Operation input device

Abstract

This provides an operation input device that easily achieves both improved operability and enhanced reliability of the return movement of the input component. [Solution] The reaction force generation mechanism, which generates a reaction force to a rotational operating force applied to an input member, comprises a linear motion conversion mechanism that mutually converts the linear motion of a piston housed in a cylindrical member with the rotational motion of the input member, and a first elastic member and a second elastic member that have different biasing forces and bias the piston toward the first axial side. The linear motion conversion mechanism is configured such that, with respect to the rotation angle of the input member, the amount of movement of the piston is the linear motion conversion ratio, and when the piston moves toward the second axial side with respect to the cylindrical member, the second variable rate, which is the rate of change of the linear motion conversion ratio in the second stroke region RS2 where the second elastic member mainly deforms, is higher than the first variable rate, which is the rate of change of the linear motion conversion ratio in the first stroke region RS1 where the first elastic member mainly deforms.

Description

Technical Field

[0001] The present invention relates to an operation input device including an input member to which a rotational operation force is input, and a reaction force generation mechanism that generates a reaction force against the rotational operation force input to the input member.

Background Art

[0002] An example of such an operation input device is disclosed in Japanese Laid-Open Patent Publication No. 2008-143334. Hereinafter, in the description of the background art, reference numerals in the document are cited in parentheses.

[0003] In this operation input device, the input member (14) is connected so as to rotate integrally with an operation tool (80) operated by a driver of a vehicle. The reaction force generation mechanism includes a tubular member (18A) disposed on a reference axis (12), a piston (16) accommodated in the tubular member (18A), and a linear motion conversion mechanism that mutually converts rotational motion of the input member (14) and linear motion of the piston (16) along the reference axis (12).

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of Invention

Problems to be Solved by the Invention

[0005] In the above operation input device, the piston (16) is biased by an elastic member (68) in a direction opposite to the moving direction of the piston (16) when the operation tool (80) is operated by the driver. Further, a gap between the outer peripheral surface of the piston (16) and the inner peripheral surface of the tubular member (18A) is sealed by seal members (64, 66).

[0006] Therefore, in the above reaction force generation mechanism, when the operating tool (80) is operated by the driver, a reaction force is generated against the rotational operating force applied to the input member, based on the biasing force of the elastic member (68) and the frictional force of the sealing members (64, 66).

[0007] However, with the above configuration, if the frictional force of the sealing members (64, 66) is increased to improve the feel of operation, it may become difficult for the input member (14) to return to its initial position when the driver releases the operation of the control device (80). Furthermore, in the above operation input device, if the reaction force characteristics for the target stroke of the control device are realized solely by varying the linear conversion ratio, for example, if the object being operated is a braking device, it is necessary to set the linear conversion ratio at the beginning of the stroke to about 3 to 4 times the normal level in order to provide a braking force that is easily understood by the occupant. However, if the linear conversion ratio at the beginning of the stroke is increased, the frictional force required to hold the control device (80) must also be set to a large level. On the other hand, from the middle to the end of the stroke, it is necessary to lower the linear conversion ratio from the initial level in order to balance the ease of returning the control device (80) with a comfortable feel of operation (e.g., the feel of stepping on it). As a result, hysteresis on the operating surface (on the tread surface) increases compared to the beginning of the stroke, and it may become difficult for the return operation from the middle to the end of the stroke. Furthermore, if the friction force is set low to optimize the return motion from the middle to the later stages of the stroke, the hysteresis on the operating surface in the initial stages of the stroke becomes extremely low, around 1 / 3 to 1 / 4, which could make it difficult to hold the operating tool in the initial stroke region.

[0008] In other words, in the reaction force generation mechanism described above, the biasing force from the elastic member (68) and the frictional force from the sealing members (64, 66) are used as the reaction force to the rotational operating force. However, there is still room for improvement in improving the operating feel when the operator operates the control tool (80). For example, the operating feel of the control tool includes factors such as the responsiveness when the operator operates the tool, the balance between rigidity and responsiveness, the feel during sudden operations, the holdability of the control tool, and the ease with which the control tool returns to its original position. There is still room for improvement in order to adequately satisfy these factors.

[0009] Therefore, there is a need for an input device that can easily achieve both improved operability and increased reliability of the return movement of the input components. [Means for solving the problem]

[0010] The operation input device in view of the above is: An input member to which a rotational operating force is applied, The system includes a reaction force generating mechanism that generates a reaction force to the rotational operating force input to the input member, With the direction along the reference axis as the axial direction, one side of the axial direction is designated as the axial first side, and the other side of the axial direction is designated as the axial second side. The reaction force generation mechanism is, A cylindrical member positioned on the aforementioned reference axis, A piston housed in the cylindrical member, A linear motion conversion mechanism that mutually converts the rotational motion of the input member and the linear motion of the piston along the axial direction, A first elastic member that biases the piston toward the first axial direction, The piston is biased toward the first axial direction, and a second elastic member having a different biasing force from the first elastic member is provided, When the piston moves along the axial direction toward the second axial direction relative to the cylindrical member, the region in which the first elastic member mainly deforms is defined as the first stroke region, and the region in which the second elastic member mainly deforms is defined as the second stroke region. The amount of movement of the piston with respect to the rotation angle of the input member is defined as the linear motion conversion ratio of the linear motion conversion mechanism. The first variable ratio is defined as the difference between the linear motion conversion ratio at the first starting period, which is the start of the first stroke range, and the linear motion conversion ratio at the first ending period, which is the end of the first stroke range, divided by the linear motion conversion ratio at the first starting period. The second variable ratio is obtained by dividing the difference between the linear motion conversion ratio at the second starting period, which is the start of the second stroke range, and the linear motion conversion ratio at the second ending period, which is the end of the second stroke range, by the linear motion conversion ratio at the second starting period. The linear motion conversion mechanism is configured such that the second variable ratio is higher than the first variable ratio.

[0011] With this configuration, the first variable ratio, which represents the degree of change in the linear motion conversion ratio in the first stroke range, and the second variable ratio, which represents the degree of change in the linear motion conversion ratio in the second stroke range, are different. This allows for a difference in the reaction force perceived by the operator throughout the entire stroke range. When the operator applies rotational force to the input member, the difference in the perceived reaction force makes it easier for the operator to feel the operation, such as the stiffness corresponding to the stroke amount and the responsiveness. Specifically, in the first stroke range, the variable ratio of the linear motion conversion ratio is low, so the change in reaction force with respect to the stroke is small, and the operation on the input member becomes faster, allowing the operator to feel the effect coming on sooner. Also, in the second stroke range, the change in reaction force with respect to the stroke is large, so the operator can control the effect while feeling the change in stiffness when applying rotational force to the input member. Since the piston is biased toward the first axial direction by the first elastic member and the second elastic member, the return movement of the input member to its initial position can also be performed appropriately. Therefore, this configuration makes it easier to realize an input device that achieves both further improvements in operability and improved reliability of the return movement of the input component.

[0012] Furthermore, the operation input device in view of the above is: An input member to which a rotational operating force is applied, The system includes a reaction force generating mechanism that generates a reaction force to the rotational operating force input to the input member, With the direction along the reference axis as the axial direction, one side of the axial direction is designated as the axial first side, and the other side of the axial direction is designated as the axial second side. The reaction force generation mechanism is, A cylindrical member positioned on the aforementioned reference axis, A piston housed in the cylindrical member, A linear motion conversion mechanism that mutually converts the rotational motion of the input member and the linear motion of the piston along the axial direction, A first elastic member that biases the piston toward the first axial direction, The piston is biased toward the first axial direction, and a second elastic member having a different biasing force from the first elastic member is provided, The direction perpendicular to the aforementioned reference axis is defined as the radial direction, the direction toward the aforementioned reference axis along the radial direction is defined as the radially inward direction, and the direction away from the aforementioned reference axis along the radial direction is defined as the radially outward direction. The reaction force generation mechanism is, A friction member is positioned at the sliding point between the outer circumferential surface of the piston and the inner circumferential surface of the cylindrical member, The system includes a tensioning mechanism that presses the friction member from the radially inner side toward the radially outer side to apply tension to the inner circumferential surface of the cylindrical member, or presses the friction member from the radially outer side toward the radially inner side to apply tension to the outer circumferential surface of the piston, The friction member is A sliding member is disposed on the sliding surface between the cylindrical member and the piston, The substrate comprises the sliding member to which the sliding member is bonded on the radially outer or radially inner side, The tension-applying mechanism presses the base material, on which the sliding member is positioned radially outward, from the radially inward side toward the radially outward side, or presses the base material, on which the sliding member is positioned radially inward, from the radially outward side toward the radially inward side.

[0013] According to this configuration, the pressing force applying mechanism applies a pressing force to the inner peripheral surface of the tubular member or the outer peripheral surface of the piston, thereby increasing the frictional force of the friction member and easily applying an appropriate reaction force against the input of the rotational operation force to the input member by the operator. In addition, since the biasing force of the first elastic member and the biasing force of the second elastic member are different, a difference can be imparted to the reaction force perceived by the operator over the entire stroke range in the rotational stroke of the input member and the linear stroke of the piston. When the operator applies a rotational operation force to the input member, the reaction force perceived by the operator differs, so that the operator can easily experience operational feelings such as a sense of rigidity and responsiveness according to the stroke amount, for example. Since the piston is biased toward the first axial side by the first elastic member and the second elastic member, the return operation of the input member to the initial position can also be appropriately performed. Therefore, according to the present configuration, it is easy to realize an operation input device that facilitates the achievement of both further improvement in operational feel and improvement in the reliability of the return operation of the input member.

[0014] Further, an operation input device in view of the above is configured as follows: An input member to which a rotational operation force is input, A reaction force generation mechanism that generates a reaction force against the rotational operation force input to the input member, A direction along the reference axis is defined as an axial direction, one side of the axial direction is defined as a first axial side, and the other side of the axial direction is defined as a second axial side, The reaction force generation mechanism includes: A tubular member disposed on the reference axis, A piston housed in the tubular member, A linear motion conversion mechanism that mutually converts rotational motion of the input member and linear motion of the piston along the axial direction, An elastic member that biases the piston toward the first axial side, A friction member disposed at a sliding portion between the outer peripheral surface of the piston and the inner peripheral surface of the tubular member, The friction member is configured such that the frictional force is larger when the piston moves to the second axial side than when the piston moves to the first axial side.

[0015] With this configuration, when a rotational operating force is applied to the input member so that the piston moves to the second axial direction, the biasing force of the elastic member toward the first axial direction and the relatively large frictional force of the friction member can generate a relatively large reaction force to the rotational operating force applied to the input member. On the other hand, when the rotational operating force applied to the input member is released, the biasing force of the elastic member toward the first axial direction and the relatively small frictional force of the friction member can move the piston relatively easily toward the first axial direction. This ensures a large reaction force from the reaction force generation mechanism when moving the piston toward the second axial direction, while appropriately returning the input member to its initial position when moving the piston toward the first axial direction is performed by the biasing force of the elastic member. Therefore, it is easy to achieve both improved operability of the operating input device and improved reliability of the return movement of the input member. [Brief explanation of the drawing]

[0016] [Figure 1] Side view of the operation input device according to the first embodiment [Figure 2] Cross-sectional view along the axial direction of the operation input device according to the first embodiment [Figure 3] A cross-sectional view along the radial direction of the operation input device according to the first embodiment. [Figure 4] This figure shows the configuration of the piston in the operation input device according to the first embodiment. [Figure 5] Cross-sectional view along the axial direction of the operation input device according to the second embodiment. [Figure 6] A cross-sectional view along the axial direction of the operation input device according to the third embodiment. [Figure 7] This figure shows the configuration of the linear motion conversion mechanism of the operation input device according to the third embodiment. [Figure 8] A graph showing the relationship between the operating force (pedaling force) applied to input member 1 and the amount of movement of the input member (pedal stroke). [Figure 9] Side view of the operation input device according to the fourth to seventh embodiment. [Figure 10] A cross-sectional view along the axial direction of the operation input device according to the fourth embodiment. [Figure 11] A cross-sectional view along the axial direction of the operation input device according to the fifth embodiment. [Figure 12] A cross-sectional view along the axial direction of the operation input device according to the sixth embodiment. [Figure 13] Cross-sectional view along the axial direction of the operation input device according to the seventh embodiment. [Figure 14] Side view of the operation input device according to the eighth embodiment. [Figure 15] A graph showing the rotational-to-linear conversion ratio of the operation input device according to the eighth embodiment. [Figure 16] A cross-sectional view along the axial direction of the operation input device according to the ninth embodiment. [Figure 17] A cross-sectional view along the radial direction of the operation input device according to the ninth embodiment. [Figure 18] This figure shows the configuration of the cam mechanism and guide mechanism of the operation input device according to the ninth embodiment. [Figure 19] A graph showing the rotational-to-linear conversion ratio of the operation input device according to the ninth embodiment. [Modes for carrying out the invention]

[0017] 1. First Embodiment First, the operation input device 100 according to the first embodiment will be described with reference to Figures 1 to 4. As shown in Figure 1, in this embodiment, the operation input device 100 is fixed to the vehicle body B.

[0018] As shown in Figure 2, the operation input device 100 comprises an input member 1 and a reaction force generation mechanism 2.

[0019] The input member 1 is a member to which a rotational operating force is input. The input member 1 is connected to an operating device (pedal 19: omitted in Figure 1, see Figure 9) operated by the driver of the vehicle. In this embodiment, the input member 1 is an arm member that swings about a pivot axis Y (which coincides with the reference axis X described later in the first embodiment). In this embodiment, the operating device connected to the input member 1 is either an accelerator pedal or a brake pedal. The input member 1 may be connected so as to swing integrally with the operating device. Alternatively, the input member 1 may be connected to the operating device via a gear mechanism, linkage mechanism, etc. In such a configuration, the pivot axis Y of the input member 1 may be located on a different axis from the reference axis X.

[0020] As will be described later, in the rotation-to-linear motion conversion mechanism (linear motion conversion mechanism 5) provided in the reaction force generation mechanism 2, which mutually converts rotational motion and linear motion, the direction of movement of the linear motion is along the "reference axis X". In the first embodiment, the "reference axis X" is also the rotation axis of the rotational motion. In the following description, the direction along the reference axis X will be referred to as the "axial direction L". One side of the axial direction L will be referred to as the "first axial direction L1", and the other side of the axial direction L will be referred to as the "second axial direction L2". Furthermore, the direction perpendicular to a certain axis (for example, the reference axis X) will be referred to as the "radial direction R" with respect to that axis, and the direction that circles around a certain axis (for example, the reference axis X) will be referred to as the "circumferential direction C" with respect to that axis. Furthermore, the direction toward the axis (for example, the reference axis X) along the radial direction R will be referred to as the radially inward direction R1, and the direction away from the axis (for example, the reference axis X) along the radial direction R will be referred to as the radially outward direction R2.

[0021] The reaction force generation mechanism 2 is configured to generate a reaction force in response to the rotational operating force input to the input member 1. The reaction force generated by the reaction force generation mechanism 2 allows the driver to perceive the amount of pedal 19 being operated. In this embodiment, when the driver depresses the pedal 19, which is the accelerator pedal or brake pedal, the reaction force generation mechanism 2 generates a reaction force that returns the pedal 19 to its initial position.

[0022] The reaction force generation mechanism 2 comprises a cylindrical member 3, a piston 4, a linear motion conversion mechanism 5, an elastic member 6, and a friction member 7. In this embodiment, the reaction force generation mechanism 2 further comprises a holding member 8.

[0023] The cylindrical member 3 is formed in a cylindrical shape. The cylindrical member 3 is positioned on the reference axis X. In other words, the cylindrical member 3 is formed in a cylindrical shape centered on the reference axis X. In this embodiment, the cylindrical member 3 is a housing that accommodates the piston 4, the linear motion conversion mechanism 5, the elastic member 6, and the friction member 7. The cylindrical member 3 comprises a peripheral wall portion 31 and a bottom wall portion 32.

[0024] The peripheral wall portion 31 is open on the first axial side L1 and the second axial side L2, and is formed in a cylindrical shape centered on the reference axis X.

[0025] The bottom wall portion 32 is positioned to close the opening L2 on the second axial side of the peripheral wall portion 31. In this embodiment, the bottom wall portion 32 is formed integrally with the peripheral wall portion 31.

[0026] The piston 4 is housed in the cylindrical member 3. The piston 4 is configured to be movable along the axial direction L. In this embodiment, the piston 4 includes a sliding portion 41, a shaft portion 42, and a flange portion 43.

[0027] The sliding portion 41 is configured to slide along the inner circumferential surface of the peripheral wall portion 31 in the axial direction L. In this embodiment, the sliding portion 41 is formed in the shape of a disc centered on the reference axis X.

[0028] The shaft portion 42 is formed to extend along the axial direction L. The shaft portion 42 is positioned on the reference axis X. In this embodiment, the shaft portion 42 is formed to extend from the flange portion 43 toward the second axial side L2.

[0029] The flange portion 43 is formed to extend radially outward R2 from the shaft portion 42. In this embodiment, the flange portion 43 is joined to the sliding portion 41 from the axial second side L2.

[0030] The linear motion conversion mechanism 5 is configured to convert between the rotational motion of the input member 1 and the linear motion of the piston 4 along the axial direction L. In this embodiment, the linear motion conversion mechanism 5 includes a transmission member 51, a cam mechanism 52, and a guide mechanism 53.

[0031] The transmission member 51 is a shaft member to which the rotation of the input member 1 is transmitted. The transmission member 51 is positioned on the reference axis X. The transmission member 51 is rotatably supported on the cylindrical member 3 around the reference axis X. In this embodiment, the transmission member 51 includes a first connecting portion 511, a second connecting portion 512, and a third connecting portion 513.

[0032] The first connecting portion 511 is connected to the input member 1 so as to rotate integrally with it. The second connecting portion 512 is positioned spaced apart from the first connecting portion 511 in the axial direction second L2. The second connecting portion 512 is connected to the cam mechanism 52. The third connecting portion 513 is formed to connect the first connecting portion 511 and the second connecting portion 512 in the axial direction L. The third connecting portion 513 is formed in a cylindrical shape centered on the reference axis X.

[0033] The cam mechanism 52 is configured to convert between the rotational motion of the transmission member 51 and the linear motion of the piston 4 along the axial direction L.

[0034] The guide mechanism 53 is configured to restrict the relative rotation of the piston 4 in the circumferential direction C with respect to the cylindrical member 3, and to allow the relative movement of the piston 4 in the axial direction L with respect to the cylindrical member 3.

[0035] The elastic member 6 is a member that biases the piston 4 toward the first axial direction L1. In this embodiment, the elastic member 6 includes an inner spring 61 (first elastic member) and an outer spring 62 (second elastic member). In this embodiment, each of the inner spring 61 and the outer spring 62 is a compression coil spring.

[0036] The retaining member 8 is a member for holding the elastic member 6. In this embodiment, the retaining member 8 comprises a cylindrical portion 81, an inner retaining portion 82, and an outer retaining portion 83.

[0037] The cylindrical portion 81 is formed as a bottomed cylindrical shape centered on the reference axis X, with the first axial side L1 being open and the second axial side L2 being closed. The cylindrical portion 81 is positioned to cover the shaft portion 42 of the piston 4 from the radially outer side R2.

[0038] The inner retaining portion 82 is formed in a disc shape centered on the reference axis X. The inner retaining portion 82 closes the axial second side L2 of the cylindrical portion 81.

[0039] The outer retaining portion 83 is formed in the shape of an annular plate centered on the reference axis X. The outer retaining portion 83 is formed to protrude radially outward R2 from the end of the axial first side L1 of the cylindrical portion 81.

[0040] The inner spring 61 is positioned between the flange portion 43 of the piston 4 and the inner retaining portion 82 of the retaining member 8, with the shaft portion 42 of the piston 4 inserted through it. The outer spring 62 is positioned between the outer retaining portion 83 of the retaining member 8 and the bottom wall portion 32 of the cylindrical member 3, with the cylindrical portion 81 of the retaining member 8 inserted through it.

[0041] The friction member 7 is positioned at the sliding point between the outer circumferential surface of the piston 4 and the inner circumferential surface of the cylindrical member 3. In this embodiment, the friction member 7 is positioned between the outer circumferential surface of the sliding portion 41 of the piston 4 and the inner circumferential surface of the peripheral wall portion 31 of the cylindrical member 3.

[0042] In this embodiment, the friction member 7 is attached to the outer circumferential surface of the piston 4. The friction member 7 is positioned in a state of being pressed against the inner circumferential surface of the cylindrical member 3. In this embodiment, the friction member 7 is an annular elastic body. The friction member 7 is positioned on the reference axis while attached to the outer circumferential surface of the piston 4. In this example, the friction member 7 is made of synthetic resin.

[0043] In this embodiment, the outer circumferential surface of the piston 4 includes an outer inclined surface 4a, an outer restricting surface 4b, and an outer parallel surface 4c.

[0044] The outer circumferential inclined surface 4a is inclined so that it moves radially outward R2 as it moves toward the first axial side L1. In this embodiment, the outer circumferential inclined surface 4a is formed from the end of the sliding portion 41 on the first axial side L1.

[0045] The outer peripheral restricting surface 4b is formed to restrict the movement of the friction member 7 toward the second axial direction L2. The outer peripheral restricting surface 4b is formed to extend along the radial direction R. The outer peripheral restricting surface 4b is spaced apart from the outer peripheral inclined surface 4a toward the second axial direction L2.

[0046] The outer circumferential parallel surface 4c is formed to be parallel to the axial direction L. The outer circumferential parallel surface 4c is positioned between the outer circumferential inclined surface 4a and the outer circumferential restricting surface 4b in terms of axial direction L.

[0047] In this embodiment, the inner circumferential surface of the friction member 7 includes an inner circumferential inclined surface 7a and an inner circumferential parallel surface 7b.

[0048] The inner circumferential inclined surface 7a is formed along the outer circumferential inclined surface 4a. In other words, the inner circumferential inclined surface 7a is inclined radially outward R2 as it moves toward the first axial side L1. The inner circumferential inclined surface 7a is positioned to be in contact with the outer circumferential inclined surface 4a.

[0049] The inner circumferential parallel surface 7b is formed to be parallel to the axial direction L. In this embodiment, the inner circumferential parallel surface 7b is formed to be continuous with the inner circumferential inclined surface 7a from the end of the second axial side L2 of the friction member 7.

[0050] In this embodiment, when the piston 4 moves toward the first axial direction L1, the friction member 7 moves toward the first axial direction L1 together with the piston 4 because its movement toward the second axial direction L2 is restricted by the outer peripheral restricting surface 4b.

[0051] On the other hand, when the piston 4 moves in the second axial direction L2, the friction member 7 moves relative to the piston 4 in the first axial direction L1 such that its inner circumferential inclined surface 7a slides on its outer circumferential inclined surface 4a. At this time, the radial width R between the outer circumferential inclined surface 4a of the piston 4 and the inner circumferential surface of the cylindrical member 3 gradually narrows as it moves toward the first axial direction L1. Therefore, as the piston 4 moves in the second axial direction L2 and the friction member 7 moves relative to the piston 4 in the first axial direction L1, the frictional force acting on the friction member 7 increases.

[0052] Thus, the friction member 7 is configured such that the frictional force is greater when the piston 4 moves in the second axial direction L2 compared to when the piston 4 moves in the first axial direction L1.

[0053] In this embodiment, a viscoelastic body 71 is placed on the sliding surface of the friction member 7. The viscoelastic body 71 is a viscoelastic material. In this embodiment, the viscoelastic body 71 is attached to the outer circumferential surface of the friction member 7. Furthermore, in this embodiment, the viscoelastic body 71 is a so-called semi-dry friction material impregnated with oil. In this example, the viscoelastic body 71 is a fibrous material impregnated with high-viscosity grease.

[0054] As shown in Figure 2, in this embodiment, the operation input device 100 further includes a first manipulated amount sensor 91 and a second manipulated amount sensor 92.

[0055] The first manipulated amount sensor 91 is a sensor for detecting the amount of manipulation of the input member 1. The first manipulated amount sensor 91 is configured to detect at least one of the amount of rotation and twist of the third connecting portion 513 of the transmission member 51. The first manipulated amount sensor 91 is, for example, a rotation sensor for detecting the amount of rotation of the third connecting portion 513, or a torque sensor for detecting the twist of the third connecting portion 513. The first manipulated amount sensor 91 is housed radially inward R1 relative to the cylindrical member 3. In this embodiment, the first manipulated amount sensor 91 is positioned radially inward R1 relative to the peripheral wall portion 31 of the cylindrical member 3.

[0056] The second manipulated amount sensor 92 is a sensor for detecting the amount of manipulation of the input member 1. In this embodiment, the second manipulated amount sensor 92 is positioned adjacent to the first axial side L1 with respect to the first connecting portion 511 of the transmission member 51. The second manipulated amount sensor 92 is a rotation sensor that detects the amount of rotation of the first connecting portion 511. In this embodiment, the second manipulated amount sensor 92 is fixed to the cover portion 33. The cover portion 33 is formed to cover a part of the circumferential direction C of the input member 1 from the radially outer side R2, and to cover a part of the radial direction R of the input member 1 from the axial first side L1. The cover portion 33 is joined to the circumferential wall portion 31 of the cylindrical member 3 from the axial first side L1.

[0057] As shown in Figures 2 and 3, in this embodiment, the cam mechanism 52 includes a cam path 54 and a cam driven member 55. The cam path 54 extends along a direction inclined with respect to both the axial direction L and the circumferential direction C. The cam driven member 55 is configured to move along the cam path 54. One of the cam path 54 and the cam driven member 55 is provided on the transmission member 51. The other of the cam path 54 and the cam driven member 55 is provided on the piston 4. In this embodiment, the cam path 54 is provided on the piston 4 and the cam driven member 55 is provided on the transmission member 51.

[0058] As shown in Figure 4, in this embodiment, the piston 4 is provided with a pair of path-forming portions 44. The pair of path-forming portions 44 are formed to protrude from the sliding portion 41 toward the first axial side L1. In this embodiment, the pair of path-forming portions 44 are arranged to be point-symmetric with respect to the reference axis X in an axial view along the axial direction L. In the illustrated example, each of the pair of path-forming portions 44 is formed in the shape of an arc with a central angle less than 45 degrees around the reference axis X in an axial view along the axial direction L.

[0059] In the following explanation, one side of the circumferential direction C will be referred to as "Circumferential direction first side C1," and the other side of the circumferential direction C will be referred to as "Circumferential direction second side C2."

[0060] In this embodiment, the cam path 54 is a cam surface 541 formed on each of the pair of path forming sections 44. In other words, in this embodiment, multiple (in this case, two) cam paths 54 are arranged at equal intervals in the circumferential direction C. In the example shown in Figure 4, each of the pair of cam surfaces 541 is formed in an arc shape centered on the reference axis X when viewed in the axial direction along the axial direction L. Furthermore, each of the pair of cam surfaces 541 is inclined so that it gradually moves toward the first axial direction L1 as it moves toward the first circumferential side C1.

[0061] As shown in Figures 2 and 3, in this embodiment, the cam driven member 55 is a cam roller 551. In this embodiment, the cam roller 551 rolls on each of the pair of cam surfaces 541. In other words, in this embodiment, one cam driven member 55 is provided for each cam path 54 such that a pair of cam rollers 551 correspond to a pair of cam surfaces 541. Thus, in this embodiment, the cam mechanism 52 is provided with multiple (in this case, two) sets of cam paths 54 and cam driven members 55.

[0062] In this embodiment, a connecting shaft 552, formed to extend along the radial direction R, is fixed to the second connecting portion 512 of the transmission member 51, with the shaft penetrating the second connecting portion 512 in the radial direction R. Cam rollers 551 are rotatably supported on each of the portions of the connecting shaft 552 that protrude from the second connecting portion 512 in the radial direction R. Therefore, in this embodiment, each of the pair of cam rollers 551 is configured to rotate around the axis of the connecting shaft 552 and to rotate (revolve) around the reference axis X in conjunction with the rotation of the connecting shaft 552.

[0063] In this embodiment, each of the pair of cam rollers 551 is positioned to contact the cam surface 541 from the circumferential second side C2. Furthermore, each of the pair of cam rollers 551 is positioned at the axial second side L2 on the cam surface 541 when no rotational operating force is applied to the input member 1.

[0064] Furthermore, in this embodiment, each of the pair of cam rollers 551 has an outer peripheral surface whose outer edge, when viewed axially along the axial direction L, is formed in an arc shape, and is a so-called spherical outer ring type cam follower (see Figure 3). With this configuration, the cam rollers 551 can rotate in the circumferential direction C while rolling appropriately on the cam surface 541.

[0065] In this embodiment, the guide mechanism 53 includes a guide path 56 and a guide driven member 57.

[0066] The guide path 56 extends along the axial direction L. The guide driven member 57 is configured to move along the guide path 56. One of the guide path 56 and the guide driven member 57 is provided on the piston 4. The other of the guide path 56 and the guide driven member 57 is provided on the cylindrical member 3. In this embodiment, the guide path 56 is provided on the piston 4 and the guide driven member 57 is provided on the cylindrical member 3.

[0067] In this embodiment, the axial L arrangement regions of the cam path 54 and the guide path 56 overlap with each other. Also, the axial L arrangement regions of the cam driven member 55 and the guide driven member 57 overlap with each other.

[0068] As shown in Figure 4, in this embodiment, the guide path 56 is a guide surface 561 formed on each of the pair of path forming sections 44. In other words, in this embodiment, multiple (in this case, two) guide paths 56 are arranged at equal intervals in the circumferential direction C. In the example shown in Figure 4, each of the pair of guide surfaces 561 is formed to face the first circumferential side C1. Furthermore, each of the pair of guide surfaces 561 is formed in a straight line along the axial direction L when viewed radially along the radial direction R.

[0069] As shown in Figures 2 and 3, in this embodiment, the guide-driven member 57 is a guide roller 571 that rolls on each of the pair of guide surfaces 561. In other words, in this embodiment, one guide-driven member 57 is provided for one guide path 56 such that a pair of guide rollers 571 correspond to a pair of guide surfaces 561. Thus, in this embodiment, the guide mechanism 53 is provided with multiple (in this case, two) sets of guide paths 56 and guide-driven members 57.

[0070] As shown in Figure 3, in this embodiment, each of the pair of guide rollers 571 is positioned to contact the guide surface 561 from the circumferential first side C1. And, as shown in Figure 2, each of the pair of guide rollers 571 is positioned at the second axial side L2 on the guide surface 561 when no rotational operating force is applied to the input member 1.

[0071] Furthermore, as shown in Figure 3, in this embodiment, each of the pair of guide rollers 571 is rotatably supported on a support shaft 572 formed to extend along the radial direction R. The pair of support shafts 572 are arranged on both sides of the radial direction R with respect to the reference axis X. The pair of support shafts 572 are fixed to the peripheral wall portion 31 of the cylindrical member 3.

[0072] In this embodiment, when a rotational operating force is input to the input member 1 and the transmission member 51 rotates, a pair of cam rollers 551 rotate (revolve) in the first circumferential direction C1 around the reference axis X via the connecting shaft 552 connected to the second connecting portion 512 of the transmission member 51. Accordingly, each of the pair of cam rollers 551 rolls on the cam surface 541 while in contact with it from the second circumferential direction C2. At this time, each of the pair of guide rollers 571 rolls on the guide surface 561 while in contact with it from the first circumferential direction C1. As a result, with the rotation of the piston 4 in the circumferential direction C relative to the cylindrical member 3 restricted, the piston 4 moves in the second axial direction L2 relative to the cylindrical member 3 against the reaction force generated by the reaction force generation mechanism 2.

[0073] On the other hand, when rotational force is no longer applied to the input member 1, the reaction force generated by the reaction force generation mechanism 2 pushes the piston 4 toward the first axial direction L1. Consequently, each of the pair of cam rollers 551 rolls along the cam surface 541 while in contact with it from the second circumferential direction C2. At this time, each of the pair of guide rollers 571 rolls along the guide surface 561 while in contact with it from the first circumferential direction C1. Therefore, with the rotation of the piston 4 relative to the cylindrical member 3 restricted in the circumferential direction C, the pair of cam rollers 551 rotate (revolve) around the reference axis X in the second circumferential direction C2, and the input member 1 rotates via the transmission member 51 to return to its initial position.

[0074] 2. Second Embodiment In the following description, the operation input device 100 according to the second embodiment will be explained with reference to Figure 5. In this embodiment, the configuration of the friction member 7 differs from that of the first embodiment. In the following description, the differences from the first embodiment will be the main focus. Unless otherwise specified, the same applies as in the first embodiment.

[0075] As shown in Figure 5, in this embodiment, an elastic body 72 is arranged on the inner circumferential surface of the friction member 7. The elastic body 72 is formed in an annular shape. The elastic body 72 is arranged to seal the space between the inner circumferential surface of the friction member 7 and the outer circumferential surface of the sliding portion 41 of the piston 4. In the illustrated example, the friction member 7 has a groove formed such that the inner circumferential parallel surface 7b is recessed radially outward R2 over the entire circumference in the circumferential direction C. The elastic body 72 is then arranged in the groove so as to contact the outer circumferential parallel surface 4c of the piston 4. In this example, the elastic body 72 is an O-ring.

[0076] With this configuration, the frictional force when the friction member 7 moves relative to the piston 4 in the first axial direction L1 is greater than in the first embodiment described above.

[0077] 3. Third Embodiment In the following description, the operation input device 100 according to the third embodiment will be explained with reference to Figures 6 and 7. In this embodiment, the configuration of the reaction force generation mechanism 2 differs from that of the first embodiment. In the following description, the differences from the first embodiment will be the main focus. Points that are not specifically explained will be the same as those in the first embodiment.

[0078] As shown in Figure 6, in this embodiment, the piston 4 comprises a tip portion 45, a holding portion 46, a small diameter portion 47, a large diameter portion 48, and a connecting portion 49.

[0079] The tip portion 45 is formed to extend from the holding portion 46 toward the second axial direction L2. The tip portion 45 is formed to have a smaller diameter than the holding portion 46. The holding portion 46 is formed in a cylindrical shape centered on the reference axis X. The holding portion 46 is formed integrally with the tip portion 45. In this embodiment, the inner spring 61 is positioned between the holding portion 46 and the inner holding portion 82 in the axial direction L with the tip portion 45 inserted through it.

[0080] In this embodiment, the sliding portion 41 is formed to protrude radially outward R2 from the axial first side L1 end of the holding portion 46.

[0081] In this embodiment, the friction member 7 is made of synthetic rubber. In this embodiment, the viscoelastic body 71 is not placed on the sliding surface of the friction member 7. Therefore, in this embodiment, the outer circumferential surface of the friction member 7 and the inner circumferential surface of the peripheral wall portion 31 are in direct contact.

[0082] The small-diameter portion 47 is positioned radially inward R1 relative to the holding portion 46. The small-diameter portion 47 abuts against the tip portion 45 from the axial first side L1, thereby restricting its movement in the axial second side L2.

[0083] The large-diameter portion 48 is formed to be larger in diameter than the small-diameter portion 47. The large-diameter portion 48 is positioned on the first axial side L1 relative to the small-diameter portion 47. The large-diameter portion 48 is formed integrally with the small-diameter portion 47.

[0084] The connecting portion 49 is formed to protrude from the large-diameter portion 48 in the axial direction toward the first side L1. The connecting portion 49 is formed to have a smaller diameter than the large-diameter portion 48. The connecting portion 49 is formed integrally with the large-diameter portion 48.

[0085] In this embodiment, the transmission member 51 is formed in a cylindrical shape centered on the reference axis X. The transmission member 51 is positioned radially outward R2 relative to the peripheral wall portion 31 of the cylindrical member 3. Furthermore, the transmission member 51 is rotatably supported by the peripheral wall portion 31.

[0086] In this embodiment, the cam path 54 is a cam groove 542 formed in the transmission member 51. The cam groove 542 is formed to extend along a direction that is inclined with respect to both the axial direction L and the circumferential direction C (see Figure 7). In this embodiment, the cam roller 551 rolls on the inner surface of the cam groove 542. In this embodiment, multiple cam grooves 542 are arranged distributed in the circumferential direction C.

[0087] In this embodiment, the cylindrical covering member 515 is connected to the transmission member 51 from the radially outer R2 such that it covers all of the cam grooves 542. In this embodiment, the first operating amount sensor 91 and the second operating amount sensor 92 are located radially outward R2 from the covering member 515 and on the axial first side L1 from the input member 1.

[0088] In this embodiment, the guide path 56 is a guide groove 562 formed in the cylindrical member 3. The guide groove 562 is an elongated groove extending along the axial direction L. The guide groove 562 is formed to penetrate the peripheral wall portion 31 of the cylindrical member 3 in the radial direction R. In this embodiment, a plurality of guide grooves 562 are arranged dispersed in the circumferential direction C.

[0089] In this embodiment, the linear motion conversion mechanism 5 includes a connecting member 58. The connecting member 58 is a member that connects the cam driven member 55 and the piston 4. The connecting member 58 includes a coupling portion 581, a support portion 582, and a guided portion 583.

[0090] The coupling portion 581 is connected to the connecting portion 49 of the piston 4. In this embodiment, the coupling portion 581 is formed in a cylindrical shape that covers the connecting portion 49 from the radially outer side R2. On the inner circumference of the coupling portion 581, a plurality of splines extending in the axial direction L are formed and dispersed in the circumferential direction C. On the other hand, on the outer circumference of the connecting portion 49, a plurality of splines that engage with them are formed and dispersed in the circumferential direction C.

[0091] Thus, in this embodiment, the coupling portion 581 is supported relative to the piston 4 so as to be movable in the axial direction L, while its rotation in the circumferential direction C is restricted. As described above, in this embodiment, the connecting portion 49 is formed to be smaller in diameter than the large-diameter portion 48. Therefore, the coupling portion 581, which is supported relative to the connecting portion 49 so as to be movable in the axial direction L, is restricted from moving toward the second axial direction L2 by the large-diameter portion 48.

[0092] The support portion 582 rotatably supports the cam roller 551. The support portion 582 is formed to extend along the radial direction R. In this embodiment, a plurality of support portions 582 are arranged distributed in the circumferential direction C.

[0093] The guided portion 583 extends radially outward R2 from the connecting portion 581 and is connected to the support portion 582. In other words, the same number of guided portions 583 are provided as the number of support portions 582. In this embodiment, multiple guided portions 583 are arranged distributed in the circumferential direction C.

[0094] The guided portion 583 is positioned to penetrate the guide groove 562 in the radial direction R. Therefore, the connecting member 58 is configured to be guided in the axial direction L while its rotation in the circumferential direction C is restricted by the inner surface of the guide groove 562. In other words, in this embodiment, the guided portion 583 functions as a guide-driven member 57.

[0095] Figure 7 shows the transmission member 51, which has a cam groove 542 formed therein, and the peripheral wall portion 31 of the cylindrical member 3, which has a guide groove 562 formed therein, laid out on a plane along the circumferential direction C and arranged so that their positions in the circumferential direction C align.

[0096] As shown in Figure 7, in this embodiment, the multiple cam grooves 542 are arranged at equal intervals in the circumferential direction C. Similarly, the multiple guide grooves 562 are also arranged at equal intervals in the circumferential direction C. In the example shown in Figure 7, there are two of each of the cam grooves 542 as cam paths 54, cam rollers 551 as cam driven members 55, guide grooves 562 as guide paths 56, and guided members 583 as guide driven members 57.

[0097] In this embodiment, when no rotational operating force is applied to the input member 1, each of the multiple cam rollers 551 is at the position furthest axially first L1 in the cam groove 542 (hereinafter referred to as "first position P1"). At this time, each of the multiple guided portions 583 is at the position furthest axially first L1 in the guide groove 562.

[0098] Furthermore, each of the multiple cam rollers 551 can move relative to the second axial position L2 in the cam groove 542 when a rotational operating force is applied to the input member 1 (hereinafter referred to as "second position P2"). Also, each of the multiple guided parts 583 can move relative to the second axial position L2 in the guide groove 562 when a rotational operating force is applied to the input member 1.

[0099] In this embodiment, the pair of surfaces facing both sides in the circumferential direction C of the guide groove 562 and the pair of surfaces facing both sides in the circumferential direction C of the guided portion 583 are formed in a planar shape such that the surfaces facing each other in the circumferential direction C are parallel to each other. In this embodiment, since the dimension of the guided portion 583 in the circumferential direction C is set to be approximately the same as the dimension of the guide groove 562 in the circumferential direction C, the relative movement of the guided portion 583 in the circumferential direction C with respect to the cylindrical member 3 is restricted.

[0100] In this embodiment, each of the multiple cam grooves 542 is formed such that it gradually moves toward the second axial side L2 as it moves toward the second circumferential side C2. Therefore, in this embodiment, the linear motion conversion mechanism 5 converts the rotational motion of the transmission member 51 toward the first circumferential side C1 into the linear motion of the piston 4 toward the second axial side L2. The linear motion conversion mechanism 5 also converts the linear motion of the piston 4 toward the first axial side L1 into the rotational motion of the transmission member 51 toward the second circumferential side C2. In other words, in this embodiment, when a rotational operating force is input to the input member 1 and the transmission member 51 rotates toward the first circumferential side C1, the piston 4 moves toward the second axial side L2 against the reaction force generated by the reaction force generation mechanism 2. On the other hand, when the rotational operating force is no longer input to the input member 1, the reaction force generated by the reaction force generation mechanism 2 causes the piston 4 to move toward the first axial side L1, and the transmission member 51 rotates toward the second circumferential side C2 so that the input member 1 returns to its initial position.

[0101] To elaborate, when a rotational operating force is applied to the input member 1 so that the transmission member 51 rotates in the first circumferential direction C1, the inner surface of the cam groove 542 formed in the transmission member 51 connected to the input member 1 presses the cam roller 551 toward the first circumferential direction C1. As a result, a force toward the first circumferential direction C1 acts on the guided portion 583 connected to the support portion 582 that supports the cam roller 551.

[0102] However, since the surface of the guided portion 583 facing the first circumferential side C1 abuts against the surface of the guide groove 562 facing the second circumferential side C2, the rotation of the connecting member 58 relative to the cylindrical member 3 toward the first circumferential side C1 is restricted. As a result, each of the multiple cam rollers 551 rolls from the first position P1 to the second position P2 of the cam groove 542 as the transmission member 51 rotates toward the first circumferential side C1. Consequently, the piston 4 connected to the cam roller 551 via the connecting member 58 moves toward the second axial side L2 against the reaction force generated by the reaction force generation mechanism 2.

[0103] On the other hand, when no rotational operating force is applied to the input member 1 while each of the cam rollers 551 is in the second position P2 of the cam groove 542, the reaction force generated by the reaction force generation mechanism 2 presses the connecting member 58 toward the first axial side L1 via the piston 4. As a result, with the rotation of the connecting member 58 in the circumferential direction C relative to the cylindrical member 3 restricted by the inner surface of the guide groove 562, the transmission member 51 rotates toward the second circumferential side C2 so that the input member 1 returns to its initial position as each of the multiple cam rollers 551 rolls from the second position P2 to the first position P1 of the cam groove 542.

[0104] 4. Modifiable aspects Modifiable aspects of the configurations disclosed in each of the embodiments described above will now be explained. The configurations disclosed herein, including the modifiable aspects shown below, as well as the fourth to ninth embodiments described below, can be applied in combination with configurations disclosed in other embodiments, as long as this does not create a contradiction. The embodiments disclosed herein are in all respects merely illustrative. Therefore, each embodiment can be modified in various ways as appropriate, without departing from the spirit of the invention.

[0105] (1) In the above description, a configuration in which the transmission member 51 is connected to the input member 1 so as to rotate integrally with it was described as an example. However, the configuration is not limited to such a configuration, and for example, as in the fourth embodiment illustrated below, the input member 1 may be arranged on a different axis from the transmission member 51 and connected to the transmission member 51 via a link mechanism, gear mechanism, etc.

[0106] (2) In the above description, the linear motion conversion mechanism 5 was described as having a configuration comprising a cam mechanism 52 and a guide mechanism 53. However, the linear motion conversion mechanism 5 is not limited to such a configuration, and may also have a configuration comprising a crank mechanism, a ball screw mechanism, a rack and pinion, etc., as shown in the fourth embodiment illustrated below.

[0107] (3) In the above description, the elastic member 6 was described as having a configuration that includes two springs, an inner spring 61 (first elastic member) and an outer spring 62 (second elastic member). However, the configuration is not limited to such a configuration, and in the fourth to ninth embodiments shown below, although examples are omitted, for example, the elastic member 6 may be composed of one or more springs, or it may be composed of an elastic body other than a spring.

[0108] (4) In the above description, a configuration in which the friction member 7 is attached to the outer circumferential surface of the piston 4 was described as an example. However, the configuration is not limited to such a configuration, and in the fourth to ninth embodiments shown below, although examples are omitted, the friction member 7 may also be attached to the inner circumferential surface of the cylindrical member 3. In this configuration, it is preferable that the viscoelastic body 71 be attached to the inner circumferential surface of the friction member 7.

[0109] (5) In the above description, a configuration in which the outer circumferential surface of the piston 4 includes the outer parallel surface 4c was described as an example. However, the configuration is not limited to such a configuration, and a configuration in which the outer circumferential surface of the piston 4 does not include the outer parallel surface 4c, such as the fourth embodiment illustrated below, is also possible, that is, a configuration in which the outer inclined surface 4a and the outer restricting surface 4b are formed continuously.

[0110] 5.Operation feeling In the above description, we focused on ensuring a large reaction force from the reaction force generation mechanism 2 when moving the piston 4 toward the second axial direction L2, while appropriately performing the return movement of the input member 1 to its initial position when moving the piston 4 toward the first axial direction L1 using the biasing force of the elastic member 6, that is, appropriately performing the movement of the piston 4 in different directions along the axial direction L. However, by varying the strength of the reaction force from the reaction force generation mechanism 2 when moving the piston 4 toward the second axial direction L2, the driver's feel can be further improved. For example, the feel of operating the pedal 19 as an operating tool includes elements such as (a) the responsiveness when the driver operates the pedal 19, (b) the balance between rigidity and responsiveness, (c) the feel during sudden operation, (d) the holdability of the pedal 19, and (e) the ease with which the pedal 19 returns. Below, we will also focus on these points and illustrate the fourth to ninth embodiments as examples. Points similar to those described in the first to third embodiments above will be omitted from explanation as appropriate.

[0111] Here, for example, if pedal 19 is a brake pedal, then each of the elements (a) to (e) above corresponds to the following: (a) The responsiveness when the driver operates pedal 19 corresponds to the initial braking effect that is easily perceived by the driver. For example, it corresponds to the setting of an appropriate starting load for the brake. Also, (b) the balance between rigidity and responsiveness corresponds to the rigidity and braking effect perceived by the driver. For example, it corresponds to the appropriate change in rigidity on the operating surface (tread surface). (c) The feel during sudden operation corresponds to the resistance when pedal 19 is pressed quickly, such as during sudden braking. Physically, this corresponds to the application of an appropriate kinetic friction force to the operation of pedal 19 (input member 1). (d) The retention of pedal 19 means that pedal 19 is appropriately held in response to the operation of pedal 19 (input member 1). Physically, this corresponds to the application of an appropriate static friction force necessary to hold pedal 19. (e) The good return of the pedal 19 corresponds to the controllability of the pedal 19 (input member 1) when the driver reduces the force applied to the pedal 19, that is, when the force applied to the pedal 19 is released. Physically, this corresponds to applying an appropriate frictional force that does not worsen the return of the pedal 19 (input member 1) to its initial position.

[0112] As described above, the reaction force generating mechanism 2 includes an inner spring 61 (first elastic member) that biases the piston 4 toward the first axial direction L1, and an outer spring 62 (second biasing member) that biases the piston 4 toward the first axial direction L1 with a biasing force different from that of the inner spring 61 (corresponding here to the "spring constant"). Here, when the piston 4 moves toward the second axial direction L2 along the axial direction L with respect to the cylindrical member 3, the region in which the inner spring 61 mainly deforms is called the first stroke region, and the region in which the outer spring 62 mainly deforms is called the second stroke region. Here, the "region in which deformation mainly occurs" is not the absolute value of the deformation amount from the free length of the elastic members 6 (first elastic member (inner spring 61), second elastic member (outer spring 62)), but rather the region in which the deformation amount of one elastic member (spring) corresponding to the amount of movement of the piston 4 is greater than that of the other elastic member (spring).

[0113] The "first stroke region," which is the region in which the "first elastic member (inner spring 61) mainly deforms," ​​is the region in which the deformation ratio of the first elastic member (inner spring 61) is higher than the deformation ratio of the second elastic member (outer spring 62), and also includes the region in which only the first elastic member (inner spring 61) deforms. The "second stroke region," which is the region in which the "second elastic member (outer spring 62) mainly deforms," ​​is the region in which the deformation ratio of the second elastic member (outer spring 62) is higher than the deformation ratio of the first elastic member (inner spring 61), and also includes the region in which only the second elastic member (outer spring 62) deforms. In this embodiment, both the first elastic member (inner spring 61) and the second elastic member (outer spring 62) deform in the first stroke region, and in the second stroke region, only the second elastic member (outer spring 62) deforms.

[0114] The graph in Figure 8 shows the relationship between the operating force applied to the input member 1 (in this case, the force applied to the pedal 19) and the amount of movement of the input member 1 (in this case, the pedal stroke). The pedal stroke represents the position of the input member 1 between the initial position "P0" when no force is applied to the pedal 19 and the full stroke position "Pf" when the pedal 19 is fully depressed and the input member 1 is at its maximum displacement. As shown in Figure 8, the characteristic curve shows different trajectories when the pedal 19 is depressed (shown by the solid line) and when the pedal 19 is released (shown by the dashed line), exhibiting so-called hysteresis.

[0115] Pedal 19 generally has some play, and as shown in Figure 8, until the pedaling force reaches "f1", the input member 1 hardly moves in response to the applied pedaling force. When the pedaling force reaches "f1", the input member 1 begins to move substantially in response to the pedaling force applied to pedal 19 (substantial initial position "P1"). The first stroke region RS1 is the displacement region of the input member 1 on the side where the movement begins, that is, the displacement region of the input member 1 on the side where the position of the input member 1 is the initial position "P0". The second stroke region RS2 is the displacement region on the side of the full stroke position "Pf", which is the position where the pedal 19 is pressed down the most.

[0116] As shown in Figure 8, in the first stroke region RS1, the amount of change in pedal stroke with respect to the pedaling force is larger compared to the second stroke region RS2. As described above, the operating input device 100 exemplified in this specification, including the embodiments exemplified below, is equipped with a reaction force generation mechanism 2 that generates a reaction force to the rotational operating force input to the input member 1, and the amount of movement (stroke) of the input member 1 is affected by the reaction force. For example, in the first embodiment described above, when the piston 4 begins to move axially to the second side L2 and the inner spring 61 compresses, the amount of movement of the input member 1 is affected by the reaction force due to the deformation of the inner spring 61, of the two springs. The first stroke region RS1 can be said to be the region in which the inner spring 61 deforms. Furthermore, when the piston 4 moves axially to the second side L2 and the outer spring 62 also begins to compress, the amount of movement of the input member 1 is affected by the reaction force due to the deformation of the outer spring 62, of the two springs. The second stroke region RS2 can be described as the region where the outer spring 62 deforms most significantly.

[0117] As described above, the inner spring 61 and the outer spring 62 have different biasing forces (spring constants). In the reaction force generation mechanism 2 illustrated in this specification, the biasing force of the outer spring 62 is greater than that of the inner spring 61. Therefore, in the second stroke region RS2 compared to the first stroke region RS1, the amount of movement of the input member 1 per unit operating force is smaller for the operating force applied to the input member 1. This makes it easier to provide a reliable operating feel to the driver operating the pedal 19. For example, if the pedal 19 is a brake pedal, the driver can easily feel the effectiveness of the brakes due to the reaction force that increases as the amount of pedal 19 is pressed increases.

[0118] The gradient of stroke change differs between the first stroke region RS1, where the deformation of the inner spring 61 is the primary force acting, and the second stroke region RS2, where the deformation of the outer spring 62 is the primary force acting. If there is a difference between the gradient of stroke change in the first stroke region RS1 and the gradient of stroke change in the second stroke region RS2, the driver may feel uncomfortable when transitioning from the first stroke region RS1 to the second stroke region RS2. For this reason, a transition region RT is provided to mitigate the gradient change so that the pedal stroke does not undergo a sudden gradient change when transitioning from the first stroke region RS1 to the second stroke region RS2. In the reaction force generation mechanism 2 exemplified in this specification, the transition region RT is provided before the transition to the second stroke region RS2, and the transition region RT is included in the first stroke region RS1.

[0119] In the reaction force generation mechanism 2 illustrated in this specification, the transition region RT is realized using an elastic member (here, rubber) that functions as a damper. For example, in the first to third embodiments, when the piston 4 moves axially to the second side L2 and the inner spring 61 compresses, the first damper rubber 68 (see Figures 2, 5, and 6) comes into contact with the inner retaining portion 82. As the piston 4 moves further axially to the second side L2, the first damper rubber 68 compresses further. As the piston 4 moves further axially to the second side L2, the retaining member 8 also begins to move axially to the second side L2, and the outer spring 62 also begins to compress. Generally, the range of change in pedal stroke from when the first damper rubber 68 comes into contact with the inner retaining portion 82 and begins to compress, until before the outer spring 62 begins to compress, corresponds to the transition region RT. In order to smoothly connect the first stroke region RS1 and the second stroke region RS2, which have different gradients, it is preferable that the gradient change in the transition region RT is nonlinear with respect to the pedaling force (operating force).

[0120] Such dampers are also provided to create a bottoming region RB at the end of the second stroke region RS2. The elastic member (rubber in this case) that realizes the bottoming region RB is the second damper rubber 69 (see Figures 2, 5, and 6). For example, in the first to third embodiments, when the piston 4 and the retaining member 8 move axially to the second side L2 and the outer spring 62 compresses, the second damper rubber 69 comes into contact with the bottom wall portion 32 of the cylindrical member 3. Furthermore, as the piston 4 and the retaining member 8 move axially to the second side L2, the second damper rubber 69 compresses. Generally, the range of change in pedal stroke after the second damper rubber 69 comes into contact with the bottom wall portion 32 and begins to compress corresponds to the bottoming region RB.

[0121] As shown in Figure 8, once the position of the input member 1 reaches "P1" (and the pedal force reaches "f1" or later), the pedal stroke of the input member 1 increases almost linearly with respect to the pedal force. By appropriately setting the biasing force of the inner spring 61 (low spring constant, so-called low spring rate), an appropriate starting load can be applied (realization of element (a)). The stroke change shown by the dashed line in Figure 8 illustrates the case when the driver performs a quick operation (e.g., sudden braking). In this case, an appropriate dynamic friction force (e.g., the operating friction force by the friction member 7) is applied, which gives the driver a sense of operation and suppresses the feeling of the pedal not working (realization of element (c)).

[0122] The position "P2" of the input member 1 is both the end point of the first stroke range RS1 and the start point of the second stroke range RS2. The pedal force at this time is "f2". The pedal force "f3" is the maximum pedal force specified for dry roads. In the second stroke range RS2, particularly between pedal forces "f2" and "f3", the retention of the input member 1 is ensured by, for example, the application of static friction force by the friction member 7 (realization of element (d)). Furthermore, by appropriately setting the biasing force of the outer spring 62 (setting a higher spring constant than the inner spring 61), the pedal stroke is changed with an appropriate gradient. This makes it possible to achieve both effective braking and a sense of rigidity for the driver (realization of element (d)).

[0123] The pedaling force "f5" is the force required to move the input member 1 until the second damper rubber 69 contacts the bottom wall portion 32. If the driver applies further force to the pedal 19 beyond the pedaling force "f5", the second damper rubber 69 compresses. This ensures a higher reaction force, giving the driver the feeling of maximum pedal pressure.

[0124] Furthermore, as shown in Figure 8, the characteristic curve exhibits different trajectories when the pedal 19 is pressed (shown by the solid line) and when it is released (shown by the dashed line), thus possessing so-called hysteresis. As described above, by applying an appropriate frictional force with the friction member 7, the controllability of the input member 1 is ensured when the driver reduces the operating force on the pedal 19, that is, when the force applied to the pedal 19 is released (realization of element (e)).

[0125] Here, the amount of movement of the piston 4 with respect to the amount of rotation of the input member 1 to which rotational operating force is input (rotation angle or arc trajectory centered on a reference point (such as the pivot axis)) is defined as the rotation-to-linear conversion ratio of the linear conversion mechanism 5 ("amount of rotation (rotation angle) / linear movement amount", which is appropriately abbreviated as "linear conversion ratio"). The first variable rate is defined as the difference between the linear conversion ratio at the start of the first stroke region RS1 and the linear conversion ratio at the end of the first stroke region, divided by the linear conversion ratio at the start of the first stroke region. The second variable rate is defined as the difference between the linear conversion ratio at the start of the second stroke region RS2 and the linear conversion ratio at the end of the second stroke region, divided by the linear conversion ratio at the start of the second stroke region.

[0126] As described above with reference to Figure 8, considering the play, the input member 1 effectively begins to move at position "P1". Therefore, the "first start time" corresponds to the pedal stroke in which the input member 1 is located at position "P1". The "first end time" and the "second start time" are both position "P2" corresponding to the same pedal stroke. The "second end time" corresponds to the pedal stroke in which the input member 1 is at the full stroke position "Pf".

[0127] By displacing in a direction that increases the reaction force in response to the rotational operation, the operator can easily perceive the operation. For this reason, the linear motion conversion ratio changes in a direction that decreases as the rotational operation amount increases. The linear motion conversion ratio at the end of the first phase is less than or equal to the linear motion conversion ratio at the beginning of the first phase, and the linear motion conversion ratio at the end of the second phase is less than the linear motion conversion ratio at the beginning of the second phase. Also, since the first stroke area RS1 and the second stroke area RS2 are continuous, the linear motion conversion ratio at the beginning of the second phase and the linear motion conversion ratio at the end of the first phase are the same. The first variable rate is an index that shows the change in the direction in which the rotational linear motion conversion ratio stays the same or decreases, and the second variable rate is an index that shows the rate of change in the direction in which the rotational linear motion conversion ratio decreases. The linear motion conversion mechanism 5 is configured such that the second variable rate is higher than the first variable rate.

[0128] Specific examples will be described later with reference to graphs showing the change in the linear motion conversion ratio (Figures 15 and 19: the eighth and ninth embodiments), but it is preferable that the second variable ratio be 20% or more. In the second stroke region RS2, as the rotation angle of the input member 1 increases, the reaction force becomes stronger, making it easier for the operator to perceive a clear sense of operation. In addition, in the second stroke region RS2, the linearity between rotational motion and linear motion is reduced compared to the first stroke region RS1 (especially in Figure 15). In this way, the operation input device 100 is designed to allow the operator to feel a greater sense of operation.

[0129] In the embodiments illustrated in Figures 15 and 19, as will be described later, the first variable ratio is "5.2%" and "0%", respectively, and in this specification, embodiments in which the first variable ratio is zero or greater are illustrated. However, the first variable ratio also includes cases where "the linear motion conversion ratio at the first start < the linear motion conversion ratio at the first end", resulting in a value less than zero (a negative value). That is, the linear motion conversion mechanism 5 is configured such that the second variable ratio is higher on the positive side than the first variable ratio.

[0130] 6. Other examples of rotation-to-linear conversion (Watt linkage mechanism) The following describes the operation input devices 100 according to the fourth to ninth embodiments. Before describing each embodiment, the structure of the linear motion conversion mechanism 5 in the operation input devices 100 according to the fourth to seventh embodiments will be described. In the operation input devices 100 according to the fourth to seventh embodiments, the form of power transmission from the input member 1 to the reaction force generation mechanism 2 differs from that of the first to third embodiments described above. In the first to third embodiments, an example was given in which the oscillation axis Y on which the input member 1 oscillates and the reference axis X of the linear motion conversion mechanism 5 are coaxial. However, as shown in Figure 9, in the fourth to seventh embodiments, the oscillation axis Y and the reference axis X are on different axes. The reference axis X is orthogonal to the oscillation axis Y.

[0131] In the first embodiment, in the linear motion conversion mechanism 5, the rotational motion of the input member 1 is converted into linear motion in a direction along the rotation axis (oscillating axis Y) of the rotational motion by the cam mechanism 52. That is, the rotational motion of the transmission member 51, which is an axial member to which the rotation of the input member 1 around the oscillating axis Y (= reference axis X) is transmitted, and the linear motion along the reference axis X are mutually converted by the cam mechanism 52. In the fourth to seventh embodiments, the rotational motion of the input member 1 is converted into linear motion via a Watt linkage mechanism 20, which is a mechanism that can create a pseudo-linear motion within a specific range.

[0132] The Watt link mechanism 20 has a first link axis W1 and a second link axis W2 as fixed axes, and a third link axis W3 and a fourth link axis W4 as driven axes. The first link axis W1, the second link axis W2, the third link axis W3, and the fourth link axis W4 are parallel to each other and are simply referred to as "link axes" when not distinguished. The first link axis W1 coincides with the oscillating axis Y. The oscillating axis Y and the reference axis X are orthogonal, and each link axis is orthogonal to the reference axis X. The third link axis W3 and the fourth link axis W4 are positioned on the reference axis X when the input member 1 is in its initial position, as viewed in the direction along the link axes.

[0133] The first link axis W1 and the third link axis W3 are connected by the first link section 21, the second link axis W2 and the fourth link axis W4 are connected by the second link section 22, and the third link axis W3 and the fourth link axis W4 are connected by the third link section 23. The first link section 21, the second link section 22, and the third link section 23 are pivotable around the axis to which each link section is connected.

[0134] Furthermore, a clevis 24 is pivotably connected to the fourth link axis W4, and the clevis 24 is connected to the piston 4 via a pinhead 25. In response to the oscillation of the input member 1 around the first link axis W1 (oscillating axis Y), the third link section 23 performs a pseudo-linear motion along the reference axis X, causing the fourth link axis W4 to also perform a pseudo-linear motion along the reference axis X, and the clevis 24 to perform a linear motion along the reference axis X. As a result, the piston 4, which is connected to the clevis 24 via the pinhead 25, performs a linear motion along the reference axis X. In this way, the linear motion conversion mechanism 5 of the fourth to seventh embodiments converts the rotational motion of the input member 1 into linear motion using a conversion mechanism centered on the Watt link mechanism 20.

[0135] 7. Fourth Embodiment Figure 10 is a cross-sectional view of the operation input device according to the fourth embodiment, along the axial direction L. As described above, the operation input device 100 of the fourth embodiment performs rotational-to-linear motion conversion by the Wattlink mechanism 20. The following describes the structure relating to the linear motion of the piston 4. Matters common to those described in the first to third embodiments will be omitted as appropriate. In the first embodiment (and the second embodiment), the piston 4 is provided with a plate-shaped sliding portion 41 with a relatively short axial dimension L. In the fourth embodiment, the piston 4 is provided with a long shaft-shaped sliding portion 41 with a longer axial dimension L compared to the first embodiment.

[0136] Furthermore, in the first embodiment (and the second embodiment), the cylindrical member 3 that houses the piston 4 is formed as a cylindrical shape with the same diameter, but in the fourth embodiment, the peripheral wall portion 31 is formed as a stepped cylindrical shape having a first peripheral wall portion 31a and a second peripheral wall portion 31b of different diameters. The first peripheral wall portion 31a is positioned on the first axial side L1 relative to the second peripheral wall portion 31b. Also, the diameter of the second peripheral wall portion 31b is larger than the diameter of the first peripheral wall portion 31a. The second peripheral wall portion 31b is formed to have a larger diameter than the first peripheral wall portion 31a in order to house the outer spring 62 radially inward R1.

[0137] In the first and second embodiments (see Figures 2 and 5), the bottom wall portion 32 of the cylindrical member 3 is exemplified as being integrally formed from the same material as the peripheral wall portion 31. However, in the fourth embodiment (and the fifth to seventh embodiments described later), as shown in Figure 10 (and Figures 11 to 13), the bottom wall portion 32 is exemplified as being formed from a different material than the peripheral wall portion 31 and connected to the peripheral wall portion 31 in an integrated manner. The bottom wall portion 32 may be made from a different material than the peripheral wall portion 31 in the first and second embodiments as well, and may be integrally formed from the same material as the peripheral wall portion 31 in the fourth embodiment (and the fifth to seventh embodiments).

[0138] The piston 4 housed in the cylindrical member 3 slides along the axial direction L on the inner surface of the first circumferential wall portion 31a. The reaction force generation mechanism 2 includes a friction member 7 positioned at the sliding point between the outer surface of the piston 4 (the outer surface of the axial sliding portion 41) and the inner surface of the cylindrical member 3 (the inner surface of the first circumferential wall portion 31a), and a tensioning force applying mechanism 74 that presses the friction member 7 from the radially inward R1 to the radially outward R2, thereby applying tension to the inner surface of the cylindrical member 3. The sliding portion 41 has an annular friction member placement groove 41t formed in the outer surface of the axial sliding portion 41, recessed radially inward R1. The friction member 7 is positioned in the friction member placement groove 41t. The friction member 7 includes a sliding member 73 positioned on the sliding surface between the cylindrical member 3 and the piston 4, and a base material 70 to which the sliding member 73 is bonded radially outward R2. Furthermore, an elastic body 72 (annular elastic body) that functions as a tensioning force application mechanism 74 is also arranged in the friction member arrangement groove 41t. The elastic body 72 is positioned radially inward R1 of the base material 70 and presses the base material 70 radially outward R2 together with the sliding member 73 by elastic force. In other words, the tensioning force application mechanism 74 presses the base material 70, on which the sliding member 73 is positioned radially outward R2, from radially inward R1 to radially outward R2. To put it another way, the tensioning force application mechanism 74 presses the base material 70 from the side on which the base material 70 is positioned toward the side on which the sliding member 73 is positioned along the radial direction R. As with the second embodiment described with reference to Figure 5, an O-ring can be used as the elastic body 72, for example.

[0139] Figure 10 illustrates a configuration in which the reaction force generation mechanism 2 includes a tensioning force applying mechanism 74 that presses the friction member 7 from the radially inner R1 to the radially outer R2, thereby applying tension to the inner circumferential surface of the cylindrical member 3. However, although not shown in the figure, the reaction force generation mechanism 2 may also include a tensioning force applying mechanism 74 that presses the friction member 7 from the radially outer R2 to the radially inner R1, thereby applying tension to the outer circumferential surface of the piston 4. In this case, the tensioning force applying mechanism 74 presses the base material 70 from the radially outer R2 to the radially inner R1. Specifically, an annular friction member placement groove is formed in the inner circumferential surface of the cylindrical member 3, recessed radially outward R2, and the friction member 7 is placed in this friction member placement groove. The friction member 7 includes a sliding member 73 positioned on the sliding surface between the piston 4 and the cylindrical member 3, and a base material 70 to which the sliding member 73 is bonded radially inward R1. An elastic body 72 (annular elastic body) that functions as a tensioning force-applying mechanism 74 is placed in the friction member arrangement groove. The elastic body 72 is positioned radially outward R2 of the base material 70 and presses the base material 70 radially inward R1 together with the sliding member 73 by elastic force. That is, the tensioning force-applying mechanism 74 presses the base material 70, on which the sliding member 73 is positioned radially inward R1, from radially outward R2 toward radially inward R1. In this case as well, the tensioning force-applying mechanism 74 presses the base material 70 from the side on which the base material 70 is positioned toward the side on which the sliding member 73 is positioned along the radial direction R. In this case as well, an O-ring can be used as the elastic body 72, for example.

[0140] Furthermore, the sliding member 73 is preferably a viscoelastic body 71, similar to the first and second embodiments.

[0141] 8. Fifth Embodiment Next, the operation input device 100 according to the fifth embodiment will be described with reference to Figure 11. The fifth embodiment differs from the fourth embodiment in the configuration of the reaction force generation mechanism 2, specifically the configuration of the piston 4. The following description will focus on the differences from the fourth embodiment. Points that are not specifically explained are self-evident from the above descriptions of each embodiment, and will therefore be omitted as appropriate.

[0142] As shown in Figure 11, in the fifth embodiment, the piston 4 is configured to include two members, a first member 40a and a second member 40b. More specifically, the axial sliding portion 41 of the piston 4 is divided into a first member 40a and a second member 40b. The first member 40a is positioned relatively on the first axial side L1, and the second member 40b is positioned relatively on the second axial side L2. A screw hole 401 is formed on the reference axis X on the first axial side L1 of the second member 40b, and a female screw groove is formed on the inner circumferential wall of the screw hole 401. A male screw portion 402 is formed on the second axial side L2 of the first member 40a, positioned on the reference axis X and projecting toward the second axial side L2. The male screw portion 402 is formed to project toward the second axial side L2 from a flange surface 4f that extends to the outer circumferential surface of the radially outer R2 of the axial first member 40a. A male screw groove is formed on the outer peripheral wall of the second axial side L2 of the male screw portion 402. By screwing the male screw portion 402 into the screw hole 401, the first member 40a and the second member 40b are connected, and the piston 4 is integrally formed.

[0143] In the fifth embodiment, the friction member arrangement groove 41t, in which the friction member 7 and the elastic body 72 as a tensioning mechanism 74 are arranged, is formed between the opposing end face 4g, which is the end face of the second member 40b facing the first member 40a on the axial direction L1, and the flange face 4f of the first member 40a. The width of this friction member arrangement groove 41t, i.e., the groove width d, which is the dimension along the axial direction L, changes depending on the depth (length) of the male threaded portion 402 that is screwed into the screw hole 401. When the male threaded portion 402 is screwed deeper into the screw hole 401, the arrangement positions of the first member 40a and the second member 40b in the axial direction L become closer, and the distance between the opposing end face 4g and the flange face 4f becomes shorter. As a result, the groove width d becomes narrower. Conversely, if the male threaded portion 402 is only shallowly screwed into the threaded hole 401, the positional positions of the first member 40a and the second member 40b in the axial direction L will be separated, and the distance between the opposing end face 4g and the flange face 4f will increase. As a result, the groove width d will be wider.

[0144] As the groove width d narrows, the elastic body 72 is compressed in the axial direction L and stretched in the radial direction R. Since the base of the male thread portion 402 of the first member 40a is located on the radially inner side R1 of the friction member arrangement groove 41t, the stretching of the elastic body 72 toward the radially inner side R1 is restricted, and the elastic body 72 stretches toward the radially outer side R2. Consequently, the tensioning force exerted by the elastic body 72 (annular elastic body), which functions as a tensioning force-applying mechanism 74, becomes stronger. Note that even if the stretching toward the radially inner side R1 is not restricted and the elastic body 72 stretches on both sides of the radial direction R, the tensioning force toward the radially outer side R2 will also become stronger to some extent. Conversely, as the groove width d widens, the tensioning force exerted by the elastic body 72 weakens.

[0145] In other words, the reaction force generation mechanism 2 of the operation input device 100 according to the fifth embodiment includes a position adjustment mechanism 400 which has a male screw portion 402 and a screw hole 401 to adjust the arrangement position of the first member 40a and the second member 40b in the axial direction L. By adjusting the arrangement position of the first member 40a and the second member 40b by this position adjustment mechanism 400, the tension force applied by the tension force application mechanism 74, which is composed of an annular elastic body 72, is also adjusted. In other words, the reaction force generation mechanism 2 of the operation input device 100 according to the fifth embodiment includes a tension force adjustment mechanism that can adjust the tension force applied to the friction member 7, and this tension force adjustment mechanism is composed of the position adjustment mechanism 400.

[0146] In the fourth and fifth embodiments, the tension force applied to the friction member 7 is generally the same regardless of the direction in which the piston 4 moves along the axial direction L. That is, the tension force is almost constant when the driver presses down the pedal 19 and when the pedal 19 returns to its initial position, and no significant effect can be expected with respect to hysteresis (corresponding to element (e)) as explained with reference to Figure 8. However, sufficient effects can be expected regarding the rotation-to-linear conversion ratio in the first stroke region RS1 and the second stroke region RS2 (corresponding to elements (a) to (d)).

[0147] In the sixth and seventh embodiments, which will be described below with reference to Figures 12 and 13, the tension applied to the friction member 7 changes according to the pedal stroke. Therefore, the effects of elements (a) to (e) can be obtained.

[0148] 9. Sixth Embodiment Similar to the fifth embodiment, the sixth embodiment also comprises a piston 4 with two components, a first component 40a and a second component 40b, as shown in Figure 12. That is, the axial sliding portion 41 of the piston 4 is divided into a first component 40a positioned relatively on the first axial side L1 and a second component 40b positioned relatively on the second axial side L2. In the fifth embodiment, the first component 40a and the second component 40b are connected via a screw adjustment mechanism (position adjustment mechanism 400) so as not to move relative to each other during the operation of the linear motion conversion mechanism 5. However, in the sixth embodiment, the first component 40a and the second component 40b are connected so as to be able to move relative to each other along the axial direction L even during the operation of the linear motion conversion mechanism 5.

[0149] As shown in Figure 12, an engagement hole 411 is formed on the reference axis X on the first axial side L1 of the second member 40b. A projection 412 is formed on the second axial side L2 of the first member 40a, positioned on the reference axis X and projecting outwards on the second axial side L2. The projection 412 is formed to project outwards on the second axial side L2 from a flange surface 4f that extends to the outer peripheral surface of the radially outer R2 of the axial first member 40a. By engaging the projection 412 with the engagement hole 411, the first member 40a and the second member 40b are connected in a state that allows relative movement in the axial direction L, and the piston 4 is integrally formed. The outer diameter of the projection 412 is smaller than the inner diameter of the engagement hole 411, and the projection 412 is slidable relative to the engagement hole 411.

[0150] In the sixth embodiment, the friction member arrangement groove 41t, in which the friction member 7 and the elastic body 72 as a tensioning mechanism 74 are arranged, is formed between the opposing end face 4g, which is the end face of the second member 40b facing the first member 40a on the axial direction L1, and the flange face 4f of the first member 40a. The width of this friction member arrangement groove 41t, i.e., the groove width d, which is the dimension along the axial direction L, changes depending on the engagement depth of the projection 412 with respect to the engagement hole 411. When the projection 412 is inserted deeply into the engagement hole 411, the positional positions of the first member 40a and the second member 40b in the axial direction L become closer, and the distance between the opposing end face 4g and the flange face 4f becomes shorter. As a result, the groove width d becomes narrower. Conversely, when the projection 412 is inserted shallowly into the engagement hole 411, the positional positions of the first member 40a and the second member 40b in the axial direction L become further apart, and the distance between the opposing end face 4g and the flange face 4f becomes longer. This increases the groove width d.

[0151] As the groove width d narrows, the elastic body 72 is compressed in the axial direction L and stretched in the radial direction R. Since there is a protrusion 412 of the first member 40a on the radially inner side R1 of the friction member arrangement groove 41t, the stretching of the elastic body 72 toward the radially inner side R1 is restricted, and the elastic body 72 stretches toward the radially outer side R2. Therefore, the tensioning force by the elastic body 72 (annular elastic body) which functions as a tensioning force-applying mechanism 74 becomes stronger. Note that even if the stretching toward the radially inner side R1 is not restricted and the elastic body 72 stretches on both sides of the radial direction R, the tensioning force toward the radially outer side R2 will also become stronger to some extent. Conversely, as the groove width d widens, the tensioning force by the elastic body 72 weakens.

[0152] The protrusion 412 moves axially towards the second side L2 as the operating input from the input member 1 becomes stronger. That is, as the operating input from the driver becomes stronger, the protrusion 412 moves axially towards the second side L2, compressing the elastic body 72 in the axial direction L, increasing the tension force radially outward R2, and thus increasing the reaction force. When the tip of the axial second side L2 of the protrusion 412 comes into contact with the bottom of the engagement hole 411, the relative movement between the first member 40a and the second member 40b is restricted. When no rotational operating force is input, and the positional relationship between the first member 40a and the second member 40b along the axial direction L is in its initial state, the axial distance L between the tip of the axial second side L2 of the protrusion 412 and the bottom of the engagement hole 411 is set to be shorter than the groove width d. This enables the first member 40a and the second member 40b to function as stoppers for relative movement, and allows the compression of the elastic body 72 in the axial direction L to be limited while the compressive force is less than the compressive limit of the elastic body 72 in the axial direction L. In other words, it is possible to limit the tension force while amplifying the tension force toward the radially outward direction R2.

[0153] In other words, the operation input device 100 according to the sixth embodiment includes a tension force amplification mechanism 410 in which the reaction force generation mechanism 2 is capable of amplifying the tension force applied to the friction member 7 as the linear operating force that moves the piston 4 along the axial direction L to the axial second side L2 increases. As described above, the piston 4 includes a first member 40a arranged on the axial first side L1 and a second member 40b arranged on the axial second side L2 so as to be relatively movable with respect to the first member 40a in the axial direction L. The tension force application mechanism 74 is composed of an elastic body 72 (annular elastic body) arranged between the first member 40a and the second member 40b in the axial direction L. The tension force amplification mechanism 410 is composed of a divided piston 4 and the elastic body 72 (annular elastic body). The elastic body 72 functions as a tension-applying mechanism 74 that applies tension to the radially outward R2, and also functions as a tension-amplifying mechanism 410 in which the tension to the radially outward R2 increases as the axial separation distance L between the first member 40a and the second member 40b (which can be considered as the groove width d) decreases.

[0154] Furthermore, in the case of return (when there is no operational input to the input member 1), the elastic force of the elastic body 72 also acts in the direction that separates the first member 40a and the second member 40b. As a result, the tension force is reduced, and the piston 4 can move with less tension force when moving in the axial direction first side L1 compared to when moving in the axial direction second side L2. Therefore, the input member 1 can be quickly returned to its initial position.

[0155] 10. Seventh Embodiment Similar to the fifth and sixth embodiments, the seventh embodiment also comprises a piston 4 with two members, a first member 40a and a second member 40b, as shown in Figure 13. That is, the axial sliding portion 41 of the piston 4 is divided into a first member 40a positioned relatively on the first axial side L1 and a second member 40b positioned relatively on the second axial side L2. In the seventh embodiment, as in the sixth embodiment, the first member 40a and the second member 40b are connected so as to be able to move relative to each other along the axial direction L.

[0156] As shown in Figure 13, an engagement hole 411 is formed on the reference axis X on the first axial side L1 of the second member 40b. A projection 412 is formed on the second axial side L2 of the first member 40a, positioned on the reference axis X and projecting outwards on the second axial side L2. By engaging the projection 412 with the engagement hole 411, the first member 40a and the second member 40b are connected, and the piston 4 is integrally formed. The outer diameter of the projection 412 is smaller than the inner diameter of the engagement hole 411, and the projection 412 is slidable relative to the engagement hole 411.

[0157] In the sixth embodiment, the bottom of the radially inner R1 of the friction member arrangement groove 41t is a surface parallel to the axial direction L, but in the seventh embodiment, the bottom is an inclined surface (first member outer peripheral inclined surface 410a) that is inclined with respect to the axial direction L. The first member outer peripheral inclined surface 410a is inclined radially inward R1 as it approaches the axial second side L2. Also, in the sixth embodiment and the like, the cross-sectional shape of the base material 70 is rectangular, but in the seventh embodiment, the base material 70 also has a tapered surface (an inclined surface in cross-section) radially inner R1 surface in accordance with the shape of the friction member arrangement groove 41t (base material inner peripheral inclined surface 70a). The base material inner peripheral inclined surface 70a is inclined radially inward R1 as it approaches the axial second side L2. The first member outer peripheral inclined surface 410a and the base material inner peripheral inclined surface 70a are in contact opposite each other in the radial direction R.

[0158] Similar to the sixth embodiment, the relative positions of the first member 40a and the second member 40b in the axial direction L change depending on the engagement depth of the projection 412 with respect to the engagement hole 411. When the projection 412 is inserted deeply into the engagement hole 411, the positional alignment of the first member 40a and the second member 40b in the axial direction L approaches, and conversely, when the projection 412 is inserted shallowly into the engagement hole 411, the positional alignment of the first member 40a and the second member 40b in the axial direction L moves further apart.

[0159] As the positional positions of the first member 40a and the second member 40b in the axial direction L approach each other, the outer circumferential inclined surface 410a of the first member comes into contact with the first axial direction L1, and the inner circumferential inclined surface 70a of the base material comes into contact with the second axial direction L2. That is, the first member 40a and the base material 70 come into contact with each other at a position where the radial dimension R is larger, and the force pushing the base material 70 radially outward R2 by the first member 40a, i.e., the tension force radially outward R2, increases. As shown in Figure 13, in the seventh embodiment, an annular elastic body 72 is not placed between the first member 40a and the base material 70. In the sixth embodiment, the annular elastic body 72 functions as a tension force applying mechanism 74, but in the seventh embodiment, the divided piston 4 and the base material 70 function as a tension force applying mechanism 74.

[0160] That is, as described above, the operation input device 100 according to the seventh embodiment includes a piston 4 which comprises a first member 40a positioned on the first axial side L1 and a second member 40b positioned on the second axial side L2 so as to be relatively movable in the axial direction L with respect to the first member 40a. The outer circumferential surface of the first member 40a is provided with a first member outer circumferential inclined surface 410a (outer circumferential inclined surface) which is inclined toward the radially inward R1 as it moves toward the second axial side L2. The base material 70 is provided with a base material inner circumferential inclined surface 70a (inner circumferential inclined surface) which is inclined toward the radially inward R1 as it moves toward the second axial side L2. The base material 70 is positioned between the first member 40a and the second member 40b in the axial direction L, and between the first member outer circumferential inclined surface 410a and the inner circumferential surface of the cylindrical member 3, with the base material inner circumferential inclined surface 70a engaging with the first member outer circumferential inclined surface 410a. The tension-applying mechanism 74 applies tension to the inner surface of the cylindrical member 3 by changing the position in the axial direction L where the outer circumferential inclined surface 410a of the first member and the inner circumferential inclined surface 70a of the base material come into contact, as the piston 4 moves toward the second axial direction L2.

[0161] In the case of return (when there is no operational input to the input member 1), the radial stress R transmitted from the inner circumferential surface of the cylindrical member 3 to the outer circumferential inclined surface 410a of the first member via the base material 70 causes slippage at the engagement portion (contact portion) between the outer circumferential inclined surface 410a of the first member and the inner circumferential inclined surface 70a of the base material, causing the first member 40a and the second member 40b to separate. As the first member 40a and the second member 40b separate, the tension force decreases, so the input member 1 can be returned to its initial position while reducing the tension force. In the seventh embodiment without an elastic body 72, it is preferable to set the inclination angle of the outer circumferential inclined surface 410a of the first member and the inner circumferential inclined surface 70a of the base material such that the pressing force at the engagement portion (contact portion) between the outer circumferential inclined surface 410a of the first member and the inner circumferential inclined surface 70a of the base material, and the slippage at the engagement portion (contact portion) due to stress from the inner circumferential surface of the cylindrical member 3, are appropriately generated.

[0162] 11. Eighth Embodiment As examples of the configuration of the linear motion conversion mechanism 5, the first to third embodiments illustrate a configuration using a cam roller, while the fourth to seventh embodiments illustrate a configuration using a Watt link mechanism 20. However, the linear motion conversion mechanism 5 is not limited to these configurations, and may also be a configuration using the principle of a link mechanism and a cam (composite mechanism 200), as illustrated in Figure 14.

[0163] The composite mechanism 200, like the Watt link mechanism 20 described above with reference to Figure 9, has a first link axis W1 and a second link axis W2 as fixed axes. This composite mechanism 200 also has a third link axis W3 as a driven axis. The first link axis W1 coincides with the oscillation axis Y of the input member 1. The first link axis W1 and the reference axis X are orthogonal, and each link axis (second link axis W2, third link axis W3) is also orthogonal to the reference axis X. Furthermore, the third link axis W3 is positioned on the reference axis X when viewed in the direction along the link axis with the input member 1 in its initial position.

[0164] The first link axis W1 and the third link axis W3 are connected by the first link section 21, and the second link axis W2 and the third link axis W3 are connected by the second link section 22. The third link axis W3 is positioned within a link cam groove 29 formed in the first link section 21. When the input member 1 swings clockwise around the first link axis W1, the third link axis W3 moves axially to the second side L2 at a certain position within the link cam groove 29 (on the side of the input member 1 within the link cam groove 29 in Figure 13), and the second link section 22 swings with the second link axis W2 as its pivot point. When the swing angle of the input member 1 exceeds a reference value, the third link axis W3 moves within the link cam groove 29 (to the side opposite to the input member 1 within the link cam groove 29 in Figure 13). The rotation-to-linear conversion ratio can be changed by the movement of the third link axis W3 within the link cam groove 29.

[0165] Figure 15 is a graph showing an example of the rotation-to-linear conversion ratio (= rotation angle / linear movement) of the operation input device 100 according to the eighth embodiment. The horizontal axis represents the pedal stroke, and the vertical axis represents the rotation-to-linear conversion ratio. The oscillation angle (pedal stroke) of the input member 1, in which the third link axis W3 moves within the link cam groove 29, roughly corresponds to the boundary between the first stroke range RS1 and the second stroke range RS2.

[0166] As shown in Figure 15, in the first stroke region RS1, the rotation-to-linear conversion ratio changes from "7.7" at the beginning of the first stroke region RS1 to "7.3" at the end of the first stroke region RS1. The first variable ratio, which is the difference of "0.4" between the rotation-to-linear conversion ratio of "7.7" at the beginning of the first stroke region and the rotation-to-linear conversion ratio of "7.3" at the end of the first stroke region, divided by the rotation-to-linear conversion ratio of "7.7" at the beginning of the first stroke region, is approximately "5.2%".

[0167] As shown in Figure 15, in the second stroke region RS2, the rotation-to-linear conversion ratio changes from "7.3" at the start of the second stroke region RS2 to "5.6" at the end of the second stroke region RS2. The second variable ratio, which is the difference of "1.7" between the rotation-to-linear conversion ratio "7.3" at the start of the second stroke region and the rotation-to-linear conversion ratio "5.6" at the end of the second stroke region, divided by the rotation-to-linear conversion ratio "7.3" at the start of the second stroke region, is approximately "23.3%".

[0168] As described above with reference to Figure 8, the operation input device 100 is configured such that the linear motion conversion mechanism 5 has a second variable ratio that is higher than the first variable ratio. The linear motion conversion mechanism 5 of the operation input device 100 according to the eighth embodiment is also configured such that the second variable ratio is higher than the first variable ratio. Preferably, the linear motion conversion mechanism 5 is configured such that the linear motion conversion ratio in the second stroke region RS2 increases as the amount of movement of the piston 4 increases as the rotation angle of the input member 1 increases, and the second variable ratio is 20% or more. The linear motion conversion mechanism 5 of the operation input device 100 according to the eighth embodiment has a second variable ratio of approximately "23.3%", and thus satisfies this condition.

[0169] 12. The ninth embodiment As a third embodiment, another configuration example of the reaction force generation mechanism 2 equipped with a linear motion conversion mechanism 5 using the cam mechanism 52 described above is illustrated as a ninth embodiment with reference to Figures 16 to 19. The following explanation will focus on the differences from each of the above embodiments (particularly the first to third embodiments). Points not specifically explained are the same as in each of the above embodiments.

[0170] The linear motion conversion mechanism 5 comprises a transmission member 51, a piston 4, a cylindrical member 3, a cam mechanism 52, and a guide mechanism 53.

[0171] The transmission member 51 is a shaft member to which the rotation of the input member 1 is transmitted. The transmission member 51 is formed to extend along the axial direction L. The transmission member 51 is positioned on the reference axis X. The transmission member 51 is rotatably supported by the cylindrical member 3 around the reference axis X and rotates integrally with the input member 1. The piston 4 has an outer mounting portion 451 positioned radially outward R2 relative to the transmission member 51. The piston 4 is positioned on the reference axis X. The piston 4 is movably supported by the cylindrical member 3 in the axial direction L.

[0172] The cam mechanism 52 is configured to convert the rotational motion of the transmission member 51 into axial motion L of the piston 4 and transmit it. The transmission member 51 and the piston 4 are connected to each other via the cam mechanism 52. The piston 4 comprises a sliding portion 41, a shaft portion 42, and a flange portion 43 (radially extending portion).

[0173] The guide mechanism 53 is configured to restrict the circumferential movement C of the piston 4 relative to the cylindrical member 3, while allowing the axial movement L of the piston 4 relative to the cylindrical member 3. Therefore, the piston 4 and the cylindrical member 3 are connected to each other via the guide mechanism 53.

[0174] The transmission member 51 includes a first connecting portion 511 connected to the input member 1, a second connecting portion 512 connected to the cam mechanism 52, a third connecting portion 513 connecting the first connecting portion 511 and the second connecting portion 512 in the axial direction L, and a fourth connecting portion 514 connected to the end of the first connecting portion 511 on the axial direction L1. The first connecting portion 511 is arranged to penetrate the first side wall portion 34 and the second side wall portion 35 in the axial direction L, and rotates integrally with the input member 1. The second connecting portion 512 is arranged spaced apart from the first connecting portion 511 on the axial direction L2. The third connecting portion 513 is formed in a cylindrical shape centered on the reference axis X and is connected to the end of the first connecting portion 511 on the axial direction L2. The fourth connecting portion 514 is formed in a cylindrical shape centered on the reference axis X and rotates integrally with the first connecting portion 511.

[0175] As shown in Figure 16, in the ninth embodiment, the cylindrical member 3 comprises a first side wall portion 34 and a second side wall portion 35. Each of the first side wall portion 34 and the second side wall portion 35 is formed to extend along the radial direction R. The first side wall portion 34 is joined to the circumferential wall portion 31 from the axial first side L1 so as to close the opening on the axial first side L1 of the circumferential wall portion 31. The first side wall portion 34 is positioned on the axial second side L2 with respect to the input member 1. The second side wall portion 35 is positioned on the axial first side L1 with respect to the input member 1.

[0176] The first connecting portion 511 of the transmission member 51 is positioned to penetrate the first side wall portion 34 and the second side wall portion 35 in the axial direction L. A third connecting portion 513 is connected to the axial second side L2 end of the first connecting portion 511. In this embodiment, the third connecting portion 513 is formed in a cylindrical shape centered on the reference axis X.

[0177] The cover portion 33 is formed to cover the fourth connecting portion 514 from the axial first side L1 and the radially outer side R2. The cover portion 33 is joined to the second side wall portion 35 from the axial first side L1.

[0178] As shown in Figures 16 and 17, the outer arrangement portion 451 of the piston 4 includes a path forming portion 44. The path forming portion 44 is formed in a cylindrical shape centered on the reference axis X and is arranged to extend from the sliding portion 41 toward the first axial side L1.

[0179] The cam path 54 is a first cam groove 575 formed so as to penetrate the path forming portion 44 radially in the direction R at each of two locations in the path forming portion 44 facing the radial direction R. The cam driven member 55 is a first pin 576 that rolls on the inner surfaces of each of the pair of first cam grooves 575.

[0180] Each of the pair of first pins 576 is inserted into the first cam groove 575 from a radially inward R1. Each of the pair of first pins 576 is rotatably held by a first retaining portion 761 so as to rotate around its axis, with the portion of the first pin 576 radially inward R1 from the first cam groove 575 being held by the first retaining portion 761. The pair of first retaining portions 761 are fixed to the second connecting portion 512 of the transmission member 51. In this way, each of the pair of first pins 576 is configured to roll on the inner surface of the first cam groove 575.

[0181] As shown in Figure 17, the guide path 56 is a first guide groove 585 formed so as to penetrate the path forming section 44 radially in the radial direction R at each of the two locations in the path forming section 44 facing the radial direction R. The guide driven member 57 is a second pin 586 that rolls on the inner surface of each of the pair of first guide grooves 585.

[0182] Each of the pair of second pins 586 is inserted into the first guide groove 585 from a radially inward R1. Each of the pair of second pins 586 is rotatably held by a second retaining part 861 so as to rotate around its axis, with the portion of the second pin 586 radially inward R1 from the first guide groove 585 being held rotatably. The pair of second retaining parts 861 are fixed to the peripheral wall portion 31 of the cylindrical member 3. In this way, each of the pair of second pins 586 is configured to roll on the inner surface of the first guide groove 585.

[0183] Figure 18 shows a diagram of the path forming section 44, in which a pair of first cam grooves 575 and a pair of first guide grooves 585 are formed, unfolded on a plane along the circumferential direction C.

[0184] As shown in Figure 18, the pair of first cam grooves 575 are arranged at equal intervals in the circumferential direction C. Each of the pair of first cam grooves 575 is inclined so that it gradually moves toward the first axial side L1 as it moves toward the first circumferential side C1.

[0185] Each of the pair of first pins 576 is at the position C2 on the second circumferential side in the first cam groove 575 (hereinafter referred to as the "reference position") when no rotational force is applied to the input member 1. Each of the pair of first pins 576 is then relatively movable to the position L1 on the first axial side in the first cam groove 575 (hereinafter referred to as the "limit position") when a rotational force is applied to the input member 1. Therefore, when a rotational force is applied to the input member 1 so that the pair of first pins 576 rotate towards the first circumferential side C1, the piston 4 moves towards the second axial side L2.

[0186] Each of the pair of first cam grooves 575 is formed such that the angle of inclination with respect to the axial direction L gradually decreases as it moves from the reference position to the limit position. In other words, the first angle θ1, which is the angle of inclination of the first cam groove 575 with respect to the axial direction L at the reference position, is greater than the second angle θ2, which is the angle of inclination of the first cam groove 575 with respect to the axial direction L at the limit position. Therefore, the ratio of the amount of movement of the piston 4 in the axial direction L to the amount of movement of the first pin 576 in the circumferential direction C at the reference position is smaller than the ratio of the amount of movement of the piston 4 in the axial direction L to the amount of movement of the first pin 576 in the circumferential direction C at the limit position.

[0187] Thus, the linear motion conversion mechanism 5 of the ninth embodiment is configured such that as the rotation angle of the input member 1 increases from the reference angle (the rotation angle when no rotational operating force is applied to the input member 1), the amount of axial movement L of the piston 4 per unit rotation angle of the input member 1 gradually increases. This configuration makes it easier to provide a natural feel for the operator when operating the control device.

[0188] A pair of first guide grooves 585 are arranged at equal intervals in the circumferential direction C. Each of the pair of first guide grooves 585 is formed to extend along the axial direction L.

[0189] Each of the pair of second pins 586 is at the position L2 on the second axial side in the first guide groove 585 when no rotational force is applied to the input member 1. When a rotational force is applied to the input member 1, each of the pair of second pins 586 is relatively movable to the position L1 on the first axial side in the first guide groove 585. At this time, since the outer diameter of each of the pair of second pins 586 is set to be approximately the same as the circumferential dimension C of the first guide groove 585, the relative movement of the pair of second pins 586 in the circumferential direction C is restricted. As a result, the rotation of the piston 4 in the circumferential direction C relative to the cylindrical member 3 is restricted.

[0190] Figure 19 is a graph showing an example of the rotation-to-linear conversion ratio (= rotation angle / linear movement) of the operation input device 100 according to the ninth embodiment. The horizontal axis represents the pedal stroke, and the vertical axis represents the rotation-to-linear conversion ratio.

[0191] As shown in Figure 19, in the first stroke region RS1, the rotation-to-linear conversion ratio is the same value at the start of the first stroke region RS1 ("7.77") and at the end of the first stroke region RS1 ("7.77"). Therefore, the first variable ratio, which is the difference between the rotation-to-linear conversion ratio at the start of the first stroke region and the rotation-to-linear conversion ratio at the end of the first stroke region divided by the rotation-to-linear conversion ratio at the start of the first stroke region, is zero.

[0192] As shown in Figure 19, in the second stroke region RS2, the rotation-to-linear conversion ratio changes from "7.77" at the start of the second stroke region RS2 to "5.93" at the end of the second stroke region RS2. The second variable ratio, which is the difference of "1.84" between the rotation-to-linear conversion ratio "7.77" at the start of the second stroke region and the rotation-to-linear conversion ratio "5.93" at the end of the second stroke region, divided by the rotation-to-linear conversion ratio "7.77" at the start of the second stroke region, is approximately "23.68%".

[0193] As described above with reference to Figure 8, the operation input device 100 is configured such that the linear motion conversion mechanism 5 has a second variable ratio that is higher than the first variable ratio. The linear motion conversion mechanism 5 of the operation input device 100 according to the ninth embodiment is also configured such that the second variable ratio is higher than the first variable ratio. Preferably, the linear motion conversion mechanism 5 is configured such that the linear motion conversion ratio in the second stroke region RS2 increases as the amount of movement of the piston 4 increases as the rotation angle of the input member 1 increases, and the second variable ratio is 20% or more. The linear motion conversion mechanism 5 of the operation input device 100 according to the ninth embodiment has a second variable ratio of approximately "23.68%", which satisfies this condition.

[0194] 13. Summary of Embodiments The following describes the overview of the operation input device (100) described above.

[0195] In one embodiment, the operation input device (100) is: An input member (1) to which a rotational operating force is applied, The device comprises a reaction force generating mechanism (2) that generates a reaction force to the rotational operating force input to the input member (1), With the direction along the reference axis (X) defined as the axial direction (L), one side of the axial direction (L) is defined as the first axial side (L1), and the other side of the axial direction (L) is defined as the second axial side (L2). The reaction force generation mechanism (2) is, A cylindrical member (3) positioned on the aforementioned reference axis (X), The piston (4) housed in the cylindrical member (3), A linear motion conversion mechanism (5) mutually converts the rotational motion of the input member (1) and the linear motion of the piston (4) along the axial direction (L), A first elastic member (61) biases the piston (4) toward the first axial direction (L1), The piston (4) is biased toward the first axial direction (L1), and a second elastic member (62) has a different biasing force than the first elastic member (61), When the piston (4) moves along the axial direction (L1) toward the second axial direction (L2) relative to the cylindrical member (3), the region in which the first elastic member (61) mainly deforms is defined as the first stroke region (RS1), and the region in which the second elastic member (62) mainly deforms is defined as the second stroke region (RS2). The amount of movement of the piston (4) with respect to the rotation angle of the input member (1) is defined as the linear motion conversion ratio of the linear motion conversion mechanism. The first variable ratio is defined as the difference between the linear motion conversion ratio at the first starting period (P1), which is the start of the first stroke range (RS1), and the linear motion conversion ratio at the first ending period (P2), which is the end of the first stroke range (RS1), divided by the linear motion conversion ratio at the first starting period (P1). The second variable ratio is obtained by dividing the difference between the linear motion conversion ratio at the second starting period (P2), which is the start of the second stroke region (RS2), and the linear motion conversion ratio at the second ending period (Pf), which is the end of the second stroke region (RS2), by the linear motion conversion ratio at the second starting period (P2). The linear motion conversion mechanism (5) is configured such that the second variable ratio is higher than the first variable ratio.

[0196] With this configuration, the first variable ratio, which represents the degree of change in the linear motion conversion ratio in the first stroke range (RS1), and the second variable ratio, which represents the degree of change in the linear motion conversion ratio in the second stroke range (RS2), are different. This allows for a difference in the reaction force perceived by the operator throughout the entire stroke range. When the operator applies rotational force to the input member (1), the difference in the perceived reaction force makes it easier for the operator to feel the operation, such as the stiffness corresponding to the stroke amount and the responsiveness. Specifically, in the first stroke range (RS1), the variable ratio of the linear motion conversion ratio is low, so the change in reaction force with respect to the stroke is small, and the operation on the input member (1) becomes faster, allowing the operator to feel the effect coming on sooner. Also, in the second stroke range (RS2), the change in reaction force with respect to the stroke is large, so the operator can control the effect while feeling the change in stiffness when applying rotational force to the input member (1) more strongly. Since the piston (4) is biased axially toward the first side (L1) by the first elastic member (61) and the second elastic member (62), the input member (1) can also be properly returned to its initial position.

[0197] Furthermore, it is preferable that the linear motion conversion mechanism (5) of the operation input device (100) is configured such that the linear motion conversion ratio in the second stroke range (RS2) increases as the rotation angle of the input member (1) increases, and the second variable ratio becomes 20% or more.

[0198] With this configuration, as the rotation angle of the input member (1) increases in the second stroke range (RS2), the reaction force becomes stronger, making it easier for the operator to perceive a firm sense of control.

[0199] In addition, as one embodiment, the operation input device (100) is: An input member (1) to which a rotational operating force is applied, The device comprises a reaction force generating mechanism (2) that generates a reaction force to the rotational operating force input to the input member (1), With the direction along the reference axis (X) defined as the axial direction (L), one side of the axial direction (L) is defined as the first axial side (L1), and the other side of the axial direction (L) is defined as the second axial side (L2). The reaction force generation mechanism (2) is, A cylindrical member (3) positioned on the aforementioned reference axis (X), The piston (4) housed in the cylindrical member (3), A linear motion conversion mechanism (5) mutually converts the rotational motion of the input member (1) and the linear motion of the piston (4) along the axial direction (L), A first elastic member (61) biases the piston (4) toward the first axial direction (L1), The piston (4) is biased toward the first axial direction (L1), and a second elastic member (62) has a different biasing force than the first elastic member (61), The direction perpendicular to the reference axis (X) is defined as the radial direction (R), the direction along the radial direction (R) toward the reference axis (X) is defined as the radially inward direction (R1), and the direction along the radial direction (R) away from the reference axis (X) is defined as the radially outward direction (R2). The reaction force generation mechanism (2) is, A friction member (7) is positioned at the sliding point between the outer circumferential surface of the piston (4) and the inner circumferential surface of the cylindrical member (3), The device comprises a tensioning mechanism (74) that presses the friction member (7) from the radially inward side (R1) toward the radially outward side (R2) to apply tension to the inner circumferential surface of the cylindrical member (3), or presses the friction member (7) from the radially outward side (R2) toward the radially inward side (R1) to apply tension to the outer circumferential surface of the piston (4), The friction member (7) is A sliding member (73) is positioned on the sliding surface between the cylindrical member (3) and the piston (4), The base material (70) to which the sliding member (73) is bonded to the radially outer side (R2) or the radially inner side (R1), The tension-applying mechanism (74) presses the base material (70), on which the sliding member (73) is positioned on the radially outer side (R2), from the radially inner side (R1) toward the radially outer side (R2), or presses the base material (70), on which the sliding member (73) is positioned on the radially inner side (R1), from the radially outer side (R2) toward the radially inner side (R1).

[0200] With this configuration, the tension-applying mechanism (74) applies tension to the inner surface of the cylindrical member (3) or the outer surface of the piston (4), thereby strengthening the frictional force of the friction member (7) and making it easier to apply an appropriate reaction force to the rotational operating force applied to the input member (1) by the operator. Furthermore, because the biasing force of the first elastic member (61) and the biasing force of the second elastic member (62) are different, it is possible to create a difference in the reaction force perceived by the operator throughout the entire stroke range of the rotational stroke of the input member (1) and the linear stroke of the piston (4). When the operator applies a rotational operating force to the input member (1), the difference in the reaction force perceived by the operator makes it easier for the operator to feel the operating sensation, such as rigidity according to the stroke amount and responsiveness. Since the piston (4) is biased toward the first axial side (L1) by the first elastic member (61) and the second elastic member (62), the return movement of the input member (1) to its initial position can also be performed appropriately.

[0201] Furthermore, the operating input device (100) preferably has a sliding member (73) made of a viscoelastic material (71).

[0202] With this configuration, the frictional force of the friction member (7) can be increased as the movement speed of the piston (4) increases. Therefore, it is easier to improve the feel of operating the control input device (100).

[0203] Furthermore, the operation input device (100) is, The reaction force generating mechanism (2) includes a tension force adjustment mechanism that can adjust the tension force applied to the friction member (7), The piston (4) is The first member (40a) is arranged on the axial first side (L1), The second member (40b) is positioned on the axial second side (L2), The device includes a position adjustment mechanism (400) for adjusting the arrangement position of the first member (40a) and the second member (40b) in the axial direction (L), The tension-applying mechanism (74) is composed of an annular elastic body (72) disposed between the first member (40a) and the second member (40b) in the axial direction (L), The tension adjustment mechanism is comprised of the position adjustment mechanism (400).

[0204] The appropriate reaction force may differ depending on the object on which the operating input device (100) is mounted, and the appropriate tension force may also differ depending on the object. With this configuration, by providing a tension force adjustment mechanism, the tension force can be appropriately adjusted according to the object on which the operating input device (100) is mounted.

[0205] Furthermore, the operation input device (100) is, The reaction force generating mechanism (2) includes a tension force amplification mechanism (410) that can amplify the tension force applied to the friction member (7) as the linear operating force that moves the piston (4) along the axial direction (L) toward the second axial direction (L2) increases. The piston (4) is The first member (40a) is arranged on the axial first side (L1), The first member (40a) is positioned on the second axial side (L2) so as to be movable relative to the first member (40a) in the axial direction (L), The tension-applying mechanism (74) is composed of an annular elastic body (72) disposed between the first member (40a) and the second member (40b) in the axial direction (L), The tension amplification mechanism (74) is configured to include the divided piston (4) and the annular elastic body (72).

[0206] With this configuration, as the axial distance (d) between the first member (40a) and the second member (40b) decreases, the annular elastic body (72) expands radially (R), thereby appropriately increasing the tension force radially outward (R2). As the rotational operating force increases and the linear movement force increases, the tension force becomes stronger, providing the operator with an appropriate feel of operation.

[0207] Furthermore, the operation input device (100) is, The piston (4) The first member (40a) is arranged on the axial first side (L1), The first member (40a) is positioned on the second axial side (L2) so as to be movable relative to the first member (40a) in the axial direction (L), The outer circumferential surface of the first member (40a) is provided with an outer circumferential inclined surface (410a) that is inclined toward the radially inward (R1) direction as it is toward the axial second side (L2), The base material (70) has an inner circumferential inclined surface (70a) that is inclined radially inward (R1) as it is directed toward the second axial side (L2), The base material (70) is positioned between the first member (40a) and the second member (40b) in the axial direction (L), and between the outer peripheral inclined surface (410a) and the inner peripheral surface of the cylindrical member (3), with the inner peripheral inclined surface (70a) engaging with the outer peripheral inclined surface (410a). Preferably, the tension-applying mechanism (74) applies tension to the inner surface of the cylindrical member (3) by changing the position in the axial direction (L) where the outer circumferential inclined surface (410a) and the inner circumferential inclined surface (70a) come into contact as the piston (4) moves toward the second axial direction (L2).

[0208] With this configuration, when the piston (4) moves to the second axial side (L2), as the axial distance (d) between the first member (40a) and the second member (40b) decreases, the radial position (R) of the base material (70) can be moved radially outward (R2). In other words, as the linear operating force that moves the piston (4) to the second axial side (L2) increases, the tension force applied to the friction member (7) via the base material (70) can be increased. As the rotational operating force increases and the linear movement force increases, the tension force increases, which provides the operator with an appropriate operating feel.

[0209] In one embodiment, the operation input device (100) is: An input member (1) to which a rotational operating force is applied, The device comprises a reaction force generating mechanism (2) that generates a reaction force to the rotational operating force input to the input member (1), The direction along the reference axis (X) is defined as the axial direction (L), one side of the axial direction (L) is defined as the first axial side (L1), and the other side of the axial direction (L) is defined as the second axial side (L2). The reaction force generation mechanism (2) is, A cylindrical member (3) positioned on the aforementioned reference axis (X), The piston (4) housed in the cylindrical member (3), A linear motion conversion mechanism (5) mutually converts the rotational motion of the input member (1) and the linear motion of the piston (4) along the axial direction (L), An elastic member (6) biases the piston (4) toward the first axial direction (L1), The device comprises a friction member (7) positioned at the sliding point between the outer circumferential surface of the piston (4) and the inner circumferential surface of the cylindrical member (3), The friction member (7) is configured such that the frictional force is greater when the piston (4) moves to the second axial side (L2) compared to when the piston (4) moves to the first axial side (L1).

[0210] With this configuration, when a rotational operating force is applied to the input member (1) so that the piston (4) moves to the second axial side (L2), the biasing force of the elastic member (6) toward the first axial side (L1) and the relatively large frictional force of the friction member (7) can generate a relatively large reaction force to the rotational operating force applied to the input member (1). On the other hand, when the rotational operating force applied to the input member (1) is released, the biasing force of the elastic member (6) toward the first axial side (L1) and the relatively small frictional force of the friction member (7) can move the piston (4) toward the first axial side (L1) relatively easily. This ensures a large reaction force from the reaction force generation mechanism (2) when moving the piston (4) toward the second axial side (L2), while the return movement of the input member (1) to its initial position when moving the piston (4) toward the first axial side (L1) can be appropriately performed by the biasing force of the elastic member (6). Therefore, it is easier to achieve both improved operability of the control input device (100) and improved reliability of the return operation of the input member (1).

[0211] Furthermore, it is preferable that the operating input device (100) has a viscoelastic body (71) arranged on the sliding surface of the friction member (7) with the cylindrical member (3).

[0212] With this configuration, the frictional force of the friction member (7) can be increased as the movement speed of the piston (4) increases. Therefore, it is easier to improve the feel of operating the control input device (100).

[0213] Furthermore, the operation input device (100) is, The friction member (7) is attached to the outer circumferential surface of the piston (4), The direction perpendicular to the aforementioned reference axis (X) is defined as the radial direction (R), and the direction moving away from the reference axis (X) along the radial direction (R) is defined as the radially outward direction (R2). The outer circumferential surface of the piston (4) includes an outer circumferential inclined surface (4a) that is inclined radially outward (R2) as it is directed toward the first axial side (L1), The friction member (7) includes an inner circumferential inclined surface (7a) that is inclined toward the radially outward (R2) direction as it moves toward the axial first side (L1) and contacts the outer circumferential inclined surface (4a), The reaction force generating mechanism (2) applies tension to the inner surface of the cylindrical member (3) by changing the position in the axial direction (L) where the outer circumferential inclined surface (4a) and the inner circumferential inclined surface (7a) come into contact as the piston (4) moves toward the second axial direction (L2).

[0214] With this configuration, when the piston (4) moves to the second axial side (L2), the friction member (7) is easily moved to the side where the radial distance (R) between the outer surface of the piston (4) and the inner surface of the cylindrical member (3) becomes narrower. This makes it possible to appropriately apply tension to the cylindrical member (3).

[0215] Furthermore, it is preferable that the operating input device (100) has a friction member (7) that is an annular elastic body (72) and is mounted on the outer circumferential surface of the piston (4) and positioned on the reference axis (X).

[0216] This configuration allows the friction member (7) to be stably attached to the outer circumferential surface of the piston (4). Furthermore, when the piston (4) moves in the second axial direction (L2), it is easier to move the friction member (7) further to the side where the radial width (R) between the outer circumferential surface of the piston (4) and the inner circumferential surface of the cylindrical member (3) narrows. [Explanation of Symbols]

[0217] 100: Operation input device, 1: Input member, 2: Reaction force generation mechanism, 3: Cylindrical member, 4: Piston, 4a: Outer peripheral inclined surface, 5: Linear motion conversion mechanism, 6: Elastic member, 7: Friction member, 7a: Inner peripheral inclined surface, 40a: First member, 40b: Second member, 70: Base material, 70a: Inner peripheral inclined surface of base material (an inner peripheral inclined surface provided on the radially inward side of the base material, inclined radially inward as it is directed toward the second axial side), 71: Viscoelastic body, 72: Elastic body (annular elastic body, annular elastic body), 73: Sliding member, 74: Tensioning force application mechanism, 400: Position adjustment mechanism (tensioning force adjustment mechanism), 410: Tensioning force amplification mechanism, 410a: Outer peripheral inclined surface of the first member (outer peripheral inclined surface of the first member that is inclined radially inward as it moves toward the second axial side), X: Reference axis, L: Axial direction, L1: First axial side, L2: Second axial side, R: Radial direction, R1: Radial inward, R2: Radial outward, RS1: First stroke area, RS2: Second stroke area

Claims

1. An input member to which a rotational operating force is applied, The system includes a reaction force generating mechanism that generates a reaction force to the rotational operating force input to the input member, With the direction along the reference axis as the axial direction, one side of the axial direction is designated as the axial first side, and the other side of the axial direction is designated as the axial second side. The reaction force generation mechanism is, A cylindrical member positioned on the aforementioned reference axis, A piston housed in the cylindrical member, A linear motion conversion mechanism that mutually converts the rotational motion of the input member and the linear motion of the piston along the axial direction, A first elastic member that biases the piston toward the first axial direction, The piston is biased toward the first axial direction, and a second elastic member having a different biasing force from the first elastic member is provided, When the piston moves along the axial direction toward the second axial direction relative to the cylindrical member, the region in which the first elastic member mainly deforms is defined as the first stroke region, and the region in which the second elastic member mainly deforms is defined as the second stroke region. The amount of movement of the piston with respect to the rotation angle of the input member is defined as the linear motion conversion ratio of the linear motion conversion mechanism. The first variable ratio is defined as the difference between the linear motion conversion ratio at the first starting period, which is the start of the first stroke range, and the linear motion conversion ratio at the first ending period, which is the end of the first stroke range, divided by the linear motion conversion ratio at the first starting period. The second variable ratio is obtained by dividing the difference between the linear motion conversion ratio at the second starting period, which is the start of the second stroke range, and the linear motion conversion ratio at the second ending period, which is the end of the second stroke range, by the linear motion conversion ratio at the second starting period. The linear motion conversion mechanism is configured such that the second variable ratio is higher than the first variable ratio, and is an operation input device.

2. The aforementioned linear motion conversion mechanism is In the second stroke range, the linear motion conversion ratio increases as the rotation angle of the input member increases, and the amount of movement of the piston increases. The operation input device according to claim 1, configured such that the second variable ratio is 20% or more.

3. An input member to which a rotational operating force is applied, The system includes a reaction force generating mechanism that generates a reaction force to the rotational operating force input to the input member, With the direction along the reference axis as the axial direction, one side of the axial direction is designated as the axial first side, and the other side of the axial direction is designated as the axial second side. The reaction force generation mechanism is, A cylindrical member positioned on the aforementioned reference axis, A piston housed in the cylindrical member, A linear motion conversion mechanism that mutually converts the rotational motion of the input member and the linear motion of the piston along the axial direction, A first elastic member that biases the piston toward the first axial direction, The piston is biased toward the first axial direction, and a second elastic member having a different biasing force from the first elastic member is provided, The direction perpendicular to the aforementioned reference axis is defined as the radial direction, the direction toward the aforementioned reference axis along the radial direction is defined as the radially inward direction, and the direction away from the aforementioned reference axis along the radial direction is defined as the radially outward direction. The reaction force generation mechanism is, A friction member is positioned at the sliding point between the outer circumferential surface of the piston and the inner circumferential surface of the cylindrical member, The system includes a tensioning mechanism that presses the friction member from the radially inner side toward the radially outer side to apply tension to the inner circumferential surface of the cylindrical member, or presses the friction member from the radially outer side toward the radially inner side to apply tension to the outer circumferential surface of the piston, The friction member is A sliding member is disposed on the sliding surface between the cylindrical member and the piston, The substrate comprises the sliding member to which the sliding member is bonded on the radially outer or radially inner side, The tension-applying mechanism is an operation input device that presses the base material, on which the sliding member is positioned radially outward, from the radially inward side toward the radially outward side, or presses the base material, on which the sliding member is positioned radially inward, from the radially outward side toward the radially inward side.

4. The operation input device according to claim 3, wherein the sliding member is a viscoelastic material.

5. The reaction force generating mechanism includes a tension force adjustment mechanism that can adjust the tension force applied to the friction member, The aforementioned piston is The first member arranged on the axial first side, The second member, which is positioned on the axial second side, The system includes a position adjustment mechanism for adjusting the axial position of the first member and the second member, The tension-applying mechanism is composed of an annular elastic body disposed between the first member and the second member in the axial direction, The operation input device according to claim 3 or 4, wherein the tension adjustment mechanism is configured by the position adjustment mechanism.

6. The reaction force generating mechanism includes a tension force amplification mechanism capable of amplifying the tension force applied to the friction member as the linear operating force that moves the piston along the axial direction toward the second axial side increases, The aforementioned piston is The first member arranged on the axial first side, The system comprises a second member positioned on the second axial side so as to be movable relative to the first member in the axial direction, The tension-applying mechanism is composed of an annular elastic body disposed between the first member and the second member in the axial direction, The operation input device according to claim 3 or 4, wherein the tension amplification mechanism comprises a divided piston and an annular elastic body.

7. The aforementioned piston is The first member arranged on the axial first side, The system comprises a second member positioned on the second axial side so as to be movable relative to the first member in the axial direction, The outer circumferential surface of the first member is provided with an outer circumferential inclined surface that is inclined radially inward as it is directed toward the second axial side, The substrate has an inner circumferential inclined surface that is inclined radially inward as it is directed toward the second axial side, The base material is positioned between the first member and the second member in the axial direction, and between the outer peripheral inclined surface and the inner peripheral surface of the cylindrical member, with the inner peripheral inclined surface engaging with the outer peripheral inclined surface. The operation input device according to claim 3 or 4, wherein the tensioning mechanism applies tension to the inner surface of the cylindrical member by changing the axial position where the outer circumferential inclined surface and the inner circumferential inclined surface come into contact as the piston moves toward the second axial side.

8. An input member to which a rotational operating force is applied, The system includes a reaction force generating mechanism that generates a reaction force to the rotational operating force input to the input member, The direction along the reference axis is defined as the axial direction, one side of the axial direction is defined as the first axial side, and the other side of the axial direction is defined as the second axial side. The reaction force generation mechanism is, A cylindrical member positioned on the aforementioned reference axis, A piston housed in the cylindrical member, A linear motion conversion mechanism that mutually converts the rotational motion of the input member and the linear motion of the piston along the axial direction, An elastic member that biases the piston toward the first axial direction, The piston and the cylindrical member are provided with a friction member positioned at the sliding point between the outer circumferential surface of the piston and the inner circumferential surface of the cylindrical member, An operation input device wherein the friction member is configured such that the frictional force is greater when the piston moves in the second axial direction than when the piston moves in the first axial direction.

9. The operation input device according to claim 8, wherein the friction member has a viscoelastic body disposed on the sliding surface with the cylindrical member.

10. The friction member is attached to the outer circumferential surface of the piston. The direction perpendicular to the aforementioned reference axis is defined as the radial direction, and the direction moving away from the aforementioned reference axis along the radial direction is defined as the radially outward direction. The outer circumferential surface of the piston includes an outer circumferential inclined surface that is inclined radially outward as it is directed toward the first axial side, The friction member includes an inner circumferential inclined surface that is inclined radially outward as it moves toward the first axial side and contacts the outer circumferential inclined surface, The operation input device according to claim 8 or 9, wherein the reaction force generating mechanism applies tension to the inner surface of the cylindrical member by changing the axial position where the outer circumferential inclined surface and the inner circumferential inclined surface come into contact as the piston moves toward the second axial side.

11. The operation input device according to claim 10, wherein the friction member is an annular elastic body and is positioned on the reference axis while attached to the outer circumferential surface of the piston.

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