating member,
It is stretched between a first locking point set on the first rotating member and a second locking point set on the second rotating member, and applies an accelerator reaction force to the accelerator pedal. The first to provide
It is configured to include a return spring for urging the rotating member in one rotation direction thereof, and adjusting means for adjusting the position of the second locking point by changing the rotating position of the second rotating member.

Thus, the tension and the tension of the return spring are changed by rotating the second rotating member, thereby making it possible to easily and easily set the magnitude of the depressing reaction force of the accelerator pedal and the increasing characteristics. This is possible with a simple configuration.

The adjusting means includes a worm gear mechanism including a wheel-type gear serving also as part or all of the second rotating member, and a cylindrical screw-type gear meshing with the wheel-type gear; Worm gear turning means for turning the second turning member via the wheel type gear by turning the gear,
In particular, the worm gear rotating means is constituted by an electric motor connected to the cylindrical screw gear.

Thus, automatic and accurate rotation control by the electric force of the wheel-type gear urged by the return spring can be performed. Furthermore, in the worm gear mechanism, since the rotation of the wheel-type gear can be performed only by rotating the cylindrical screw-type gear with only a small force, a small output motor can be adopted as a driving means of the cylindrical screw-type gear, and the worm gear mechanism has The transmission of rotational force is possible only in one direction from the cylindrical screw type gear to the wheel type gear, and as a result, the wheel type gear is fixed without rotating unless the cylindrical screw type gear is rotated, so-called self-locking Since the mechanism works, reliable and stable operation can be achieved without providing a lock mechanism.

Further, according to the present invention, a rotational position detecting means for detecting a rotational position of the second rotating member, a rotational position inputting means for inputting a rotational position of the second rotating member, and the second rotating member include: Control means for controlling the driving of the electric motor based on the rotational position detected by the rotational position detecting means so as to attain the desired rotational position input by the rotational position inputting means. The position detecting means is constituted by a potentiometer provided coaxially with the rotation axis of the second rotating member.

As a result, a simple but clear and accurate control operation can be performed.

The present invention further comprises a rotation range regulating means for forcibly stopping the rotation of the second rotation member at a desired rotation position without the potentiometer, and detecting the rotation position. Means for detecting an increase in the current of the electric motor when the second rotation member is forcibly stopped by the rotation range restricting means, and detecting the increase in the current by detecting the increase in the current. It is also configured to determine that the two rotating members are at the desired rotational position.

As a result, it is possible to reduce the manufacturing cost without using an expensive potentiometer.

In the present invention, the worm gear rotating means may not be an electric motor, but may be configured as a knob which is provided on a shaft of the cylindrical screw type gear and which can manually rotate the cylindrical screw type gear.

As a result, it is possible to greatly reduce manufacturing costs and improve reliability by reducing the frequency of failures.

Further, the present invention further comprises a rotation position display means for displaying the rotation position of the second rotating member, so that a clearer and more accurate control operation can be performed.

In the present invention, it is preferable that the rotation center axis be located on a tangent line which comes into contact with the movement locus of the first locking point at the first locking point position in a state where the accelerator pedal is not depressed. A two-rotation member is provided, and the position of the second locking point is controlled to be recognizable in each quadrant unit having the tangent as one dimensional axis on the second rotation member.

This makes it easy to arbitrarily switch the increasing characteristic of the pedal reaction force in which the position of the second locking point on the second rotating member changes for each quadrant unit.

[0041]

Embodiments of the present invention will be described below with reference to the drawings.

First, FIG. 1 is a schematic view of the structure of a mechanism and a control unit in an accelerator pedal reaction force control device according to a first embodiment of the present invention. In this figure, the toe board 11
In the floor panel of the vehicle cab, a finite length opening 11a is formed in the floor panel of the vehicle cab, and the accelerator pedal 12 is pivotally mounted on the toe board 11 so as to be rotatable around a shaft 12a provided on the lower side.

The arm 15 has an L-shape that can be rotated about a base shaft 15a, and the base shaft 15a is
1 is rotatably loosely fitted in a support cylinder 14 located below the opening 11a in parallel with the first opening 1a.
A roller 16 is provided at the end of the accelerator pedal 1a, and is slidably in contact with the back surface of the accelerator pedal 12.

A torsion spring 18 is fitted in a gap between the inner diameter of the support cylinder 14 and the base shaft 15a. One end of the spring is fixed on the base shaft 15a, and the other end is fixed to the inner diameter of the support cylinder 14 respectively. I have.

A rotating plate 17 is vertically mounted on a shaft portion (a front side on the paper surface of the drawing) from which the base shaft 15a protrudes through the support cylinder 14, and a part thereof penetrates through the opening 11a. A protruding restricting portion 17a is formed.

A locking point A is set near the outer edge of the rotating plate 17 at a position substantially opposite to the base shaft 15a of the regulating portion 17a, and one end of the coil spring 19 is inserted into a locking hole formed at that point. Is locked.

Here, the difference from the conventional structure is that a locking point B for locking the other end of the coil spring 19 is substantially on the circumference of the wheel type gear 22 which is a component in the worm gear mechanism 21 installed on the vehicle body. And the coil spring 19 is stretched. Further, the side surface of the wheel-type gear 22 on the side where the coil spring 19 is locked is on a flat surface where the rotation shaft does not protrude, and even if the wheel-type gear 22 rotates 360 degrees or more, the coil spring 19 is securely locked at the locking point B. Is in a possible configuration.
It should be noted that this wheel type gear 22
The rotation shaft center Og is axially provided so as to be located on the tangent line L1 which is in contact with the movement locus arc S of the locking point A at the locking point A position when the accelerator pedal 12 is not depressed at all.

The torsion spring 18 and the coil spring 19
The two springs are characterized in that the biasing force (torsional force or tension) is linearly proportional to torsion or elongation.

At the tip end where the base shaft 15a protrudes through the support cylinder 14, a potentiometer 10 for accelerator output is provided.
Is provided on the shaft.

In this configuration, the accelerator pedal 1
By depressing 2, the rotation angle of the base shaft 15a is output from the potentiometer 10 as the accelerator depression amount while simultaneously providing an increased reaction force due to the urging forces of the two springs.

The driving of the worm gear mechanism 21 (specifically, the rotation driving of the cylindrical screw gear 23) in the configuration of the driving section is performed by an electric motor 24,
U25 controls the drive of the electric motor 24 based on the operation information input from the operator via the switch 26,
At the same time, the display 27 displays the rotational position information of the wheel-type gear 22 from the potentiometer 20 (filled with a broken line) coaxially with the rotation axis of the wheel-type gear 22 to the operator.

The relative positional relationship between the locking points A and B for locking both ends of the coil spring 19 is roughly controlled by the control device having the above configuration into two states as shown in FIG. .

FIG. 2 shows a state in which the accelerator pedal 12 is not depressed at all. Og in the figure indicates the center of rotation of the wheel-type gear 22, L2 indicates tangent lines L1 and O2.
The lines orthogonal to g are indicated by Θa, Θb, Θc, and Θd, which indicate the angle range of each quadrant unit obtained by dividing the entire peripheral angle of the wheel gear 22 by L1 and L2. Further, it is assumed that the locking points Ba and Bb for locking in the states of the coil springs 19a and 19b in the drawing are arranged at intermediate positions between Θa and Θb, respectively.

In the above diagram, when attention is paid to the relative positional relationship between the locking points A and B, the locking points A and Ba for locking both ends of the coil spring 19a are at the same positions as those in FIG. Therefore, as described above, the increase characteristic of the reaction force by only the coil spring 19a at the initial stage of pedal depression in this state corresponds to the characteristic between θa and θb in FIG. 10, and therefore, the urging force of the torsion spring 8 In this case, the pedal reaction force in the case of integration with the above has an increasing characteristic shown by a curve Ca in FIG.

As shown by the curve in FIG.
The characteristic that the rate of increase of the reaction force is particularly small at the initial stage of depression of the pedal means that the accelerator operation in the inching operation is a light operation in which the pedal force is particularly suppressed to a small value.

On the other hand, the coil spring 19b shown in FIG.
The locking points A and Bb for locking both ends of the coil spring 19b are in the same positional relationship as in FIG.
The increase characteristic of the reaction force due to only this corresponds to the characteristic between θb and θc in FIG. 10, and in this case, the integrated pedal reaction force becomes the increase characteristic indicated by the curve of Cb in FIG.

As shown by the curve in the figure, the characteristic that the rate of increase of the reaction force is particularly large at the initial stage of the depression of the pedal means that the accelerator operation in the inching operation requires a particularly depressing force and is stable. Become.

The distinction between the above two characteristics is shown in FIG.
An angular range divided by a tangent L1 on the wheel-type gear 22, that is, a range obtained by combining Θb and Θc,
コ イ ル a and Θd are divided into respective ranges, and the angle range divided by the orthogonal line L2, that is, the range combining た a and Θb and the range combining Θc and Θd, The difference is in the length of elongation.

Considering these, the locking points Ba, B are located at the intermediate positions of the angular ranges Θa, Θb, Θc, Θd in each quadrant unit.
The increase characteristics of the respective reaction forces when b, Bc, and Bd are located are represented by curves Ca, Cb, Cc, and Cd shown in FIG.

In the figure, the curves Ca and Cd and the curves Cb and Cc are almost similar to each other, and the combination of the curves Ca and Cb, and the curves Cc and Cd
The combination of moves almost parallel to the direction of the pedal reaction force.

As described above, by rotating the wheel-type gear 22 to move the locking point B, roughly four types of characteristic curves of the increase of the reaction force can be obtained.

More specifically, the CPU 25 controls the electric motor 24 based on the rotation angle information from the potentiometer 20 installed on the wheel type gear 22 so as to move the locking point B to a set rotation position where an arbitrary characteristic can be obtained. By doing.

This is because, in the inching operation particularly using the operation at the initial stage of pedal depression described above, the characteristic can be selected so as to prioritize either the lightness of the pedaling force or the operational stability. It is a configuration that also enables two-step adjustment of the magnitude of the typical reaction force.

In this embodiment, the switch 26 is configured to be able to select the above four modes as shown in FIG. 1, and the display 27 is configured to display the selected mode. As described above, it is possible to easily and accurately select and switch the increasing characteristic of the pedal reaction force in real time even during driving of the vehicle.

An electric motor 24 driven by using the worm gear mechanism 21 as a rotating means of the locking point B
Can be driven with a relatively small output, and since it has a self-locking mechanism, reliable and stable operation is possible without providing a lock mechanism.

In the present embodiment, the rotation plate 17
Is not necessarily limited to a plate-like form, but may be any shape as long as it is rotatable about a base shaft. For example, a rod-like form other than the plate-like form may be used. Further, the second rotating member described in the claims does not need to be the wheel-type gear 22 in the present embodiment at all, and has an arc shape only at least in a necessary range (a range in which it meshes with the cylindrical screw-type gear 23). It is sufficient that gear teeth are formed on the other portion, and other portions may also be formed in a rod-like form.

In the first embodiment, the rotation center axis of the wheel-type gear 22 having the locking point B substantially on the circumference thereof is set to be located on the tangent line L1, but the present invention is not limited to this. Without limitation, a configuration in which the wheel-type gear 22 is installed at another position is also possible, and the position of the locking point B is moved in each quadrant of the wheel-type gear 22 to change the increase / decrease characteristic of the pedal reaction force. Switch 26
As a Hi / Lo switching mechanism, a simple adjustment configuration in which the initial tension of the coil spring 19 is continuously increased or decreased by simply rotating the wheel-type gear 22 may be adopted. In this case, a configuration in which an increase or decrease of the pedal reaction force is displayed on the display 27 by a level meter is preferable.

However, in order to always secure the urging of the rotating plate 17 in the return direction by the coil spring 19 (the pedal reaction force by the coil spring 19), the moving range of the locking point B is as shown by the hatched area in FIG. At the position of the locking point A in a state where the accelerator pedal 12 is not depressed, the coil spring 19 is always contained within the range on the return direction side of the rotary plate 17 with the line L3 perpendicular to the movement locus arc S of the locking point A as the boundary. Need to be configured to be installed.

In addition to the configuration in which the rotational position of the wheel type gear 22 is recognized by the potentiometer 20 as in the first embodiment, a projection 22a is provided on a part of the outer periphery of the wheel type gear 22, as shown in FIG. It is also possible to adopt a configuration in which the rotation range of the protrusion 22a is regulated by the two stoppers 28.

In this case, the detection of the rotation direction of the wheel-type gear (that is, the rotation direction of the electric motor) and the projection 2
When the rotation of the wheel-type gear 22 is forcibly stopped by the contact of the stopper 2a with the stopper 28, the CPU 25 detects an increase in the motor current and stops the current. In this case, the switch 26 is used as a Hi / Lo switching mechanism to simply rotate the wheel-type gear 22 continuously, and the protrusion 22a abuts against the stopper 28 so that the wheel-type gear 2
When the rotation of the motor 2 is forcibly stopped, the CPU 25 detects an increase in the motor current and stops the current. With this configuration, an expensive potentiometer 2 is used.
Manufacturing costs can be reduced without using 0.

In addition to the configuration in which the worm gear mechanism 21 is driven by driving the electric motor 24, a knob 29 may be provided on the shaft of the cylindrical screw-type gear 23 as shown in FIG. It is possible. Further knob 29
By providing a sliding contact surface having an intermittent seating position, intermittent switching adjustment can be performed. With such a simple configuration, it is possible to significantly reduce manufacturing costs and improve reliability by reducing the frequency of failures.

[0072]

As described in detail above, according to the accelerator pedal reaction force control apparatus of the present invention, the pedal reaction at the initial stage of pedal depression, which is an important factor in the operation performance of an industrial vehicle, particularly, the inching operation performance, is considered. The force increasing characteristic can be easily switched even during operation, and the magnitude of the overall reaction force can be switched stepwise.

Further, by adopting a relatively simple configuration using a worm gear mechanism, it is possible to drive with a small output motor, and to perform self-locking for reliable and stable operation, but at a low cost. Becomes possible.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of an accelerator pedal reaction force control device according to a first embodiment of the present invention.

FIG. 2 is a diagram illustrating a relative positional relationship between locking points A and B due to rotation of a wheel-type gear.

FIG. 3 is a diagram showing an increase characteristic curve of a pedal reaction force at each position of a locking point B;

FIG. 4 is a diagram illustrating a movable range of a locking point B;

FIG. 5 is a configuration diagram of an accelerator pedal reaction force control device according to a second embodiment.

FIG. 6 is a configuration diagram of an accelerator pedal reaction force control device according to a third embodiment.

FIG. 7 is a configuration diagram of a conventional accelerator pedal reaction force control device.

FIG. 8 is a diagram showing an increase characteristic curve of a pedal reaction force of a conventional configuration.

FIG. 9 is a diagram illustrating a relative positional relationship between locking points A and B due to rotation of a rotating plate.

FIG. 10 is a diagram showing an increase characteristic curve of a reaction force caused only by a coil spring due to rotation of a rotating plate.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 10 Accelerator output potentiometer 11 Toe board 11a Opening 12 Accelerator pedal 14 Support cylinder 15 Arm 15a Base shaft 16 Roller 17 Rotating plate 18 Torsion spring 19, a, b Coil spring 20 Wheel-type gear potentiometer 21 Worm gear 22 Wheel-type gear 22a Projection 23 Cylindrical screw gear 24 Electric motor 25 CPU 26 Switch 27 Display 28 Stopper 29 Knob A Rotating plate side locking point B, a, b, c, d Wheel type gear side locking point Og Rotation center of wheel type gear S Movement locus arc of the locking point A L1 A tangent of the arc S passing through the Og L2 An orthogonal line orthogonal to the tangent L1 at Lg L3 An orthogonal line orthogonal to the tangent L1 at the anchoring point A Θa, b, c, d Wheel-type gear Angle range θa, b, c in quadrant units of rotation

Claims (10)

[Claims] An accelerator pedal reaction force control device for controlling an accelerator reaction force when an accelerator pedal is depressed, wherein the first rotation is performed in conjunction with a depression operation of the accelerator pedal to a rotation position corresponding to the depression angle. A moving member; a second rotating member rotatable in the same plane or substantially the same plane as the rotating plane of the first rotating member; and a first locking point set on the first rotating member. And a second locking point set on the second rotating member, the first locking member being adapted to provide an accelerator reaction force to the accelerator pedal.
A return spring for urging the rotating member in one rotation direction thereof; and adjusting means for changing the rotational position of the second rotating member to adjust the position of the second locking point. Accelerator pedal reaction force control device. 2. The worm gear mechanism comprising: a wheel-type gear serving also as a part or the entirety of the second rotating member; and a cylindrical screw-type gear meshing with the wheel-type gear; The accelerator pedal reaction force control device according to claim 1, further comprising: a worm gear rotating unit that rotates the second rotating member via the wheel-type gear by rotating a gear. 3. The accelerator pedal reaction force control device according to claim 2, wherein said worm gear rotating means is an electric motor connected to said cylindrical screw type gear. 4. A rotation position detection means for detecting a rotation position of the second rotation member; a rotation position input means for inputting a rotation position of the second rotation member; 4. A control means for controlling the drive of the electric motor based on the rotational position detected by the rotational position detecting means so as to be a desired rotational position inputted by the position input means, further comprising: An accelerator pedal reaction force control device as described in the above. 5. The accelerator pedal reaction force control device according to claim 4, wherein said rotational position detecting means is a potentiometer provided coaxially with a rotation axis of said second rotating member. 6. The accelerator pedal reaction force control device according to claim 4, further comprising a rotation range restricting means for forcibly stopping the rotation of said second rotation member at a desired rotation position. 7. The rotation position detection means is means for detecting an increase in the current of the electric motor when the second rotation member is forcibly stopped by the rotation range restriction means. The accelerator pedal reaction force control device according to claim 6, wherein the second rotation member is determined to be at the desired rotation position by detecting an increase in current. 8. The accelerator according to claim 2, wherein said worm gear rotating means is a knob provided on a shaft of said cylindrical screw type gear and capable of manually rotating said cylindrical screw type gear. Pedal reaction force control device. 9. The apparatus according to claim 1, further comprising rotation position display means for displaying a rotation position of said second rotating member.
An accelerator pedal reaction force control device according to any one of claims 1 to 8. 10. The second rotation so that the rotation center axis is located on a tangent line in contact with a movement locus arc of the first locking point at the first locking point position in a state where the accelerator pedal is not depressed. 10. A moving member, wherein the position of the second locking point is controlled to be recognizable on the second rotating member in a unit of a quadrant having the tangent as one dimensional axis. The accelerator pedal reaction force control device according to any one of the above.