JP2012250613A - Accelerator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an accelerator for changing hysteresis characteristics that generates a difference in a pedal effort of an accelerator pedal.SOLUTION: A lever 55 transmits the rotation of a pedal arm 51 to a hysteresis rotary shaft 41 through a roller 52. A screw 552 formed at an end 551 of the lever 55 is connected to a screw hole 411a formed at an end 411 of the hysteresis rotary shaft 41. Tightening torque applied to the screw portion 552 is changed when changing a mounting angle to the hysteresis rotary shaft 41 of the lever 55. At this moment, the rotation angle of the hysteresis rotary shaft 41 supports the change of the relative position with ends 431 and end 432 of a hysteresis spring 43 one-on-one. Therefore, an energizing force generated by the hysteresis spring 43 is changed by changing the mounting angle to the hysteresis rotary shaft 41 of the lever 55.

Description

  The present invention relates to an accelerator device.

  2. Description of the Related Art Conventionally, an accelerator device that controls the acceleration state of a vehicle according to the amount of depression of an accelerator pedal by a driver is known. The accelerator device includes a rotor that interlocks with the rotation of the accelerator pedal. The frictional force acting on the rotor varies depending on the rotation angle of the accelerator pedal and the increase / decrease state of the rotation angle. The accelerator device has a hysteresis characteristic in which a difference is generated between a pedaling force required when the accelerator pedal is depressed and a pedaling force required when the accelerator pedal is returned due to a change in the friction amount acting on the roller. Patent Document 1 describes an accelerator device that can change the set length of a spring that applies a biasing force to a rotor. Thereby, in the accelerator apparatus of patent document 1, the secular change of the frictional force which acts on a rotor can be prevented.

JP 2007-253869 A

  However, in the accelerator device described in Patent Document 1, a hysteresis mechanism is configured using a large number of components. Therefore, individual differences occur in the hysteresis characteristics generated by the hysteresis mechanism due to variations in the dimensions of the constituent parts.

  An object of the present invention is to provide an accelerator device capable of changing a hysteresis characteristic that generates a pedaling force difference of an accelerator pedal.

  According to the first aspect of the present invention, the accelerator device includes a support member that can be attached to the vehicle body, a pedal portion that is rotatably supported at one end by the support member, a first rotating shaft, a first return spring, and a rotation angle detecting means. , A second rotating shaft, a second return spring, a hysteresis mechanism part, a link mechanism part, a lever, and an attachment angle changing means. The support member supports a first rotation shaft that is interlocked with the rotation of the pedal portion and a second rotation shaft that is provided parallel to the first rotation shaft. The rotation angle detection means detects a relative rotation angle of the first rotation shaft with respect to the support member. The first return spring allows the rotation of the first rotating shaft in the accelerator opening direction when the rotational force generated by the driver's stepping is transmitted, and closes the accelerator when the rotational force is released. A first biasing force that returns the direction is generated. The second return spring allows the rotation of the second rotating shaft in the accelerator opening direction when the rotational force generated by the driver's stepping is transmitted, and closes the accelerator when the rotational force is released. A second urging force that returns the direction is generated. The hysteresis mechanism acts so as to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation shaft when the rotation force acting on the second rotation shaft increases, and the rotation force acting on the second rotation shaft. When is released, a hysteresis characteristic is generated that acts to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation shaft. The link mechanism unit is interlocked so that the rotation angle of the first rotation shaft and the rotation angle of the second rotation shaft are determined in a one-to-one correspondence.

  The lever is connected to one end of the second rotation shaft. The attachment angle changing means can change the attachment angle of the lever with respect to the second rotation shaft. The accelerator device changes the hysteresis characteristic by the mounting angle changing means.

  The accelerator device tries to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation shaft when the rotational force of the second rotation shaft increases. This prevents the vehicle from suddenly accelerating when the accelerator pedal is depressed. On the other hand, the accelerator device tries to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation shaft when the rotational force of the second rotation shaft is released. This prevents the vehicle from decelerating suddenly when the accelerator pedal is returned. The hysteresis mechanism unit thus generates a hysteresis characteristic that acts to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation axis.

  When the rotational force of the second rotating shaft is increased or decreased by the driver's stepping, the second return spring applies a second urging force that urges the second rotating shaft in either the opening direction or the closing direction of the accelerator. appear. The magnitude of the second urging force is determined by the relative positions of both ends of the second return spring. That is, the second urging force is calculated from the change in the relative position of both ends with respect to the relative position of both ends in a state where the second return spring does not generate the urging force. Further, the rotation angle of the second rotating shaft on which the second urging force acts has a one-to-one correspondence with the change in the relative position of both ends of the second return spring. The accelerator apparatus according to claim 1 includes an attachment angle changing means for changing an attachment angle of the lever with respect to the second rotation shaft. When changing the attachment angle of the lever with respect to the 2nd rotating shaft, both ends of the 2nd return spring are in a fixed relative position. Thereby, the attachment angle of a lever is changed with respect to the 2nd return spring which has the both ends which are a fixed relative position. In addition, as the both ends which are a fixed relative position, the both ends which are in a relative position where the second return spring does not generate the second biasing force are desirable. The range of the movable angle of the lever from the fully closed state to the fully open state of the accelerator is constant regardless of whether or not the mounting angle of the lever with respect to the second rotating shaft is changed. Therefore, by changing the mounting angle of the lever with respect to the second rotating shaft, the positions of both end portions of the second return spring within the range of the movable angle of the lever are changed. In the accelerator apparatus according to the first aspect, the hysteresis characteristic can be changed by changing the mounting angle of the lever with respect to the second rotating shaft.

  In the accelerator device according to the first aspect, the variation in the hysteresis characteristic caused by the variation in the parts constituting the hysteresis mechanism can be changed by the attachment angle changing and updating means. Therefore, the design tolerance of the parts constituting the hysteresis mechanism can be increased as compared with the conventional case.

  In addition, since the accelerator device that has been incompatible in the inspection of the hysteresis characteristics so far requires reassembly, the number of steps in the manufacturing process increases. However, in the accelerator device according to the first aspect, the hysteresis characteristic can be changed by the attachment angle changing means at the final stage of the manufacturing process. Thereby, the man-hour for reassembly becomes unnecessary and manufacturing cost can be reduced.

According to the second aspect of the invention, the attachment angle changing means is the screw hole portion of the second rotating shaft and the screw shaft of the lever coupled to the screw hole of the screw hole portion.
A screw shaft is formed at the end of the lever connected to the second rotation shaft. The screw shaft is coupled to a screw hole formed in the screw hole portion of the second rotating shaft. Therefore, when changing the mounting angle of the lever with respect to the second rotation shaft, the coupling state of the screw shaft to the screw hole is changed.

According to the invention described in claim 3, when changing the mounting angle of the lever with respect to the second rotating shaft, the tightening torque applied to the screw shaft is changed.
The screw shaft of the lever is coupled to the screw hole of the second rotation shaft. When changing the mounting angle of the lever with respect to the second rotating shaft, the tightening torque applied to the screw shaft is changed. By increasing the tightening torque, the lever rotates in the clockwise direction with respect to the second rotation shaft, and the mounting angle of the lever with respect to the second rotation shaft is changed. On the other hand, by reducing the tightening torque, it rotates in the counterclockwise direction with respect to the second rotating shaft, and changes the mounting angle of the lever with respect to the second rotating shaft. Therefore, when the positions of both ends of the second return spring are changed within the range of the lever movable angle, the tightening torque applied to the screw shaft can be changed, and the hysteresis characteristics can be changed.

It is a fragmentary sectional view showing the whole accelerator device by one embodiment of the present invention. It is a principal part expanded sectional view of the accelerator apparatus by one Embodiment of this invention. It is a side view of the accelerator apparatus by one Embodiment of this invention. It is a side view of the accelerator apparatus by one Embodiment of this invention, Comprising: It is a side view at the time of removing a cover. (A) The typical side view showing the position of the lever of the accelerator apparatus by one Embodiment of this invention, (b) The typical side view showing the position of the lever different from (a). It is a schematic diagram showing the relationship between the tightening torque of a lever and the angle of a lever in the accelerator apparatus by one Embodiment of this invention. (A) Schematic diagram showing the relationship between the rotation angle of the accelerator pedal and the load in the hysteresis mechanism section in the accelerator device according to one embodiment of the present invention, (b) The relationship between the rotation angle of the accelerator pedal and the load in the return mechanism section It is the schematic diagram which shows, (c) The schematic diagram which shows the relationship between the rotation angle and load of the accelerator pedal in the whole accelerator device. (A) The schematic diagram which shows the relationship between the spring set angle and load in the hysteresis mechanism part of the accelerator apparatus by one Embodiment of this invention, (b) The relationship between the rotation angle of the accelerator pedal and the load in the whole accelerator apparatus is shown. It is a schematic diagram.

Hereinafter, an accelerator device according to an embodiment of the present invention will be described with reference to the drawings.
(One embodiment)
An accelerator apparatus according to an embodiment of the present invention is shown in FIGS.
As shown in FIG. 1, the accelerator device 1 includes an accelerator pedal 10, an accelerator pedal rod 15, and a support portion 20. The accelerator device 1 is mounted on a vehicle and controls the acceleration state of the vehicle according to the amount of depression of the accelerator pedal 10 by the driver. The accelerator device 1 transmits information related to the rotation angle of the accelerator pedal 10 to an electronic control unit (ECU) of the vehicle, and controls the throttle device based on the rotation angle information. Thereby, the acceleration state of the vehicle is controlled. Hereinafter, the upper side of FIGS. 1 to 4 is “upper”, the lower side of FIGS. 1 to 4 is “lower”, the right side of FIGS. 1 and 2 is “right”, and the left side of FIGS. It will be described as “left”.

  The accelerator pedal 10 is provided at one end of the accelerator pedal rod 15. The other end of the accelerator pedal rod 15 is fixed to one end of a connecting member 26 protruding from the left side surface of the cover 25 using a screw 27 as shown in FIG. The accelerator pedal rod 15 corresponds to a “pedal part” recited in the claims.

  Next, the structure of the support portion 20 will be described with reference to FIGS. 2 is a cross-sectional view of the support portion 20 shown in FIG. 4 taken along the line II-II. 3 is a view taken in the direction of arrow III in FIG. FIG. 4 is a side view of FIG. 3 with the cover 25 removed from the support portion 20.

  The support unit 20 includes a return mechanism unit 30, a hysteresis mechanism unit 40, a link mechanism unit 50, a rotation angle detection sensor 57 as a “rotation angle detection unit”, a terminal unit 60, a cover 25, and the like. As shown in FIG. 2, the outline of the support portion 20 is formed by a first housing 21, a second housing 22, a third housing 23, and a cover 25. The return mechanism 30 is accommodated in a space formed by the first housing 21 and the third housing 23. The hysteresis mechanism 40 is accommodated in a space formed by the first housing 21 and the second housing 22. Details of the return mechanism 30 and the hysteresis mechanism 40 will be described later.

  The first housing 21 includes a substantially flat base portion 211 and a housing portion 212 having a shape in which two substantially bottomed cylinders are adjacent in the vertical direction. The first housing 21 is made of a resin having a metal inserted therein. The base 211 is formed with two bolt holes 211 a at the upper portion of the support portion 20 and one lower portion of the support portion 20 for attaching the support portion 20 to the vehicle body wall surface 100 as a “vehicle body”. Thereby, as shown in FIGS. 3 and 4, the accelerator device 1 is attached to the vehicle body wall surface 100 by the three bolts 11.

  The housing portion 212 of the first housing 21 is provided on the side opposite to the side attached to the vehicle body with respect to the base portion 211, that is, in front of the paper surface in FIG. As shown in FIG. 2, the bottom portion 212a of the housing portion 212 is located on the right side of the support portion 20, and the terminal portion 60 is adjacent to the right side of the bottom portion 212a. The accommodating part 212 has two openings in the left direction. The upper part 212 b of the housing part 212 forms an opening on the upper side of the housing part 212. An end 212 c of the upper part 212 b opposite to the side connected to the bottom 212 a is in contact with the end 221 of the second housing 22. Further, the lower portion 212 d of the housing portion 212 forms an opening on the lower side of the housing portion 212. An end 212e of the lower part 212d opposite to the side connected to the bottom 212a abuts on the end 231 of the third housing 23.

  The second housing 22 has a bottomed cylindrical shape with a substantially U-shaped cross section having an opening in the right direction of FIG. The end portion 221 on the opening side of the second housing 22 contacts the end portion 212c of the upper portion 212b as described above. Thereby, the accommodation chamber 213 is formed by the first housing 21 and the second housing 22. The accommodation chamber 213 accommodates a hysteresis mechanism 40 described later.

  As shown in FIG. 4, the second housing 22 has three second attachment portions 222 on the outer edge. Of the three second mounting portions 222, the two second mounting portions 222 are formed on the upper outer edge portion of the second housing 22. One second mounting portion 222 is formed on the lower outer edge of the second housing 22. The second attachment portion 222 is used for fastening and fixing with the first attachment portion 217 of the first housing 21.

  The third housing 23 has a bottomed cylindrical shape with a substantially U-shaped cross section having an opening in the right direction of FIG. The third housing 23 is provided below the second housing 22 so as to be adjacent to the second housing 22. As described above, the end 231 of the third housing 23 abuts on the end 212e of the lower portion 212d. Thereby, the accommodation chamber 214 is formed by the first housing 21 and the third housing 23. The return mechanism 30 is accommodated in the accommodation chamber 214. As shown in FIG. 4, the third housing 23 has two third attachment portions 232 on the outer edge. A bolt hole (not shown) is formed in the third attachment portion 232, and the third housing 23 is fixed to the first housing 21 by a bolt through the bolt hole.

Next, the return mechanism unit 30 will be described.
The return mechanism unit 30 is located below the support unit 20. Specifically, it is accommodated in an accommodation chamber 214 formed by the first housing 21 and the third housing 23. The return mechanism unit 30 includes a return rotation shaft 31, a return spring 32, a bearing 33, a rotor 34, and the like. The return mechanism unit 30 applies a biasing force to the accelerator pedal 10 in a direction opposite to the stepping direction according to the rotation angle of the accelerator pedal 10 when the accelerator pedal 10 is stepped on. Thereby, the accelerator pedal 10 is held at a predetermined rotational position (fully closed position) when the driver does not depress the accelerator pedal 10.

  The return rotation shaft 31 as the “first rotation shaft” is provided in the horizontal direction with respect to the support portion 20. The left end 311 of the return rotation shaft 31 is inserted into a through hole 233 formed in the third housing 23. A bearing 33 provided on the inner wall of the through hole 233 receives the end 311 of the return rotation shaft 31. The end portion 311 inserted through the through hole 233 passes through one end of the pedal arm 51 and is fixed to one end of the connecting member 26 connected to the accelerator pedal rod 15. The right end 312 of the return rotation shaft 31 is fixed to the rotor 34 that abuts on the lower portion 212 d of the housing portion 212. When the accelerator pedal 10 rotates as the driver depresses the accelerator pedal 10, the return rotation shaft 31 rotates at the same angle as the rotation angle of the accelerator pedal 10. Further, when the return rotation shaft 31 rotates, the rotor 34 also rotates by the same angle as the rotation angle of the accelerator pedal 10.

  The return spring 32 as the “first return spring” is a torsion spring in which a metal member is formed in a spiral shape. The torsion spring generates a biasing force in accordance with the angle of both ends with respect to the central axis of the torsion spring (hereinafter referred to as “spring set angle”). Specifically, the angle (hereinafter referred to as the angle between both ends when the biasing force is not generated (hereinafter referred to as “free angle”) and the central axis of the torsion spring when both ends are brought close to each other (hereinafter referred to as “free angle”). , The biasing force of the torsion spring is calculated from the difference from “the biasing force generation angle”). The return spring 32 of the first embodiment is provided in the return mechanism portion 30 in a state having an urging force generation angle.

  As shown in FIG. 2, the return spring 32 accommodates the return rotation shaft 31 in the spiral shape along the axial direction. An end 321 of the return spring 32 is fitted into a fitting hole 234 a formed in the inner bottom wall 234 of the third housing 23. The other end 322 of the return spring 32 is connected to the rotor 34.

  The rotor 34 has a substantially cylindrical shape. A return rotating shaft 31 is connected to the rotor 34. An end 322 of a return spring 32 is connected to the rotor 34 outside the return rotation shaft 31 connected to the rotor 34. Accordingly, when the return rotation shaft 31 rotates, the rotor 34 rotates and the end 322 of the return spring 32 moves in the rotation direction of the return rotation shaft 31. The end portion 341 of the rotor 34 is in contact with the bottom portion 212 a of the housing portion 212 of the first housing 21. The rotor 34 has one S-pole magnet and one N-pole magnet 342 on the inner wall of the end portion 341 on a diagonal line. The magnet 342 rotates in accordance with the rotation of the rotor 34.

  The rotation angle detection sensor 57 is provided adjacent to the rotor 34. The rotation angle detection sensor 57 has a protrusion 571 that protrudes into the rotor 34. A total of two Hall ICs (not shown) are provided on the diagonal of the protrusion 571 in the protrusion 571. The rotation angle detection sensor 57 detects the rotation angle of the rotor 34 using two Hall ICs. Specifically, when the accelerator pedal 10 is rotated by the driver's depression of the accelerator pedal 10, the rotor 34 rotates at the same angle as the rotation angle of the accelerator pedal 10. At this time, the magnet 342 provided on the inner wall of the rotor 34 also rotates by the same angle. As a result, the magnetic field around the protrusion 571 changes. The Hall IC of the rotation angle detection sensor 57 converts a magnetic field change into an electric signal. The electrical signal is transmitted to an electronic control device (hereinafter referred to as “ECU”) mounted on the vehicle via the connector 61 of the terminal unit 60. Thereby, the ECU can detect the rotational position of the accelerator pedal 10. Thus, the rotation angle detection sensor 57 is used to detect the rotation position of the accelerator pedal 10.

Next, the hysteresis mechanism 40 will be described.
The hysteresis mechanism part 40 is located on the upper part of the support part 20. Specifically, the hysteresis mechanism 40 is accommodated in an accommodation chamber 213 formed by the first housing 21 and the second housing 22. The hysteresis mechanism 40 includes a hysteresis rotation shaft 41, a pedal rotor 42, a hysteresis spring 43, a bearing 45, and the like. Hysteresis mechanism 40 provides a difference between the pedaling force required when the driver depresses accelerator pedal 10 and the pedaling force required when the driver depresses accelerator pedal 10. Thereby, the operativity of the accelerator pedal 10 by a driver | operator improves.

  The hysteresis rotation shaft 41 as the “second rotation shaft” is provided in the horizontal direction with respect to the support portion 20. The left end 411 of the hysteresis rotation shaft 41 is inserted into a through hole 223 formed in the second housing 22. A screw hole 411a having an opening in the left direction is formed in the end portion 411 protruding from the second housing 22. The screw hole 411a is coupled to a screw portion 552 formed in a lever 55 of the link mechanism portion 50 described later. Further, the right end 412 of the hysteresis rotation shaft 41 is inserted into a recess 215 formed in the bottom 212 a of the first housing 21. A bearing 45 for receiving the hysteresis rotation shaft 41 is provided on the inner wall of each of the through hole 223 and the recess 215. The hysteresis rotation shaft 41 rotates in conjunction with the rotation of the lever 55. At this time, the pedal rotor 42 in contact with the outer wall of the hysteresis rotation shaft 41 also rotates at the same angle as the rotation angle of the hysteresis rotation shaft 41.

  The pedal rotor 42 has a shape in which two hollow cylinders having different diameters are connected in the axial direction. A hysteresis rotation shaft 41 is inserted into the pedal rotor 42. The large diameter portion 421 of the pedal rotor 42 is provided on the end portion 411 side of the hysteresis rotation shaft 41. An annular second friction plate 424 is provided on the wall surface 421a of the large diameter portion 421 on the second housing 22 side. The second friction plate 424 contacts the inner bottom wall 224 of the second housing 22. As a result, the pedal rotor 42 can slide with the second housing 22 via the second friction plate 424. The small diameter portion 422 is connected to the wall surface 421b of the large diameter portion 421 on the first housing 21 side. A plurality of helical teeth 425 having inclined surfaces are formed in the circumferential direction in the radially outward direction of the small diameter portion 422 connected to the wall surface 421b. The plurality of helical teeth 425 abut on the multiple helical teeth 442 formed on the wall surface 441 of the rotor 44 on the second housing 22 side. The small diameter portion 422 of the pedal rotor 42 is provided on the first housing 21 side of the hysteresis rotation shaft 41. A rotor 44 is provided on the first housing 21 side of the small diameter portion 422.

  The rotor 44 circumscribing the small diameter portion 422 is formed in an annular shape. As described above, a plurality of helical teeth 442 are formed on the wall surface 441 of the rotor 44 on the second housing 22 side. On the other hand, an annular first friction plate 423 is provided on the wall surface 443 of the rotor 44 on the first housing 21 side. The first friction plate 423 is in contact with the inner bottom wall 216 of the first housing 21. Thereby, the rotor 44 can slide on the first housing 22 via the first friction plate 423.

  The hysteresis spring 43 as a “second return spring” is provided in the radially outward direction of the pedal rotor 42. The hysteresis spring 43 is a torsion spring like the return spring 32. The wire diameter of the metal wire forming the hysteresis spring 43 is larger than the wire diameter of the return spring 32. Moreover, the hysteresis spring 43 of this embodiment is provided in the hysteresis mechanism part 40 in the state which has the biasing force generation angle which generate | occur | produces a biasing force.

  An end 431 of the hysteresis spring 43 is fitted into a fitting hole 224 a formed in the inner bottom wall 224 of the second housing 22. The other end 432 of the hysteresis spring 43 is inserted into a through hole 444 formed in the rotor 44.

  Next, the link mechanism unit 50 will be described. As shown in FIG. 4, the link mechanism unit 50 includes a pedal arm 51, a roller 52, a lever 55, and the like. The link mechanism unit 50 transmits the rotational motion of the return rotary shaft 31 to the hysteresis rotary shaft 41.

  The pedal arm 51 is made of metal. As shown in FIG. 4, the end 511 of the pedal arm 51 is fixed to the return rotation shaft 31. The end portion 512 of the pedal arm 51 abuts on the roller 52 so as to be slidable. Further, the pedal arm 51 regulates the rotation angle of the accelerator pedal 10. Specifically, a fully-closed stopper 225 and a fully-opened stopper 226 are formed so as to protrude from the second housing 22 in the rotation direction around the return rotation shaft 31 of the pedal arm 51. When the accelerator pedal 10 is not depressed and is in the fully closed position, the pedal arm 51 contacts the fully closed stopper 225 (see the solid line in FIG. 4). At this time, the return spring 32 of the return mechanism 30 has a biasing force that rotates the pedal arm 51 counterclockwise about the return rotation shaft 31 instead of the free angle as described above. However, since the pedal arm 51 contacts the fully closed stopper 225, it does not rotate any more. Further, as shown by the broken line in FIG. 4, when the accelerator pedal 10 is depressed and is in the fully open position, the pedal arm 51 contacts the fully open stopper 226. As a result, the pedal arm 51 does not rotate clockwise about the return rotation shaft 31 any more. The fully closed stopper 225 and the fully opened stopper 226 are formed of a resin containing metal inserted into the second housing 22.

  The roller 52 is rotatably provided at one end of the lever 55. The roller 52 slides on the pedal arm 51 in accordance with the movement of the pedal arm 51 around the return rotation shaft 31.

  The lever 55 rotatably supports the roller 52 as described above. The lever 55 transmits the rotation of the pedal arm 51 to the hysteresis rotation shaft 41 via the roller 52. As shown in FIG. 2, a screw portion 552 is formed at an end portion 551 opposite to the side where the roller 52 of the lever 55 is provided. The screw portion 552 as the “screw shaft” is coupled to the screw hole 411 a formed in the end portion 411 of the hysteresis rotation shaft 41. In the lever 55, the attachment angle of the lever 55 to the hysteresis rotation shaft 41 is changed by changing the tightening degree of the screw portion 552 into the screw hole 411a. Details will be described later.

  The cover 25 is attached to the left side of the support portion 20 as shown in FIGS. A link mechanism unit 50 is accommodated in the cover 25. Further, the cover 25 is formed with a through hole 251 through which the connecting member 26 protrudes. The connecting member 26 connected to the return rotating shaft 31 is inserted into the through hole 251 and protrudes to the outside of the cover 25 as shown in FIG. The cover 25 prevents foreign matter from entering the link mechanism unit 50, the return mechanism unit 30, and the hysteresis mechanism unit 40.

Next, based on FIG. 5 and FIG. 6, the change of the hysteresis characteristic when the attachment angle of the lever 55 with respect to the hysteresis rotation shaft 41 is changed will be described.
FIG. 5 shows a schematic view of the support portion 20 as seen from the left side as in FIG. FIG. 5A shows the position of the lever 55 when the hysteresis spring 43 is at a free angle, the position of the lever 55 when it is on the straight line 241, and the lever 55 and the pedal arm when the accelerator pedal 10 is fully closed. The positional relationship with 51 is shown. Hereinafter, the state of the relationship between the lever 55 and the hysteresis mechanism 40 in FIG. When the accelerator pedal 10 is in the fully closed state, the pedal arm 51 contacts the fully closed stopper 225. At this time, the lever 55 that rotates while sliding on the pedal arm 51 is positioned on the straight line 24. The lever 55 when the hysteresis spring 43 in FIG. 5A is at a free angle is positioned on the straight line 241 as described above. Thereby, in the pattern 1, when the accelerator pedal 10 is in the fully closed state, the biasing force acting on the accelerator pedal 10 is an angle θ1 formed by the straight line 24 and the straight line 241 with the center 551a of the end 551 as the corner vertex. This is a product of the spring constant of the hysteresis spring 43.

  Next, in the lever 55, the tightening torque to the screw hole 411a of the screw portion 552 is reduced. Thereby, the position of the lever 55 in a state where the hysteresis spring 43 is at a free angle rotates counterclockwise around the center 551a. FIG. 5B shows a state where the lever 55 is rotated by reducing the tightening torque to the screw hole 411a of the screw portion 552 from the state of FIG. 5A.

  FIG. 5B shows the position of the lever 55 when the hysteresis spring 43 is at a free angle, the position of the lever 55 when it is on the straight line 242, and the lever 55 and the pedal arm when the accelerator pedal 10 is fully closed. The positional relationship with 51 is shown. Hereinafter, the state of the relationship between the lever 55 and the hysteresis mechanism 40 in FIG. When the accelerator pedal 10 is fully closed, the lever 55 is positioned on the straight line 24. This is the same position as in FIG. On the other hand, the lever 55 when the hysteresis spring 43 in FIG. 5B is at a free angle is positioned on the straight line 242. Thereby, in pattern 2, when the accelerator pedal 10 is in the fully closed state, the urging force acting on the accelerator pedal 10 is an angle θ2 formed by the straight line 24 and the straight line 242 with the center 551a of the end portion 551 as the corner vertex. This is a product of the spring constant of the hysteresis spring 43.

  As shown in FIG. 5, the angle θ2 is larger than the angle θ1. Therefore, when the accelerator pedal 10 is fully closed, the urging force acting on the accelerator pedal 10 is greater in the pattern 2 than in the pattern 1.

  In FIG. 5, the urging force that acts on the accelerator pedal 10 when the accelerator pedal 10 is in the fully closed state has been described, but the same applies to the urging force that acts on the accelerator pedal 10 when the accelerator pedal 10 is in the fully open state. The angle range θ0 of the rotation angle θ from the fully closed state to the fully open state of the accelerator pedal 10 does not change in the pattern 1 and the pattern 2. Therefore, the biasing force acting on the accelerator pedal 10 in the fully open state in the pattern 1 is calculated from the total value of the angle θ1 and the angle range θ0 and the spring constant of the hysteresis spring 43. Further, the urging force acting on the accelerator pedal 10 in the fully open state in the pattern 2 is calculated from the total value of the angle θ2 and the angle range θ0 and the spring constant of the hysteresis spring 43. As described above, since the angle θ2 is larger than the angle θ1, the urging force acting on the accelerator pedal 10 in the fully opened state is larger in the pattern 2 than in the pattern 1.

FIG. 6 shows the relationship between the tightening torque of the screw portion 552 of the lever 55 to the screw hole 411a and the “initial lever angle”. Here, the “initial lever angle” is an angle at which the position of the lever 55 when the accelerator pedal 10 is in the fully closed state and the position of the lever 55 when the hysteresis spring 43 is at the free angle forms the center 551a as the apex of the corner. Say.
If the above-mentioned pattern 1 is the maximum value of the adjustable range of the tightening torque, the angle θ1 is the minimum value of the adjustable range of the initial lever angle. On the other hand, if the pattern 2 is the minimum value of the adjustable range of the tightening torque, the angle θ2 is the minimum value of the adjustable range of the initial lever angle. When the tightening torque to the screw hole 411a of the lever 55 is decreased, the initial lever angle is decreased and the urging force acting on the accelerator pedal 10 is also decreased.

(Function)
Next, the operation of the accelerator device 1 will be described with reference to FIG. FIG. 7A is a graph showing the load F necessary for maintaining the rotation angle θ with respect to the rotation angle θ of the accelerator pedal 10 in the hysteresis mechanism 40. The load F is a pedaling force necessary for the driver to maintain the rotation angle θ of the accelerator pedal 10. FIG. 7B is a graph showing the load F necessary for maintaining the rotation angle θ with respect to the rotation angle θ of the accelerator pedal 10 in the return mechanism 30. Moreover, FIG.7 (c) is a graph showing the sum total of the load F shown to Fig.7 (a) and (b).

  When the driver does not depress the accelerator pedal 10, the accelerator pedal 10 is in a predetermined position. That is, the rotation of the accelerator pedal 10 is restricted by the fully closed stopper 225 with which the pedal arm 51 is in contact. This position is set to a rotation angle θ = 0 degree of the accelerator pedal 10 (corresponding to the origin of the horizontal axis in FIGS. 7A to 7C).

  When the driver steps on the accelerator pedal 10, the rotation angle θ of the accelerator pedal 10 increases. That is, the value on the horizontal axis increases in the graph of FIG. At this time, in the hysteresis mechanism section 40, the load calculated from the spring constant of the hysteresis spring 43 and the biasing force generation angle of the hysteresis spring 43 corresponding to the rotation angle θx of the accelerator pedal 10 is applied to the first friction plate 423 and the first friction plate 423. A load Fx is generated by adding the frictional force between the housing 21 and the frictional force between the second friction plate 424 and the second housing 22. In the hysteresis mechanism 40, the helical teeth 425 formed on the pedal rotor 42 and the helical teeth 442 formed on the rotor 44 are engaged with each other while abutting on the inclined surfaces. When the driver depresses the accelerator pedal 10, the distance between the pedal rotor 42 and the rotor 44 is increased, the frictional force between the first friction plate 423 and the first housing 21, and the second friction plate 424 and the second housing 22. The frictional force increases. Thus, a frictional force having a magnitude corresponding to the rotation angle θx of the accelerator pedal 10 is applied to the surface of the first friction plate 423 on the first housing 21 side and the surface of the second friction plate 424 on the second housing 22 side. Works. Therefore, in the hysteresis mechanism 40, when the accelerator pedal 10 is depressed, a load Fx larger than the urging force of the hysteresis spring 43 alone is required (see FIG. 7A). On the other hand, in the return mechanism unit 30, an urging force corresponding to the rotation angle θx of the accelerator pedal 10 is generated (see FIG. 7B).

  When the driver releases the depression of the accelerator pedal 10, the rotation angle θ of the accelerator pedal 10 decreases. At this time, as shown in FIG. 7A, in the hysteresis mechanism section 40, when the rotation angle θ of the accelerator pedal 10 is small, the rotation of the accelerator pedal 10 is larger than when the rotation angle of the accelerator pedal 10 is large. The load F necessary for maintaining the angle θx is reduced. This is because the restoring force of the hysteresis spring 43 is relatively weakened by the frictional force between the first friction plate 423 and the first housing 21 and the frictional force between the second friction plate 424 and the second housing 22 described above. is there. On the other hand, in the return mechanism unit 30, an urging force corresponding to the rotation angle θx of the accelerator pedal 10 is generated (see FIG. 7B).

  FIG. 7C is a graph in which the loads F corresponding to the rotation angle θ of the accelerator pedal 10 in the hysteresis mechanism 40 and the return mechanism 30 described above are totaled. When the rotation angle θ of the accelerator pedal 10 increases due to the depression of the accelerator pedal 10 by the driver, the load F for maintaining the rotation angle θx of the accelerator pedal 10 increases according to the magnitude of the rotation angle θx. Further, when the driver releases the depression of the accelerator pedal 10, a load F for maintaining the rotation angle θx of the accelerator pedal 10 is also required according to the magnitude of the rotation angle θx. However, comparing the case where the rotation angle θ of the accelerator pedal 10 increases and the case where the rotation angle θ decreases, the load F required to maintain the rotation angle θx is different even at the same rotation angle θx. That is, at the rotation angle θx, the load F is smaller when the rotation angle θ decreases than when the rotation angle θ increases. As a result, when the driver depresses the accelerator pedal 10, the rotation angle θ of the accelerator pedal 10 does not suddenly increase, thereby preventing the vehicle from accelerating rapidly. Further, when the driver releases the depression of the accelerator pedal 10, the rotation angle θ of the accelerator pedal 10 is not suddenly reduced, so that the vehicle is prevented from decelerating rapidly.

  In the accelerator device 1 according to the present embodiment, when the magnitude of the load F with respect to the rotation angle θ of the accelerator pedal 10 is changed, the attachment angle of the lever 55 with respect to the hysteresis rotation shaft 41 is changed. At the stage of manufacturing the accelerator device 1, the accelerator device 1 is extracted from one product lot, and the relationship of the magnitude of the load F to the rotation angle θ of the accelerator pedal 10 is measured. At this time, the mounting angle of the lever 55 with respect to the hysteresis rotating shaft 41 is changed based on the measured value of the load F. Specifically, when the hysteresis spring 43 is at a free angle, the tightening torque to the screw hole 411a of the hysteresis rotating shaft 41 of the screw portion 552 of the lever 55 is changed. After the attachment angle of the lever 55 to the hysteresis rotation shaft 41 is determined, the lever 55 is moved to a position where the accelerator pedal 10 is fully closed. Thereby, the initial lever angle is determined. Thereafter, the hysteresis characteristic of the accelerator device in one lot is changed by similarly changing the tightening torque applied to the screw portion 552 of the lever 55 for the accelerator device of the same lot.

FIG. 8A shows the relationship between the spring set angle of the hysteresis spring 43 and the load F. FIG.
5A, the spring set angle of the hysteresis spring 43 used by the rotation of the accelerator pedal 10 is in the region shown in FIG. On the other hand, the spring set angle used in the pattern 2 of FIG. 5B is the region shown in FIG. As shown in FIG. 8A, the minimum value of the spring set angle is larger in the pattern 2 than in the pattern 1. Further, the maximum value of the spring set angle is larger in the pattern 2 than in the pattern 1. That is, the pedaling force required at the initial depression of the accelerator pedal 10 is larger in the pattern 2. Further, the pedaling force required when the accelerator pedal 10 is fully opened is larger in the pattern 2. The region of the spring set angle used is the same angle range for both pattern 1 and pattern 2.

From the relationship between the spring set angle of the hysteresis spring 43 and the load F shown in FIG. 8A, FIG. 8B shows the relationship between the rotation angle θ of the accelerator pedal 10 and the rotation angle θ of the accelerator pedal 10. The relationship with the required load F was shown.
In FIG. 8B, the solid line shows the relationship between the rotation angle θ of the accelerator pedal 10 and the load F in the case of the pattern 1, and the broken line shows the relationship between the rotation angle θ of the accelerator pedal 10 and the load F in the case of the pattern 2. . On the other hand, in the case of the pattern 2, the accelerator pedal 10 is operated with a smaller load F than the pattern 1 from the fully closed state to the fully open state of the accelerator pedal 10. The same applies to releasing the depression of the accelerator pedal 10.

(effect)
Next, the effect of the accelerator apparatus 1 of one Embodiment is demonstrated.
(A) The hysteresis mechanism 40 generates a hysteresis characteristic as shown in FIG. 8B according to the rotation angle of the accelerator pedal 10. At this time, when a desired hysteresis characteristic is generated, the tightening torque applied to the screw portion 552 formed on the end portion 551 of the lever 55 is changed. For example, when the tightening torque is reduced from pattern 1 to pattern 2, the initial lever angle increases as shown in FIGS. 5 and 6. As a result, the pedal effort required at the initial depression of the accelerator pedal 10 is greater than that of the pattern 1. Further, the pedal effort required when the accelerator pedal 10 is fully opened is larger than that of the pattern 1. Therefore, as shown in FIG. 8B, the pedal force required for the operation of the accelerator pedal 10 is larger in the pattern 2 than in the pattern 1 over the entire rotation angle θ of the accelerator pedal 10. In this way, by adjusting the tightening torque applied to the screw portion 552, the hysteresis characteristic of the accelerator device 1 can be adjusted.

  (B) Conventionally, the hysteresis mechanism of an accelerator device is composed of a plurality of parts. The hysteresis characteristics of the accelerator device are determined by assembling these components. However, individual differences occur in the hysteresis characteristics of an accelerator device assembled from a large number of parts due to design tolerances of the individual parts. In the accelerator device 1 of the first embodiment, after assembling, when the hysteresis characteristic is not within a predetermined range by inspection, the tightening torque applied to the screw portion 552 is changed. Thereby, the accelerator apparatus 1 can change a hysteresis characteristic after assembling. Therefore, the accelerator apparatus 1 can have a predetermined hysteresis characteristic even when the tolerance of parts is large. That is, the design tolerance of the parts constituting the hysteresis mechanism 40 can be increased as compared with the conventional case.

  (C) Moreover, the accelerator apparatus which was incompatible in the inspection of the hysteresis characteristics has been increased in number of processes by reassembling so far. However, in the accelerator device 1 of the first embodiment, the hysteresis characteristic can be changed by changing the tightening torque applied to the screw portion 552 in the final stage of the manufacturing process. Thereby, the reassembly process becomes unnecessary, and the manufacturing cost can be reduced.

(Other embodiments)
(A) In the above-described embodiment, the accelerator pedal rod is provided on the left side of the support portion. However, the position where the accelerator pedal rod is provided is not limited to this. It may be on the right side of the support part.

  As mentioned above, this invention is not limited to such embodiment, It can implement with a various form in the range which does not deviate from the summary.

1 ... Accelerator device,
15 ... Accelerator pedal rod (pedal part),
20 ... support part (support member),
31 ・ ・ ・ Return rotation axis (first rotation axis),
32 ・ ・ ・ Return spring (first return spring),
40: Hysteresis mechanism,
41 ... hysteresis rotation axis (second rotation axis),
411 ・ ・ ・ End (screw hole)
411a ... screw holes,
43 ... Hysteresis spring (second return spring),
50 ... Link mechanism part,
55 ・ ・ ・ Lever,
552... Threaded portion (screw shaft),
57... Rotation angle detection sensor (rotation angle detection means)
100: Body wall surface (vehicle body).

Claims (3)

A support member attachable to the vehicle body;
A pedal portion rotatably supported at one end by the support member;
A first rotation shaft that is pivotally attached to the support member and interlocks with the rotation of the pedal portion;
When the rotational force due to the driver's stepping is transmitted, the rotation of the first rotation shaft is allowed in the accelerator opening direction, and when the rotation force is released, the rotation of the first rotation shaft is returned to the accelerator closing direction. A first return spring on which a first biasing force acts;
Rotation angle detection means for detecting a relative rotation angle of the first rotation shaft with respect to the support member;
A second rotating shaft provided in parallel to the first rotating shaft so as to be rotatable on the support member;
When the rotational force due to the driver's stepping on is transmitted, the second rotation shaft is allowed to rotate in the accelerator opening direction, and when the rotational force is released, the rotation of the second rotation shaft is returned to the accelerator closing direction. A second return spring on which a second urging force acts;
When the rotational force acting on the second rotational shaft increases, the rotational force acting on the second rotational shaft is released while the accelerator opening corresponding to the rotational angle immediately before the first rotational shaft is maintained. A hysteresis mechanism that generates a hysteresis characteristic that acts to maintain the accelerator opening corresponding to the rotation angle immediately before the first rotation axis when
A link mechanism that interlocks so that the rotation angle of the first rotation shaft and the rotation angle of the second rotation shaft are determined in a one-to-one correspondence;
A lever attached to one end of the second rotating shaft;
An attachment angle changing means capable of changing an attachment angle of the lever with respect to the second rotation shaft;
With
An accelerator device, wherein the hysteresis characteristic is changed by the attachment angle changing means.   The accelerator device according to claim 1, wherein the attachment angle changing means is a screw hole portion of the second rotating shaft and a screw shaft of the lever coupled to the screw hole of the screw hole portion.   The accelerator apparatus according to claim 2, wherein the attachment angle changing means changes a tightening torque applied to the screw shaft when changing the attachment angle of the lever with respect to the second rotation shaft.

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