Steering input device and steering device of the steer-by-wire type

Abstract

The steering actuation input device comprises a first shaft, a second shaft, a coupling element (19, 20) arranged between the first and second shafts, a first torsion spring arranged on the first shaft and connected to the coupling element, and a second torsion spring arranged on the second shaft. The second torsion spring has the same spring constant as the first torsion spring. A preload is applied to the second torsion spring. Until the first shaft is rotated 60 degrees in a predetermined direction of rotation, a compressive force from the first torsion spring acts on the first shaft. After the first shaft has been rotated 60 degrees in the predetermined direction of rotation, a compressive force from both the first and second torsion springs acts on the first shaft.

Description

Technical field

[0001] The present invention relates to a steering actuation input device and a steering device of the “steer-by-wire” type. State of the art

[0002] For example, a steering actuation input device is known which is described in the following patent specification 1.

[0003] The steering actuation input device from patent document 1 comprises a first thrusting element for generating a reaction force against one direction of rotation of a steering actuation input element of a steering device and a second thrusting element for generating a reaction force against the other direction of rotation, which is opposite to the first direction of rotation, of the steering actuation input element. The switching of the generation of the reaction force by the first thrusting element and the second thrusting element is effected by a linear motion conversion device, which converts a rotational force input by the steering actuation input element into a linear motion. Citation list

[0004] Patent document 1: Japanese unpublished patent application no. 2015-082071 Summary of the invention: Technical problem

[0005] Since special pushing elements are arranged in the steering actuation input device of patent specification 1 to generate the reaction forces against the respective rotation directions of the steering actuation input element, the number of parts for the steering actuation input device increases, which leads to a problem of increasing manufacturing costs of the steering actuation input device.

[0006] The present invention was developed taking into account the conventional situation. The aim of the present invention is therefore to provide a steering actuation input device that can reduce manufacturing costs. Solution to the problem

[0007] As one aspect of the present invention, a steering actuation input device comprises a thrusting element which exerts a thrusting force against the rotation of a shaft, and this thrusting element comprises: a first thrusting element which exerts a thrusting force on the shaft regardless of the direction of rotation of the shaft; and a second thrusting element which is attached with a preload exerted on the second thrusting element and which, after the first thrusting element exerts the thrusting force, exerts a thrusting force on the shaft regardless of the direction of rotation of the shaft. Effects of the invention

[0008] According to the present invention, it is possible to reduce the manufacturing costs of the steering actuation input device. Brief description of the figures. Fig. Figure 1 is a schematic diagram of a steer-by-wire steering device to which a steering actuation input device of the present invention is applied. Fig. Figure 2 is a longitudinal section of a steering actuation input device according to a first embodiment. Fig. Figure 3 is an explanatory diagram showing the positional relationship between a first torsion spring, a first arc groove and a second arc groove of a first shaft in a neutral position viewed from the axial direction of the first shaft. Fig. Figure 4 is an explanatory diagram showing the positional relationship between the first torsion spring, the first arc groove and the second arc groove of the first shaft when the first shaft is rotated to the right (clockwise) from the neutral position. Fig. Figure 5 is an explanatory diagram showing the positional relationship between the first torsion spring, the first arc groove and the second arc groove of the first shaft when the first shaft is rotated to the left (counterclockwise) from the neutral position. Fig. Figure 6 is a diagram showing an actuating force as a function of an actuating angle according to the first embodiment. Fig. Figure 7 is a longitudinal section of a steering actuation input device according to a second embodiment. Fig. Figure 8A is an explanatory illustration showing the steering actuation input device when a third shaft is rotated 180 degrees to the left from the neutral position. Fig. Figure 8B is an explanatory illustration showing the steering actuation input device when the third shaft is rotated 60 degrees to the left from the neutral position. Fig. Figure 8C is an explanatory illustration showing the steering actuation input device in the neutral position. Fig. Figure 9A is an explanatory illustration showing the steering actuation input device in a neutral position. Fig. Figure 9B is an explanatory illustration showing the steering actuation input device when the third shaft is rotated 60 degrees to the right from the neutral position. Fig. Figure 9C is an explanatory illustration showing the steering actuation input device when the third shaft is rotated 180 degrees to the right from the neutral position. Fig. Figure 10 is a diagram showing an actuating force as a function of an actuating angle according to a third embodiment. Embodiments for carrying out the invention

[0009] Embodiments of a steering actuation input device according to the present invention are described below with reference to the figures. The following embodiments describe examples in which the steering actuation input device is applied to a steer-by-wire steering system mounted on a vehicle. [First embodiment]

[0010] Fig. Figure 1 is a schematic diagram of a steering device of the "steer-by-wire" type to which a steering actuation input device of the present invention is applied.

[0011] The steering device of type “steer-by-wire” is configured such that the steering actuation input device described below, into which a steering actuation is input via a rotary knob 1, which is a steering actuation input element with which a driver performs a steering actuation, and a steering mechanism 3, which steers a pair of steered wheels 2 and 2, are mechanically separated from each other.

[0012] The rotary knob 1 is attached to an end section of a shaft 4, which is a column shaft arranged on the steering input device. It should be noted that instead of the rotary knob 1, another steering input element, such as a steering wheel, could also be attached to an end section of the shaft 4. An actuation angle sensor 6 for detecting an actuation angle (a steering angle) of the shaft 4 corresponding to the steering input by the driver is arranged on an outer circumferential section of the shaft 4. An actuation angle signal (a steering angle signal) detected by the actuation angle sensor 6 is transmitted to a control device 7. In addition, various other detection signals besides the steering angle signal are transmitted from an external sensor 8 to the control device 7.The control device 7 controls an electric motor 9 arranged on the steering mechanism 3 on the basis of the steering angle signal, the steering actuation angle signal mentioned below and various detection signals.

[0013] The steering mechanism 3 comprises a steering shaft 10, a pair of tie rods 11 and 11 connected to both ends of the steering shaft 10 and steering the pair of steered wheels 2 and 2, the electric motor 9 controlling a steering movement of the steering shaft 10 and a steering angle sensor 12 detecting a steering angle signal from the steering shaft 10. The steering angle signal detected by the steering angle sensor 12 is transmitted to the steering device 7.

[0014] Fig. Figure 2 is a longitudinal section of the steering actuation input device according to a first embodiment. Fig. For the sake of simplicity, the actuation angle sensor 6 has been omitted in section 2. Fig. Figure 3 is an explanatory diagram showing the positional relationship between a first torsion spring 16, a first arc groove 23, and a second arc groove 24 of a first shaft 19 in a neutral position, viewed from the axial direction of the first shaft 19. Fig. Figure 3 shows the first arc groove 23 and the second arc groove 24 as if these first and second grooves 23 and 24 were formed on the same plane, but in reality the first arc groove 23 is formed on an axial direction of an end surface 19h, while the second arc groove 24 is formed on an axial direction of another end surface 19i, which is located at a position that is displaced from the axial direction of an end surface 19h in the direction of the other end section side 19b of the first shaft 19. Fig. Figure 4 is an explanatory diagram showing the positional relationship between the first torsion spring 16, the first arc groove 23 and the second arc groove 24 of the first shaft 19 when the first shaft 19 is rotated to the right (clockwise) from the neutral position. Fig. Figure 5 is an explanatory diagram showing the positional relationship between the first torsion spring 16, the first arc groove 23 and the second arc groove 24 of the first shaft 19 when the first shaft 19 is rotated to the left (counterclockwise) from the neutral position. Fig. Figure 6 is a diagram showing an actuating force as a function of an actuating angle according to the first embodiment.

[0015] The steering actuation input device comprises the shaft 4, a coupling element 13, a coupling element cover 14, a housing 15, the first torsion spring (a first thrusting element) 16, a second torsion spring (a second thrusting element) 17 and a locking element 18.

[0016] Shaft 4 comprises the first shaft 19, to which an actuating force is transmitted from the rotary knob 1 and which rotates about a pivot axis O, and a second shaft 20, which is connected to the first shaft 19 via the coupling element 13 and the first torsion spring 16. For the sake of simplicity, the following description will be simplified as follows: Fig. 2 of the two end section sides 19a and 19b in the axial direction of the first shaft 19, the end section on the side on which the rotary knob 1 is attached is defined as “one end section side 19a”, while the end section on the side opposite the rotary knob 1 is defined as “the other end section side 19b”. Furthermore, in Fig. 3. A centerline passing through the axis of rotation O of the first wave 19 and dividing the first wave 19 into a right and a left half is defined as the “first centerline X1”. Furthermore, a centerline passing through the axis of rotation O of the first wave 19 and being orthogonal to the first centerline X1 is defined as the “second centerline X2”. It should be noted that a direction along the second centerline X2 in Fig. 3 with a right-left direction in Fig. 2 matches.

[0017] The shaft 4 has a first small-diameter section 19c, which is a shaft section located on an end section side 19a; a medium-diameter section 19d, which is integral with the first small-diameter section 19c and is a shaft section with a larger diameter than the first small-diameter section 19c; a large-diameter section 19e, which is integral with the medium-diameter section 19d and is a section of the shaft with a larger diameter than the medium-diameter section 19d; and a second small-diameter section 19f, which is integral with the large-diameter section 19e and is a section of the shaft with a smaller diameter than the large-diameter section 19e.

[0018] A D-shaped cutout 19g for engaging with the dial 1 is formed on an outer circumferential section at an end section side 19a of the first small-diameter section 19c. The D-shaped cutout 19g is attached to the rotary knob 1, for example, by a known wedge connection. A first bearing 21, which is a bearing for rotatably supporting the first small-diameter section 19c, is arranged on an outer circumferential section of an axial central section of the first small-diameter section 19c. Furthermore, a second bearing 22, which is a bearing for rotatably supporting the first small-diameter section 19c, is arranged on an outer circumferential section of an axial end section located on the other end section side 19b of the first small-diameter section 19c.

[0019] The large-diameter section 19e is a shaft section around which the first torsion spring 16 is attached. The outer diameter of the large-diameter section 19e is smaller than the inner diameter of the first torsion spring 16 when the first torsion spring 16 is maximally twisted and compressed. As shown in Fig. As shown in Figure 2, the large diameter section 19e has an axial direction of an end surface 19h located on one end section side 19a and is an annular continuous surface, and an axial direction of another end surface 19i located on the other end section side 19b and is an annular continuous surface.

[0020] The first arc groove 23, which has an arc shape concentric to the outer circumference of the first shaft 19, is formed at a position closer to an outer circumferential section on the axial direction of an end surface 19h on a side on which the D-shaped cutout 19g of the first small-diameter section 19c of the first shaft 19 is located. As in Fig. As shown in Figure 3, the first arc groove 23 is positioned on the left side with respect to the first center line X1 and extends in an arc shape from the second center line X2 at a predetermined angle, in the present embodiment 180 degrees, counterclockwise. It should be noted that the first arc groove 23 could be configured to continue in an arc shape at any angle other than 180 degrees. The first arc groove 23 has a first groove end 23a adjacent to the second center line X2 and a second groove end (not shown) located on the opposite side of the first groove end 23a. As shown in Figure 3, the first arc groove 23 has a first groove end 23a adjacent to the second center line X2 and a second groove end (not shown) located on the opposite side of the first groove end 23a. Fig. Figure 3 shows that in a neutral state of the first torsion spring 16, a first curved section 16e of a first spring end section 16b, both of which will be described later, of the first torsion spring 16 is located at the first groove end 23a of the first curved groove 23.

[0021] On the other hand, the second arc groove 24, which has an arc shape concentric to the outer circumference of the first shaft 19 and has the same shape as the first arc groove 23, is formed at a position closer to an axial, other end surface 19i on the outer circumferential surface and runs diagonally to the first arc groove 23 across the axis of rotation O of the first shaft 19. As in Fig. As shown in Figure 3, the second arc groove 24 is positioned on the right side with respect to the first center line X1 and extends clockwise in an arc shape from the second center line X2 at a predetermined angle, in the present embodiment 180 degrees. It should be noted that the second arc groove 24 could be configured to continue in an arc shape at any angle other than 180 degrees. The second arc groove 24 has a third groove end 24a adjacent to the second center line X2 and a fourth groove end (not shown) located on the opposite side of the third groove end 24a. As shown in Figure 3, the second arc groove 24 has a third groove end 24a adjacent to the second center line X2 and a fourth groove end (not shown) located on the opposite side of the third groove end 24a. Fig. As shown in Figure 3, in the neutral state of the first torsion spring 16, a second curved section 16g of a second spring end section 16c, both of which will be described later, is located at the third groove end 24a of the second curved groove 24 of the first torsion spring 16.

[0022] A third bearing 25, which is a bearing for rotatably supporting the second small-diameter section 19f, is arranged on an outer circumferential section of the second small-diameter section 19f. The second small-diameter section 19f has a section with a stepped-reduced diameter 19j, which is formed by shaping a tip section of the second small-diameter section 19f into a reduced-diameter shape. A fourth ball bearing 26, which is a bearing for rotatably supporting the section with the stepped-reduced diameter 19j, is arranged on an outer circumferential section of the section with the stepped-reduced diameter 19j.

[0023] The second shaft 20 is cylindrical and has a larger outer diameter than the large-diameter section 19e of the first shaft 19. The second shaft 20 has a circular first through-hole 20a in its central region. The small-diameter tubular section 13a of the coupling element 13, as described below, is then inserted into the first through-hole 20a, with the small-diameter section 19c of the first shaft 19 penetrating into the small-diameter tubular section 13a. The second shaft 20 has an axially oriented end surface 20b, located on one end side 19a, which is an annular, continuous surface, and an axially oriented end surface 20c, located on the other end side 19b, which is an annular, continuous surface.

[0024] A third arc groove 27, with an arc shape concentric to the outer circumference of the second shaft 20, is formed at a position closer to an outer circumferential surface in the axial direction of an end-side surface 20b of the second shaft 20. The third arc groove 27 has the same shape as the first arc groove 23, but is arranged in a radial position to the first shaft 19 in an outer position with respect to the first arc groove 23. It should be noted that the positional relationship between the third arc groove 27 and a third projection 36 mentioned below, when the second torsion spring 17 is in a neutral position, is the same as the positional relationship (one in Fig. 3 positional relationship shown) between the first arc groove 23 and a first projection 30 mentioned below, when the first torsion spring 16 is in a neutral position.

[0025] Furthermore, a fourth arc groove 28, having an arc shape concentric to the outer circumference of the second shaft 20, is formed at a position closer to an axial end circumferential surface on the other end 20c of the second shaft 20, on a side opposite the side on which the D-shaped cutout 19g of the first small-diameter section 19c of the first shaft 19 is located. The fourth arc groove 28 has the same shape as the second arc groove 24, but is arranged radially to the first shaft 19 at an outer position relative to the second arc groove 24. It should be noted that the positional relationship between the fourth arc groove 28 and a fourth projection 35 mentioned below, when the second torsion spring 17 is in the neutral position, is the same as the positional relationship (one in Fig. 3 positional relationship shown) between the second arc groove 24 and a second projection 32 mentioned below, when the first torsion spring 16 is in the neutral position.

[0026] The coupling element 13 is cylindrically shaped and made of a metal or plastic material. The coupling element 13 comprises a small-diameter tubular section 13a, a large-diameter tubular section 13b, and a connecting element 13c that joins the small-diameter tubular section 13a and the large-diameter tubular section 13b. The first small-diameter section 13c of the first shaft 19 penetrates a space within an inner circumferential surface of the small-diameter tubular section 13a. The inner circumferential surface of the small-diameter tubular section 13a is separated from an outer circumferential surface of the first small-diameter section 13c by a small gap.A D-shaped cutout (not shown) is formed on an outer circumferential surface of the small-diameter tubular section 13a, and the D-shaped cutout is attached to the first through-hole 20a of the second shaft 20 via a known wedge connection. Instead of the known wedge connection, a known screw connection could also be used to attach the first through-hole 20a of the second shaft 20 to the D-shaped cutout of the small-diameter tubular section 13a. Alternatively, the first through-hole 20a of the second shaft 20 can be attached to the small-diameter tubular section 13a via a keyway section instead of the D-shaped cutout.

[0027] The large-diameter tubular section 13b has a cylindrical shape with a larger diameter than the small-diameter tubular section 13a. The medium-diameter section 19d, the large-diameter section 19e, part of the second small-diameter section 19f of the first shaft 19, and the first torsion spring 16 are housed within the large-diameter tubular section 13b. An axial end section on one end section side 19a of the large-diameter tubular section 13b is connected via the connecting device 13c to an axial end section on the other end section side 19b of the small-diameter tubular section 13a. Conversely, another axial end section on the other end section side 19b of the large-diameter tubular section 13b is covered by the coupling element cover 14.

[0028] The connecting device 13c has an annular first annular extension section 13d, which extends radially outwards from an outer circumference of the small-diameter tubular section 13a in the direction of the first shaft 19; a tubular projection 13e, which has a tubular shape and projects from a radial end section of the first annular extension section 13d to the other end section side 19b; and an annular second annular extension section 13f, which extends radially outwards from an outer circumferential section of the tubular projection 13e in the direction of the first shaft 19. A space within an inner circumferential surface of the tubular projection 13e is a first bearing receiving section 29, which receives the second ball bearing 22, which is the bearing for the rotatable support of the first small-diameter section 19c.In a state in which the second bearing 22 is received in the first bearing receiving section 29, an end surface 22b on the other end section side 19b of an inner ring 22a of the second bearing 22 abuts an end surface 19k on an end section side 19a of the section with medium diameter 19d.

[0029] On a surface 13g on the other end section side 19b of the second annular extension section 13f at a position near the first arc groove 23 of the section 19e with large diameter of the first wave 19 a first projection 30 (in Fig. 2 (shown by a solid line and a dashed line) is designed so that it projects in the direction of section 19e with a large diameter. More precisely, as shown in Fig. Figure 3 shows the first projection 30 arranged in an area located on the left side with respect to the first center line X1 and on the top side with respect to the second center line X2, and is positioned adjacent to the second center line X2. When the first torsion spring 16 is in the neutral position, as shown in Fig. As shown in Figure 3, the first projection 30 borders the first groove end 23a of the first arc groove 23. The width of the first projection 30 along the radial direction of the first shaft 19 is greater than the width of the first arc groove 23 along the radial direction of the first shaft 19. The first projection 30 has a first flat surface 30a along the second center line X2, a second flat surface 30b on a side opposite the first flat surface 30a in the circumferential direction of the first shaft 19, a first arc surface 30c connecting the inner end sections of the first flat surface 30a and the second flat surface 30b, and a second arc surface 30d connecting the outer end sections of the first flat surface 30a and the second flat surface 30b.The first projection 30 is constructed in such a way that a first inclined section 16d of the first spring end section 16b, both of which will be described later, of the first torsion spring 16 can abut the first flat surface 30a of the first projection 30.

[0030] The coupling element cover 14 is made of metal or plastic in the form of a disc. A second through-hole 14a is formed in a central section of the coupling element cover 14 such that it penetrates the coupling element cover 14 along the axial direction of the first shaft 19. The second through-hole 14a extends from one end section side 19a to the other end section side 19b via an annularly continuous stepped section 14b in a form with a stepped diameter. A space on one end section side 19a with respect to the stepped section 14b of the second through-hole section 14a is a second bearing section 31, which accommodates the third bearing 25, which is the bearing for the rotatable support of the second, small-diameter section 19f of the first shaft 19.Furthermore, an annular continuous step 14c is formed on an outer edge section on one end section side 19a of the coupling element cover 14, and the axially oriented other end section on the other end section side 19b of the large-diameter tubular section 13b of the coupling element 13 is received in this step 14c. The other end section is then axially attached to the step 14c on the other end section side 19b of the large-diameter tubular section 13b. A surface located on the other end section side 19b of the coupling element cover 14 and facing the closure element 18 is separated from a surface 18b on an end section side 19a of the closure element 18 by a small gap.

[0031] On a surface 14d on an end section side 19a of the coupling element cover 14, at a position near the second arc groove 24 of the large diameter section 19e of the first shaft 19, the second projection 32 (in Fig. 2 (shown by a solid line and a dashed line) is designed so that it projects towards the large-diameter section 19e. More precisely, as shown in Fig. As shown in Figure 3, the second projection 32 is arranged in an area to the right of the first center line X1 and also above the second center line X2, and is located in a position adjacent to the second center line X2. When the first torsion spring 16 is in the Fig. In the neutral position shown in Figure 3, the second projection 32 borders the third groove end 24a of the second arc groove 24. The second projection 32 has a similar shape to the first projection 30. The width of the second projection 32 along the radial direction of the first shaft 19 is greater than the width of the second arc groove 24 along the radial direction of the first shaft 19. The second projection 32 has a third flat surface 32a along the second center line X2, a fourth flat surface 32b on a side opposite the third flat surface 32a in the circumferential direction of the first shaft 19, a third arc surface 32c connecting the inner end sections of the third flat surface 32a and the fourth flat surface 32b, and a fourth arc surface 32d connecting the outer end sections of the third flat surface 32a and the fourth flat surface 32b.The second projection 32 is constructed in such a way that a second inclined section 16f of the second spring end section 16c, both of which will be described later, can abut the third flat surface 32a of the second projection 32 of the first torsion spring 16.

[0032] The housing 15 comprises a first housing 33, which is located on the other end section side 19b, and a second housing 34, which is located on an end section side 19a.

[0033] The first housing 33 is formed from a metal or plastic material into a tubular shape with a base. The first housing 33 accommodates within it a section of the first shaft 19 on the other end section side 19b with respect to the second bearing 22, a part of the connecting device 13c, the large-diameter tubular section 13b of the coupling element 13, the first torsion spring 16, and the coupling element cover 14. The first housing 33 has a circular, plate-shaped base wall section 33a and a cylindrical circumferential wall section 33b extending from an outer circumferential edge section of the base wall section 33a to the other end section side 19b. A third through-hole 33c is formed in a central section of the base wall section 33a, such that it penetrates the base wall section 33a along the axial direction of the first shaft 19.The connecting device 13c of the coupling element 13 is inserted into the third through-hole 33c, with the first small-diameter section 19c of the first shaft 19 penetrating the connecting device 13c. An inner circumferential surface of the third through-hole 33c is separated from an outer circumferential surface of the connecting device 13c. On a surface 33d at an end section side 19a of the bottom wall 33a, at a position near the fourth arc groove 28 of the second shaft 20, the fourth projection 35 (in . . Fig. 2 (shown by a solid line and a dashed line) is designed so that it protrudes in the direction of the second wave 20.

[0034] The second housing 34 is formed from a metal or plastic material in a tubular shape with a base. The second housing 34 accommodates part of the first small-diameter section 19c of the first shaft 19, the small-diameter tubular section 13a of the coupling element 13, the second shaft 20, and the second torsion spring 17. The second housing 34 has a base wall section 34a, a cylindrical circumferential wall section 34b extending from an outer circumferential edge section of the base wall section 34a to the other end section side 19b, and a cylindrical extension section 34c extending from a central section of the base wall section 34a to the side of the rotary knob 1. On a surface 34d on the other end section side 19b of the base wall section 34a, at a position near the third arc groove 27 of the second shaft 20, the third projection 36 (in Fig. 2 (shown by a solid line and a dashed line) is designed such that it projects towards the second shaft 20. Furthermore, an annular flange section 34e, projecting outwards in the radial direction of the first shaft 19, is formed at an axial end section on the other end section side 19b of the circumferential wall section 34b. This flange section 34e is attached to and fastened to the bottom wall section 33a of the first housing 33 by means of a fastening element (not shown), e.g., a bolt.

[0035] A fourth hole section 34f is formed in the bottom wall section 34a and the extension section 34c, such that it penetrates the bottom wall section 34a and the extension section 34c in the axial direction of the first shaft 19. The first small-diameter section 19c of the first shaft 19 is inserted into the fourth hole section 34f. Furthermore, a third bearing section 37, which is a circular recessed section extending from the surface 34d of the bottom wall section 34a to an end section side 19a, is formed in the bottom wall section 34a and a part of the extension section 34c. The third bearing receiving section 37 receives the first bearing 21, which rotatably supports the first small-diameter section 19c of the first shaft 19.An annular, continuous groove section 34g is formed at a position on a first end section side 19a with respect to the first bearing 21 on an inner circumferential surface of the extension section 34c. The annular groove section 34g is provided with an O-ring 38 as a sealing element. The O-ring 38 seals a gap between the inner circumferential surface of the extension section 34c of the second housing 34 and the outer circumferential surface of the first section 19c with a small diameter of the first shaft 19. The O-ring 38 causes a feeling of viscosity to arise at the beginning of the rotation of the rotary knob 1 due to friction with the first shaft 19, and the driver can perceive the actuation of the rotary knob 1 through this viscous sensation.As long as the sealing element seals the gap between the inner circumferential surface of the extension section 34c of the second housing 34 and the outer circumferential surface of the first small-diameter section 19c of the first shaft 19, the sealing element is not limited to the O-ring 38. For example, an oil seal or a dust seal could be provided. Furthermore, the oil seal or the dust seal could be provided together with the O-ring 38.

[0036] The first torsion spring 16 is a linear spring that is attached to the large-diameter section 19e of the first shaft 19 via the first arc groove 23 and the second arc groove 24 of the first shaft 19 in a state where no preload is applied to the spring. The first torsion spring 16 has a helical section 16a formed by helically winding a long, thin, cylindrical, columnar metal element, as well as the hook-shaped first spring end section 16b, which is one end section of the helical section 16a, and the hook-shaped second spring end section 16c, which is the other end section of the helical section 16a. The first torsion spring 16 is arranged such that the large-diameter section 19e of the first shaft 19 is inserted into the helical section 16a. As shown in Fig. As shown in Figure 2, the first spring end section 16b has the first inclined section 16d, which is inclined from an axial direction at one end of the spiral section 16a to the side of the first arc groove 23 of the first shaft 19, and the first curved section 16e, which is bent from a tip section of the first inclined section 16d to the inside of the first arc groove 23. The second spring end section 16c has the same shape as the first spring end section 16b. The second spring end section 16c has a second inclined section 16f, which is inclined from an axial direction of the other end of the spiral section 16a to the side of the second arc groove 24 of the first shaft 19, and a second curved section 16g, which is bent from a tip section of the second inclined section 16f to the inside of the second arc groove 24.

[0037] A reaction force due to the torsion of the first torsion spring 16 is generated by a force in the Fig. The position switching mechanism 39 shown in Figures 3 to 5 is generated. The position switching mechanism 39 comprises the first arc groove 23 and the second arc groove 24 of the first shaft 19, the first curved section 16e and the second curved section 16g, which are respectively inserted into the first arc groove 23 and the second arc groove 24 of the first torsion spring 16, the first projection 30 of the coupling element 13, and the second projection 32 of the coupling element cover 14. The position switching mechanism 39 switches between an unfixed position and a fixed position of the first spring end section 16b or the second spring end section 16c on the first shaft 19 when the first shaft 19 is rotated by and according to the actuation of the rotary knob 1.This means that the position switching mechanism 39 switches the position of either the first curved section 16e, which is inserted into the first curved groove 23, or the second curved section 16g, which is inserted into the second curved groove 24, from the fixed position to the unfixed position, according to the direction of rotation of the first shaft 19. Through this position switching mechanism 39, the first torsion spring 16 exerts a penetrating force on the first shaft 19, regardless of the direction of rotation of the first shaft 19. That is, through the position switching mechanism 39, the first torsion spring 16 exerts the penetrating force on the first shaft 19 for both clockwise and counterclockwise rotation of the first shaft 19.

[0038] As in Fig. As shown in Figure 3, when the first torsion spring 16 is in the neutral position, the position-switching mechanism 39 fixes both the first curved section 16e and the second curved section 16g of the first torsion spring 16 in a fixed position. More precisely, the first inclined section 16d, which is integral with the first curved section 16e of the first spring end section 16b, abuts the first flat surface 30a of the first projection 30 of the coupling element 13, thereby fixing the position of the first curved section 16e. Conversely, the second inclined section 16f, which is integral with the second curved section 16g of the second spring end section 16c, abuts the third flat surface 32a of the second projection 32 of the coupling element cover 14, thereby fixing the position of the second curved section 16g.It should be noted that the above-mentioned “neutral position” is a neutral position in which the rotary knob 1 is neither rotated to the right (right-hand drive) nor to the left (left-hand drive) with respect to a direction of travel of a vehicle and thus the first torsion spring 16 is neither rotated to the right nor to the left.

[0039] When the first shaft 19 rotates to the right in accordance with the clockwise rotation of the rotary knob 1 (clockwise rotation in the Fig. 3), as in Fig. As shown in Figure 4, while the first inclined section 16d remains in contact with the first flat surface 30a of the first projection 30, the second curved section 16g is pressed by the third groove end 24a of the second arc groove 24, which rotates to the right, and then rotated into the unfixed position, i.e., a position outside the third flat surface 32a of the second projection 32 in the direction of rotation to the right. This generates a reaction force (the pushing force) in the left direction of rotation, which is opposite to the right direction of rotation of the first shaft 19.

[0040] If, on the other hand, the first shaft 19 rotates to the left in accordance with the leftward rotation of the rotary knob 1 (in Fig. 3 clockwise), as in Fig. As shown in Figure 5, while the second curved section 16g remains in contact with the third flat surface 32a of the second projection 32, the first curved section 16e is pressed by the first groove end 23a of the first curved groove 23, which rotates to the left, and then rotated into the unfixed position, i.e., a position outside the first flat surface 30a of the first projection 30 in the direction of rotation to the left. This generates a reaction force (the pushing force) in the right direction of rotation, which is opposite to the left direction of rotation of the first shaft 19.

[0041] When the first torsion spring 16, as described above, reaches a predetermined load due to the rotation of the first shaft 19, the coupling element 13 begins to rotate in the same direction as the direction of rotation of the first shaft 19, either against the stop of the first inclined section 16d on the first projection 30 or against the stop of the second inclined section 16f on the second projection 32. Here, the "predetermined load" is a load generated by a preload set in (or exerted upon) the second torsion spring 17. As in Fig. As shown in Figure 6, in the present embodiment the predetermined load is set to approximately 0.17 Nm, and this is set such that the first torsion spring 16 reaches 0.17 Nm when the rotary knob 1 is turned at an angle of 60 degrees. Due to the rotation of the coupling element 13, the second shaft 20, which is attached to the outer circumference of the coupling element 13, also begins to rotate. At this point, the first shaft 19 continues to rotate even after the second shaft 20 has rotated. Then, even after the second torsion spring 17 applies a compressive force to the second shaft 20, the first torsion spring 16 continues to exert a compressive force on the first shaft 19.It should be noted that instead of the configuration of the first torsion spring 16 and the second torsion spring 17 described above, a configuration could also be used in which, even if the rotation of the first torsion spring 16, which exerts the pushing force on the first shaft 19, stops due to the rotation of the rotary knob 1, the pushing force is exerted on the shaft 4 only by the second torsion spring 17 by means of a switching device (not shown), i.e. a configuration in which, after the pushing force for the first shaft 19 has been provided by the first torsion spring 16, the pushing force for the second shaft 20 is provided by the second torsion spring 17.

[0042] The second torsion spring 17 has the same spring constant as the first torsion spring 16. The second torsion spring 17 is a linear spring that is attached to the second shaft 20 via the third arc groove 27 and the fourth arc groove 28 of the second shaft 20 in a state where a preload is applied to the spring. The second torsion spring 17 has a helical section 17a formed by helically winding a long, thin, cylindrical, columnar metal element, a third spring end section 17b which is one end section of the helical section 17a, and a fourth spring end section 17c which is the other end section of the helical section 17a. The second torsion spring 17 is arranged such that the second shaft 20 is inserted into the helical section 17a. As shown in Fig. As shown in Figure 2, the third spring end section 17b has a third inclined section 17d, inclined from an axial direction of one end of the spiral section 17a towards the side of the third arc groove 27 of the second shaft 20, and a third curved section 17e, bent from a tip section of the third inclined section 17d towards the inside of the third arc groove 27. The fourth spring end section 17c has the same shape as the third spring end section 17b. The fourth spring end section 17c has a fourth inclined section 17f, inclined from an axial direction of the other end of the spiral section 17a towards the fourth arc groove 28 of the second shaft 20, and a fourth curved section 17g, bent from a tip section of the fourth inclined section 17f towards the inside of the fourth arc groove 28.A reaction force due to the torsion of the second torsion spring 17 is generated by a position-switching mechanism similar to the position-switching mechanism 39 applied to the first torsion spring 16. The position-switching mechanism applied to the second torsion spring 17 comprises the third arc groove 27 and the fourth arc groove 28 of the second shaft 20, the third curved section 17e and the fourth curved section 17g, respectively, inserted into the third arc groove 27 and the fourth arc groove 28 of the second torsion spring 17, the third projection 36 of the second housing 34, and the fourth projection 35 of the first housing 33. The position-switching mechanism switches between an unfixed position and a fixed position of the third spring end section 17b or the fourth spring end section 17c on the second shaft 20 as the second shaft 20 is rotated by and in accordance with the rotation of the first shaft 19.That is, the position switching mechanism switches the position of the third curved section 17e, which is inserted into the third curved groove 27, or of the fourth curved section 17g, which is inserted into the fourth curved groove 28, from a fixed position to a non-fixed position, according to a direction of rotation of the second shaft 20. The operation of the position switching mechanism for the second torsion spring 17 is the same as the operation of the position switching mechanism 39 for the first torsion spring 16, i.e., that described above with reference to the... Fig. 4 and Fig. 5 described switching mechanism. Through the position switching mechanism for the second torsion spring 17, the second torsion spring 17 exerts a pushing force on the second shaft 20, independent of the direction of rotation of the second shaft 20.

[0043] Furthermore, a rotary damper mechanism (not shown), which is a damping mechanism that exerts a damping force on the first torsion spring 16 via the first shaft 19, can be arranged at any position on the first shaft 19. This reduces the rotational speed of the first shaft 19, thereby reducing the rate at which the first torsion spring 16 twists and exerting the damping force on the first torsion spring 16. This rotary damper mechanism is a known rotary damper mechanism that utilizes the viscous resistance of oil and comprises a housing, a rotor contained within the housing along with oil, and a cap with a through-hole for the shaft section through which a shaft section of the rotor protrudes and which covers the housing.To increase the rotational speed of the first shaft 19 (to rotate it further), the oil can be throttled back, and to rotate the first shaft 19 in one direction of rotation and then to rotate the first shaft 19 in the other direction of rotation (to rotate it back), the oil can be diverted via a flow channel arranged in the rotary damper mechanism.

[0044] Here, with reference to Fig. 6 The two-stage spring characteristic (double spring characteristic) is described using the first torsion spring 16 and the second torsion spring 17. First, the spring constant of the first torsion spring 16 is defined as “K1” and the spring constant of the second torsion spring 17 as “K2”. As in Fig. As shown in Figure 6, at an actuation angle of 0 degrees to less than 60 degrees (in the small steering angle range), only the compressive force of the first torsion spring 16 acts on the shaft 4. Therefore, an actuation force exerted on the shaft 4 increases linearly with respect to a reaction force based on the spring constant K1 (an actuation force amplification K1). When the actuation angle reaches 60 degrees and the actuation force reaches the predetermined load, approximately 0.17 Nm in the present embodiment, the compressive force of the second torsion spring 17 also acts in addition to the compressive force of the first torsion spring 16. Therefore, a resultant spring constant (a combined spring constant) K, obtained by considering the first torsion spring 16 and the second torsion spring 17 as connected in series, can be obtained from the equation "1 / K = 1 / K1 + 1 / K2".As described above, since the spring constant of the first torsion spring 16 and the spring constant of the second torsion spring 17 are equal in the present embodiment, the equation “1 / K = 2 / K1” applies, and this equation yields “K = K1 / 2” when rearranged. Therefore, in the present embodiment, in a range where the actuation angle is between 60 degrees and 180 degrees (in a large steering angle range), the actuating force exerted on the shaft 4 increases linearly to a reaction force based on the resulting spring constant K1 / 2 (an actuating force amplification factor K1 / 2). That is, as in . Fig. As shown in Figure 6, the actuating force in the large steering angle range increases linearly at half the rate of increase of the actuating force in the small steering angle range. Therefore, the rotary knob 1 is actuated with half the force in the large steering angle range compared to the actuating force in the small steering angle range. Here, the present embodiment illustrates a case in which the spring constant of the first torsion spring 16 and the spring constant of the second torsion spring 17 are the same. However, different spring constants could also be used according to the desired reaction force characteristics.

[0045] The locking element 18 is made of a metal or plastic material in the form of a disc. An axial counter-end section on the other end section side 19b of the first housing 33 is attached to an end section side 19a of the locking element 18. A fourth bearing section 40 is formed on a central section on a surface 18b, an end section side 19a of the locking element 18, which is recessed from surface 18b to the other end section side 19b. The fourth bearing 40 accommodates the fourth ball bearing 26, which rotatably supports the section with a reduced diameter step 19j, which is arranged on the second small-diameter section 19f.

[0046] The present embodiment illustrates a case in which the first torsion spring 16 is attached to the large-diameter section 19e of the first shaft 19 via the first arc groove 23 and the second arc groove 24 of the first shaft 19 in a state where no preload is exerted on the spring. However, considering the friction generated between the first shaft 19 and the sealing element located on the annular groove section 34g, the first torsion spring 16 could be attached to the large-diameter section 19e of the first shaft 19 with a preload corresponding to the torque caused by the friction exerted on the first torsion spring 16. If the friction generated between the first shaft 19 and the sealing element (the feeling of viscosity) is caused by the sealing element, the first torsion spring 16 may have difficulty returning to its neutral position.By applying a preload corresponding to the torque caused by friction, it is therefore possible to prevent the first torsion spring 16 from having difficulty returning to the neutral position. This improves the driver's feel (steering feel) when turning the control knob. [Effects of the first embodiment]

[0047] As described above, in the first embodiment, the first torsion spring 16 generates a pushing force in the opposite direction to the rotation of the first shaft 19, regardless of the direction of rotation of the first shaft 19. That is, when the first shaft 19 rotates to the right, the first torsion spring 16 exerts a pushing force in the left direction of rotation on the first shaft 19, while when the first shaft 19 rotates to the left, the first torsion spring 16 exerts a pushing force in the right direction of rotation on the first shaft 19. More precisely, in contrast to the prior art, in which springs are arranged as special pushing elements to exert the pushing force (the reaction force) against each of the rotation directions of the shaft, in the present embodiment the common first torsion spring 16 is arranged, which generates the pushing force for both rotation directions.Since the number of springs is thus reduced compared to the state of the art, it is possible to lower the manufacturing costs of the steering actuation input device.

[0048] Furthermore, in the prior art, a single spring is arranged to exert the penetrating force for clockwise rotation of the shaft, and another single spring is arranged to exert the penetrating force for counterclockwise rotation of the shaft. Consequently, the problem arises that the penetrating force differs between clockwise and counterclockwise rotation of the shaft.

[0049] In contrast, in the present embodiment, since the common first torsion spring 16 exerts the pushing force during both right-hand and left-hand rotation of the first shaft 19, the difference in the pushing force between right-hand and left-hand rotation can be eliminated.

[0050] Furthermore, in the prior art, the switching of the springs between right-hand and left-hand rotation of the shaft is carried out via the linear motion conversion device, which converts the rotational force input by the steering actuation input element into a linear motion.

[0051] However, since in the present embodiment the common first torsion spring 16 exerts the thrust force on both rotations of the first shaft 19, a linear motion conversion device as in the prior art is not required in the present embodiment. Therefore, compared to the prior art, it is possible to reduce the manufacturing costs and assembly time of the steering actuation input device by the amount of a linear motion conversion mechanism.

[0052] Furthermore, in the present embodiment, a configuration can be used in which, after the first torsion spring 16 exerts the compressive force on the first shaft 19, the second torsion spring 17 exerts the compressive force on the second shaft 20. In this case, even if the rotation of the first torsion spring 16, which exerts the compressive force on the first shaft 19, stops, the switching device ensures that the compressive force is exerted on the shaft 4 only by the second torsion spring 17. Therefore, even if the first torsion spring 16 fails, the compressive force is exerted on the shaft 4 by the second torsion spring 17, thus continuing the operation of the steering actuation input device.

[0053] Furthermore, in the present embodiment, the first torsion spring 16 continues to exert pressure on the first shaft 19 even after the second torsion spring 17 has applied the compressive force to the second shaft 20. In this case, a switching device with the configuration described above, in which the compressive force is applied to the first shaft 19 by the first torsion spring 16 and the compressive force is then applied to the second shaft 20 by the second torsion spring 17, is not required, thus making the steering actuation input device simpler to manufacture than the configuration described above.

[0054] In addition, the steering actuation input device in the present embodiment has a position switching mechanism 39 which, upon rotation of the first shaft 19, switches between the unfixed position and the fixed position of the first curved section 16e of the first spring end section 16b or the second curved section 16g of the second spring end section 16c of the first torsion spring 16. Therefore, it is only by switching the position of the first curved section 16e or the second curved section 16g according to the rotation of the first shaft 19 that it is possible to easily provide the thrust force in the direction opposite to the rotation of the first shaft 19, without having to move a linear motion element over a relatively long distance through the linear motion conversion mechanism as in the prior art.Furthermore, in the prior art, a load acts on the shaft due to the springs and the linear motion conversion mechanism. In the present embodiment, however, only a load from the first torsion spring 16 and the second torsion spring 17 acts on the first shaft 19, etc.

[0055] Therefore, the load on the steering actuation input device can be reduced.

[0056] Furthermore, in the prior art, two coil springs are arranged along the axial direction of the shaft, whereupon the linear motion conversion mechanism is provided. Additionally, in the prior art, it is necessary to design the steering actuation input device taking into account the stroke of each coil spring along the axial direction of the shaft. Consequently, the steering actuation input device tends to increase in size.

[0057] In the present embodiment, however, the first torsion spring 16 and the second torsion spring 17 are used as compression elements. Since the extension of the first torsion spring 16 and the second torsion spring 17 after their deformation is relatively small, and each spring generates the compression force only by twisting in the circumferential direction of the spring, the size (dimension) of the steering actuation input device along the axial direction of the first shaft 19 can be reduced compared to the prior art.

[0058] To shorten the axial dimension of the steering actuation input device, a possible configuration is to arrange two coil springs in series and to place the linear motion conversion mechanism on a radially outer side of these coil springs (see Fig. 7) However, since the present embodiment does not require a linear motion conversion mechanism compared to a steering actuation input device described later according to a second embodiment, a reduction in the size of the steering actuation input device along the radial direction of the first shaft 19 can be achieved.

[0059] In the present embodiment, the shaft 4 comprises the first shaft 19, which is provided with the first torsion spring 16, and the second shaft 20, which is provided with the second torsion spring 17. Furthermore, the coupling element 13, which covers the first shaft 19 and the first torsion spring 16, is arranged on an outer surface radially to the first shaft 19. The coupling element 13 is connected to the first shaft 19 via the first torsion spring 16 and is also connected to the second shaft 20. When the first torsion spring 16 reaches the predetermined load, the coupling element 13 rotates. Due to and in accordance with this rotation of the coupling element 13, the second shaft 20 rotates, whereupon the second torsion spring 17 arranged on the second shaft 20 is twisted. For this reason, until the first torsion spring 16 reaches the predetermined load, only the pushing force based on the first torsion spring 16 is generated.Once the first torsion spring 16 has reached the specified load, the compressive force based on the first torsion spring 16 and the second torsion spring 17 is generated. This changes, as shown in . Fig. Figure 6 shows the actuation force of rotary knob 1 in two stages over an actuation angle of 60 degrees. That is, the actuation force increases at a predetermined rate (gradient) until the actuation angle reaches 60 degrees, and after 60 degrees, the actuation force increases at half the rate if the actuation angle is less than 60 degrees. Therefore, in the range with a large steering angle, where the actuation angle is 60 degrees or more, driver fatigue caused by steering can be reduced and a deterioration in the vehicle's handling (drivability or ride comfort) can be prevented.

[0060] Furthermore, in the present embodiment, the predetermined load is a load generated by the preload applied to the second torsion spring 17. Therefore, by changing the preload, it is possible to set a point at which the actuating force changes.

[0061] Furthermore, in the present embodiment, the outer diameter of the first shaft 19 is smaller than the inner diameter of the first torsion spring 16 when the first torsion spring 16 generates the compressive force and is deformed. This prevents damage to the first torsion spring 16 and the first shaft 19 caused by contact between the deformed first torsion spring 16 and an outer circumferential surface of the first shaft 19. It also prevents the rotation of the first shaft 19 from being stopped due to contact between the deformed first torsion spring 16 and the outer circumferential surface of the first shaft 19.

[0062] Furthermore, in the present embodiment, the D-shaped cutout is formed on the outer circumferential surface of the small-diameter tubular section 13a of the coupling element 13, and the coupling element 13 is attached to the first through-bore 20a of the second shaft 20 via the D-shaped cutout. Therefore, when assembling the second shaft 20 with the coupling element 13, the positioning of the second shaft 20, in particular the third arc groove 27, can be easily achieved through the D-shaped cutout.

[0063] Furthermore, in the present embodiment, the coupling element 13 and the second shaft 20 can be fastened to one another via the keyway section. In this case, the coupling element 13 and the second shaft 20 can be firmly fastened to one another even when a high torque is generated on the coupling element 13.

[0064] In addition, in the present embodiment, the annular groove section 34g of the second housing 34 is provided with the O-ring 38 as a sealing element. The O-ring 38 seals the gap between the inner circumferential surface of the expansion section 34c of the second housing 34 and the outer circumferential surface of the first section 19c with a small diameter of the first shaft 19. Since the first shaft 19 rotates against a frictional force of the O-ring 38, a feeling of viscosity arises at the beginning of the rotation of the rotary knob 1. This can improve the operating feel (steering feel) of the rotary knob for the driver.

[0065] Furthermore, in the present embodiment, the damping mechanism, which exerts a damping force on the first torsion spring 16, can be arranged at any position on the first shaft 19. In this case, the compressive force of the first torsion spring 16 is dampened, thereby reducing the operating force of the rotary knob 1 by the driver and reducing driver fatigue. [Second embodiment]

[0066] Fig. Figure 7 is a longitudinal section of a steering actuation input device according to a second embodiment. Fig. Figure 7 shows the steering actuation input device in a neutral position.

[0067] The steering actuation input device of the second embodiment comprises a rotary / linear motion conversion unit 41, a housing 42, a connecting unit 43, a reaction force generation unit 44, a first closure cover element 45, a second closure cover element 46, a third closure cover element 47, and a fourth closure cover element 48. In this steering actuation input device, a rotary force exerted on a third shaft 49 described below is converted into a linear motion by the rotary / linear motion conversion unit 41, and this linear motion is transmitted via the connecting unit 43 to the reaction force generation unit 44. The reaction force generation unit 44 transmits the compressive forces of the first coil spring 81 and second coil spring 82 described below, which are exerted in response to the transmitted linear motion, via the connecting unit 43 to the rotary / linear motion conversion unit 41.

[0068] The rotary / linear motion conversion unit 41 comprises the third shaft 49 and a linear motion conversion mechanism 50, which is a ball screw mechanism arranged on an outer circumferential section of the third shaft 49.

[0069] The third shaft 49 comprises a first small-diameter cylindrical column section 49c located at an end section side 49a, a medium-diameter cylindrical column section 49d formed integrally with the first small-diameter cylindrical column section 49c and having a larger diameter than the first small-diameter cylindrical column section 49c, a large-diameter cylindrical column section 49e formed integrally with the medium-diameter cylindrical column section 49d and having a larger diameter than the medium-diameter cylindrical column section 49d, and a second small-diameter cylindrical column section 49f formed integrally with the large-diameter cylindrical column section 49e and having a smaller diameter than the large-diameter cylindrical column section 49e.A D-shaped cutout 49g for attachment to a rotary knob (not shown), through which steering input is received, is formed on the first small-diameter cylindrical column section 49c. A fifth bearing 51, which is a bearing for rotatably supporting the medium-diameter cylindrical column section 49d, and an O-ring 38 as a sealing element are arranged on an outer circumferential section of the medium-diameter cylindrical column section 49d. As in the first embodiment, the sealing element is not limited to the O-ring 38. For example, an oil seal or a dust seal could be arranged. Furthermore, the oil seal or the dust seal can be arranged together with the O-ring 38.The linear motion conversion mechanism 50, which converts a rotational force exerted by the rotary knob (not shown) on the third shaft 49 into a linear motion along an axial direction of the third shaft 49, is arranged on an outer circumferential section of the large-diameter cylindrical section 49e. The linear motion conversion mechanism 50 will be described in detail later. A sixth ball bearing 52, which is a bearing for the rotatable support of the second small-diameter cylindrical section 49f, is arranged on an outer circumferential section of the second small-diameter cylindrical section 49f.

[0070] The linear motion conversion mechanism 50 is configured by a shaft-side ball screw groove 49h, which is a helical groove formed on an outer circumferential surface of the large-diameter cylindrical column section 49e of the third shaft 49, a nut-side ball screw groove 53a, which is a helical groove formed on an inner circumferential surface of a nut 53, which is a linear motion element, several balls 54 arranged between the ball screw spiral grooves 49h and 53a, a limiting element 55 that limits the rotation of the nut 53 in a rotational direction of the third shaft 49 and allows movement of the nut 53 along the axial direction of the third shaft 49, and a cap element 56 that holds the nut 53 against the limiting element 55. The balls 54 support the nut 53 rotatably relative to the large-diameter cylindrical section 49e of the third shaft 49.The nut 53 has an annular projecting section 53b that projects radially outward from a circumferential surface of the nut 53. The annular projecting section 53b is located closer to an axial end section on one end section side 49a of the nut 53. The limiting element 55 is formed as a cylindrical tube with a base and is arranged in a position in which a base section 55a is located on another end section side 49b. A limiting element through-hole 55b is formed in the base section 55a of the limiting element 55, which penetrates the base of the limiting element 55 along the axial direction of the third shaft 49. The large-diameter cylindrical column section 49e of the third shaft 49 is inserted into the limiting element through-hole 55b.The limiting element 55 is attached to the nut 53, with an axial end section 55c on one end section side 49a of the limiting element 55 bearing against a first contact surface 53b on the other end section side 49b of the annular projecting section 53b of the nut 53. The limiting element 55 is configured to move frictionlessly along the axial direction of the third shaft 49 by means of a guide rail (not shown) arranged on a housing section 57, described later, on the side of the conversion unit.

[0071] The cap element 56 is designed as a cylindrical tube with a base, shorter than the limiting element 55, and is arranged in a position in which a base section 56a is located on one end section 49a. A through-hole 56b is formed in the base section 56a of the cap element 56, which penetrates the base of the cap element 56 in the axial direction of the third shaft 49. The large-diameter cylindrical column section 49e of the third shaft 49 is inserted into the through-hole 56b of the cap element. Additionally, an internally threaded section (not shown) is arranged on an inner circumferential surface of the cap element 56. This internally threaded section engages an externally threaded section (not shown) located on the outer circumferential surface of the nut 53, thereby pressing the annular projecting section 53b of the nut 53 against the axial end 55c of the limiting element 55.

[0072] Instead of the linear motion conversion mechanism 50 described above, which is a ball screw mechanism, a linear motion conversion mechanism based on thread engagement can also be used in the steering actuation input device of the present embodiment.In this case, the linear motion conversion mechanism comprises a helical first uneven section (an external thread section) formed on an outer circumferential surface of the third shaft 49, a nut as a movable element having a helical second uneven section (an internal thread section) engaging with the first uneven section and movable in the axial direction of the third shaft 49 according to a rotary movement of the knob (not shown), and a limiting element that limits the rotation of the nut in the direction of rotation of the third shaft 49 and allows movement of the nut along the axial direction of the third shaft 49.

[0073] The housing 42 comprises the substantially bottom-shaped, cylindrical-tubular housing section 57 on the conversion unit side, which houses part of the third shaft 49 and the linear motion conversion mechanism 50, and a substantially cylindrical-tubular housing section 58 on the generation unit side, which is located on a radially outer side of the housing section 57 on the conversion unit side and houses the reaction force generation unit 44. As shown in Fig. As shown in Figure 7, the housing 42 is constructed such that after joining a part of an outer circumferential section of the conversion unit-side housing section 57 and a part of an outer circumferential section of the generation unit-side housing section 58, a connecting section 59 is arranged on this joined section, in which the interior of the conversion unit-side housing section 57 and the interior of the generation unit-side housing section 58 are connected to each other.

[0074] An opening on one end section 49a of the housing section 57 of the conversion unit is closed by the first cover element 45. The first cover element 45 is formed into a cylindrical tube shape with a through-hole 45a in its central section. The medium-diameter cylindrical column section 49d and the large-diameter cylindrical column section 49e of the third shaft 49 are inserted into the through-hole 45a of the cover element.An inner circumferential surface of the through-hole 45a of the cover element has a first inner circumferential surface section 45c, which adjoins a cover element end section 45b on one end section side 49a of the through-hole 45a of the cover element; a second inner circumferential surface section 45e, which is connected to the first inner circumferential surface section 45c via a first stepped section 45d and has a smaller diameter than the first inner circumferential surface section 45t; and a third inner circumferential surface section 45g, which is connected to the second inner circumferential surface section 45e via a second stepped section 45f and has a smaller diameter than the second inner circumferential surface section 45e. A space within the first inner circumferential surface section 45c is an O-ring receiving section 60, which receives the O-ring 38.A space within the second inner circumferential surface section 45e is a fifth bearing receiving section 85, which receives the fifth ball bearing 51. This bearing is for the rotatable support of the cylindrical column section with mean diameter 49d of the third shaft 49. On a surface 45h on the other end section side 49b of the first closure cover element 45, an annular, cover-side projection section 45i is formed at a position adjacent to the third inner circumferential surface section 45g, projecting from the surface 45h to the other end section side 49b. Furthermore, on the surface 45h of the first closure cover element 45, an annular, cover-side recessed section 45j is formed at a position adjacent to the cover-side annular projection 45i, recessing from the surface 45h to the other end section side 49b.

[0075] A first rubber stop 61 is arranged on an outer circumferential section of the cover-side annular projection 45i and the cover-side annular recess section 45j. The first rubber stop 61 mitigates a collision of the cap element 56 with the cover-side annular projection 45i and the resulting impact noise (or friction noise) when the nut 53 of the linear motion conversion mechanism 50 moves along the axial direction of the third shaft 49 towards one end section side 49a. The first rubber stop 61 has a first tubular body 61a with a tubular shape and an annular first overhang section 61b that projects from an outer circumferential edge section at one end section side 49a of the first tubular body 61a to the radially outer side of the third shaft 49.The first stop rubber 61 is arranged on the outer circumferential section of the lid-side annular projecting section 45i such that the first overhanging section 61b is located within the lid-side annular recessed section 45j, and a tip section of the first tubular body 61a is also positioned on the other end section side 49b with respect to a first projecting surface section 45k on the other end section side 49b of the lid-side annular projection 45i. Then, by pressing the first overhanging section 61b against a bottom surface of the lid-side annular recessed section 45j towards one end section side 49a, the first stop rubber 61 is fastened to the first closure lid element 45 by head sections of a plurality of fastening elements, e.g., bolts 62 (two bolts 62 are shown in the present embodiment).Furthermore, the first closure cover element 45 has an annular closure element flange section 45m, which extends outwards in the radial direction of the third shaft 49 from an outer circumferential section of the first closure cover element 45. The closure flange section 45m is attached and fastened to a housing flange section 57a, which is arranged on the conversion unit-side housing section 57, by screwing a fastening element, e.g., a screw 63, into the flange section 57a ​​of the conversion unit-side housing section 57 via a fastening element through-hole 45n, which is arranged on the closure flange section 45m.

[0076] At a position opposite the linear motion conversion mechanism 50 within the housing section 57 on the conversion unit side, a bottom wall section 64 is integrally formed with an inner circumferential section of the housing section 57 on the conversion unit side. The bottom wall section 64 is formed into a substantially cylindrical tube shape with a through-hole 64a in its central part. The large-diameter cylindrical column section 49e and the second small-diameter cylindrical column section 49f of the third shaft 49 are inserted into the through-hole 64a of the bottom wall section.The hole section 64a in the bottom wall section has a first inner surface section 64c, which adjoins a bottom wall end section 64b located on one end section side 49a, and a second inner surface section 64e, which is connected to the first inner surface section 64c via a stepped intermediate section 64d and has a larger diameter than the first inner surface section 64c. A space within a section adjoining the stepped intermediate section 64d on the second inner surface section 64e is a sixth bearing section 65, which accommodates the sixth bearing 52, which is the bearing for the rotatable support of the second cylindrical section 49f with a small diameter of the third shaft 49.

[0077] Additionally, an internal threaded section is formed on a section on the opposite end side 49b of the second inner surface section 64e, and this internal threaded section is screwed onto an external threaded section that is arranged on a cup-shaped second closure cap circumferential surface of the second closure cap element 46. Through this screw fastening, an axial end surface 46a arranged on the second closure cap element 46 presses an outer ring 52a of the sixth bearing 52 against the stepped intermediate section 64d, thereby fixing the outer ring 52a between the bottom wall section 64 and the second closure cap element 46.Furthermore, an external threaded section is formed on a circumferential surface of the second small-diameter cylindrical section 49f at a section located on the other end section side 49b with respect to the sixth bearing 52, and this external threaded section is screwed onto an internal threaded section formed on an inner circumferential surface of an annular pressure element 66. This screw connection causes a pressure surface 66a arranged on the pressure element 66 at one end section side 49a to press an inner ring 52b of the sixth bearing 52 against a contact surface 49i of the large-diameter cylindrical section 49e, thereby fixing the inner ring 52b between the third shaft 49 and the pressure element 66.Furthermore, on a surface 64f at one end section 49a of the bottom wall section 64, an annular, bottom-facing projection 64g is formed at a position near the first inner surface section 64c, projecting from the surface 64f towards one end section 49a. Additionally, on the surface 64f of the bottom wall section 64 at a position near the annular projection 64g, an annular depression section 64h is formed on the side of the bottom wall section, extending from the surface 64f towards the other end section 49b.

[0078] A second rubber stop 67 is arranged on an outer circumferential section of the annular projection 64g on the side of the bottom wall section and the annular recess section 64h on the side of the bottom wall section. The second rubber stop 67 mitigates a collision of the limiting element 55 with the annular projection 64g on the bottom wall side and the resulting impact noise when the nut 53 of the linear motion conversion mechanism 50 moves along the axial direction of the third shaft 49 to the other end section 49b. The second rubber stop 67 has a second tubular body 67a with a tubular shape and an annular second overhang section 67b that projects from an outer edge section on the other end section side 49b of the second tubular body 67a to the radially outer side of the third shaft 49.The second stop rubber 67 is arranged on the outer circumferential section of the annular projection 64g on the side of the bottom wall section such that the second overhanging section 67b is located within the annular recessed section 64h on the side of the bottom wall section, and a pointed section of the second tubular body 67a is positioned on one end section side 49a relative to the bottom wall end section 64b on the one end section side 49a of the annular projection 64g on the side of the bottom wall section. Then, by pressing the second overhanging section 67b against a bottom surface of the annular recessed section 64h on the side of the bottom wall section onto the other end section side 49b by means of head sections of a plurality of fastening elements, e.g., bolts 68 (two bolts 68 are shown in the present embodiment), the second stop rubber 67 is fastened to the bottom wall section 64.

[0079] The housing section 58 on the generation unit side is connected to the outer circumferential section of the housing section 57 on the conversion unit side by a housing connection section 42a on one end section side 49a and the other housing connection section 42b on the other end section side 49b. An opening located on the housing section 58 on one end section side 49a is closed by the third closure cover element 47, while an opening located on the housing section 58 on the other end section side 49b is closed by the fourth closure cover element 48.

[0080] A small tubular section 71, formed into a tubular shape with a bottom and having a smaller diameter than the outer diameter of the housing section 58 on the generation unit side, is integrally formed on an inner circumferential section of the housing section 58 on the generation unit side. The small tubular section 71 has a bottom section 71a located closer to the fourth end cap element 48, and a circumferential wall section 71b extending from an outer edge section of the bottom section 71a towards the third end cap element 47. The bottom section 71a is positioned within the generation-side housing section 58 such that, with respect to a position of the surface 64f of the bottom wall section 64 of the conversion-side housing section 57, it is located axially along the third shaft 49 on one end section side 49a.An insertion hole 73c, into which a large shaft section 77b of a second shaft section 77, both of which are described later, is inserted, is formed on a central section of the bottom section 71a such that it penetrates the bottom section 71a along the axial direction of the third shaft 49. The circumferential wall section 71b extends within the housing section 58 on the generating unit side from the outer edge section of the bottom section 71a to a position near the housing connection section 42a on one end section side in the axial direction of the third shaft 49.

[0081] The majority of the connecting unit 43 is located within the housing section 58 on the generating unit side and the connecting section 59. The connecting unit 43 connects the limiting element 55 of the linear motion conversion mechanism 50 and the reaction force generating unit 44. As shown in Fig. As shown in Figure 7, the connecting unit 43 comprises a first connecting half-section 72 and a second connecting half-section 73, which are arranged symmetrically in the axial direction of the third shaft 49. The first connecting half-section 72 and the second connecting half-section 73 are each formed by bending a thin, plate-shaped element made of a metal material three times.

[0082] The first connecting half-section 72 has a first fastening section 72a, which is attached to the limiting element 55; a first curved section 72b, which is bent at a right angle from the first fastening section 72a towards the reaction force generating unit 44; a second curved section 72c, which is bent at a right angle from one end of the first curved section 72b towards the third closure cover element 47; and a third curved section 72d, which is bent at a right angle from one end of the second curved section 72c to a side opposite the first curved section 72b. A first fastening hole 72e is formed on the first fastening section 72a such that it penetrates the first fastening section 72a. By screwing in a fastening element, e.g.A bolt 74 is inserted into an outer circumferential section of the limiting element 55 through this first fastening hole 72e, and the first fastening section 72a is attached to and fixed to the limiting element 55. At a position near a free end of the third curved section 72d, a first insertion hole 72f is formed, into which a small shaft section 76a of a first shaft section 76, both of which will be described later, penetrates along the axial direction of the third shaft 49 into the third curved section 72d.

[0083] The second connecting half-section 73 has the same shape as the first connecting half-section 72. The second connecting half-section 73 has a second fastening section 73a, which is attached to the limiting element 55; a fourth curved section 73b, which is bent at a right angle from the second fastening section 73a towards the reaction force generating unit 44; a fifth curved section 73c, which is bent at a right angle from one end of the fourth curved section 73b to the fourth closure cover element 48; and a sixth curved section 73d, which is bent at a right angle from one end of the fifth curved section 73c to a side opposite the fourth curved section 73b. A second fastening hole 73e is formed on the second fastening section 73a such that it penetrates the second fastening section 73a. By screwing in a fastening element, e.g.A bolt 75 is inserted into the outer circumferential section of the limiting element 55. Through this second fastening hole 73e, the second fastening section 73a is attached to and fixed on the limiting element 55. As shown in . Fig. As shown in Figure 7, a surface located on one end side 49a of the fourth curved section 73b abuts a surface located on the other end side 49b of the first curved section 72b of the first connecting half-section 72. At a position near a free end of the sixth curved section 73d, a second insertion hole 73f is formed, into which a small shaft section 77c of the second shaft section 77 described later is inserted, so that it penetrates the sixth curved section 73d along the axial direction of the third shaft 49.

[0084] The reaction force generating unit 44 comprises the first shaft section 76, the second shaft section 77, a first cylindrical guide tube element 78, a second cylindrical guide tube element 79, a spring connecting element 80, the first coil spring 81 and the second coil spring 82.

[0085] The first shaft section 76 comprises a small shaft section 76a, located on the side of the third closure cover element 47 and having a small diameter; a medium shaft section 76b, formed integrally with the small shaft section 76a and having a larger diameter; and a large shaft section 76c, formed integrally with the medium shaft section 76b and having a larger diameter. The first shaft section 76 is arranged on an outer surface radially to and parallel with the third shaft 49. Therefore, the axial direction of the first shaft section 76 is parallel to the axial direction of the third shaft 49.When the third shaft 49 rotates to the left, the nut 53 moves to the other end section side 49b, and this movement causes the first connecting half-section 72 to move to the fourth closure cover element 48. As the first connecting half-section 72 moves to the fourth closure cover element 48, the third curved section 72d of the first connecting half-section 72 presses against a first pressure surface 76d, located on the side of the third closure cover element 47, of the middle shaft section 76b of the first shaft section 76, and thus the first shaft section 76 moves towards the fourth closure cover element 48.

[0086] The second shaft section 77 has a spring-receiving tubular section 77a with a cylindrical tube shape and a base, wherein the large shaft section 77b projects from a base of the spring-receiving tubular section 77a towards the fourth locking clamping element 48, wherein the small shaft section 77c is formed integrally with the large shaft section 77b and has a smaller diameter than the large shaft section 77b, and a projecting section 77d projects from the base of the spring-receiving tubular section 77a towards the third locking cover element 47. The second shaft section 77 is arranged parallel to the third shaft 49. Therefore, the axial direction of the second shaft section 77 is parallel to the axial direction of the third shaft 49.When the third shaft 49 rotates to the right, the nut 53 moves to one end section side 49a, and due to and corresponding to this movement, the second connecting half-section 73 moves to the side of the third sealing cap element 47. As the second connecting half-section 73 moves to the side of the third sealing cap element 47, the sixth curved section 73d of the second connecting half-section 73 presses against a second pressure surface 77e, located on the side of the fourth sealing cap element 48, of the large shaft section 77b of the second shaft section 77, and thus the second shaft section 77 moves towards the third sealing cap element 47. In the steering actuation input device in the neutral position, a tip surface 77f of the protruding section 77d is flush with an axial end surface on the other end section side 49b of the limiting element 55 (see ). Fig. 8C and Fig. 9A).

[0087] The first cylindrical guide tube element 78 guides the central shaft section 76b of the first shaft section 76 slidably along the axial direction of the first shaft section 76. The first cylindrical guide tube element 78 has a first guide tube section 78a with a cylindrical tube shape and an annular first annular extension section 78b, which projects radially outward from an outer circumference of an axial end section on the side of the third end cap element 47 of the first guide tube section 78a. The first guide tube section 78a is, for example, attached to the circumferential wall section 71b by press-fitting.

[0088] The second cylindrical guide tube element 79 guides the large shaft section 76c of the first shaft section 76 slidably along the axial direction of the first shaft section 76. The second cylindrical guide tube element 79 has a second guide tube section 79a with a cylindrical tube shape and an annular second annular extension section 79b, which projects radially outward from an outer circumference of an axial directional end section on the side of the third end cap element 47 of the second guide tube section 79a. An inner circumferential surface of the second guide tube section 79a has an inclined section 79c, which is inclined such that an inner diameter of the second guide tube section 79a decreases from the side of the third end cap element 47 toward the fourth end cap element 48. As shown in Fig. As shown in Figure 7, in the steering actuation input device, in the neutral position, an axial end surface 76e is located on the side of the fourth end cap element 48 of the large shaft section 76c of the first shaft section 76 at a position closer to the second annular extension section 79b of the second guide tube section 79a. A space located on the side of the fourth end cap element 48, with respect to the large shaft section 76c of the first shaft section 76, within the second cylindrical guide tube element 79, is a first spring receiving section 83, which receives the first coil spring 81, which is a thrust element.

[0089] The spring connecting element 80, which connects the first coil spring 81 and the second coil spring 82, is arranged at an axial end section on the side of the fourth end cap element 48 of the second cylindrical guide tube element 79. The spring connecting element 80 has a connecting cylinder tube device 80a with a cylindrical tube shape and an annular stop extension section 80b, which projects radially outward from an outer circumferential section of an axial direction center of the connecting cylinder tube device 80a. The outer diameter of the stop extension section 80b is smaller than the inner diameter of the spring-receiving tubular section 77a of the second shaft section 77.

[0090] The first coil spring 81 is a linear coil spring arranged in a state where no preload is exerted on the coil spring, i.e., in a state of free length. The first coil spring 81 is arranged on an outer side in the radial direction of the third shaft 49. That is, the first coil spring 81 extends parallel to the third shaft 49 within the first spring retaining section 83 of the second cylindrical guide tube element 79. Within the first spring retaining section 83, one end of the first coil spring 81 abuts the axial section end surface 76e of the large shaft section 76c of the first shaft section 76, and the other end of the first coil spring 81 abuts a first stop surface 80c on the side of the third end cap element 47 of the spring connection device 80. Here, the inclined section 79c also serves as a guide, which, in a situation where the first coil spring 81 is displaced due to external vibrations, shocks, etc.The radial displacement (radial deviation) of the first coil spring 81 can be displaced radially outwards from an axis of the first shaft section 76, limiting the outward displacement (radial deviation). Furthermore, the inclined section 79c can serve as a stop against which the axial section end surface 76e of the large shaft section 76c rests when the first shaft section 76 moves maximally towards the side of the fourth closure cover element 48.

[0091] A space located on the side of the fourth locking clamping element 48 in relation to the spring connecting element 80 within the spring-receiving tubular section 77a of the second shaft section 77 is a second spring receiving section 84 which receives the second coil spring 82.

[0092] The second coil spring 82 is a linear coil spring arranged in a state where a preload is applied to the coil spring. The second coil spring 82 is arranged on an outer side in the radial direction of the third shaft 49. That is, the second coil spring 82 extends parallel to the third shaft 49 within the second spring receiving chamber 84 of the spring-receiving tubular section 77a. Within this second spring receiving chamber 84, one end of the second coil spring 82 abuts a second stop surface 80d on the side of the fourth end cap element 48 of the spring connecting element 80, and the other end of the second coil spring 82 abuts the underside of the spring-receiving tubular section 77a of the second shaft section 77 around the projecting section 77d.

[0093] A damping mechanism for damping the compressive force of the first coil spring 81, for example an axle-mounted damping mechanism similar to a suspension mounted on a vehicle, can be arranged between one end of the first coil spring 81 and the axial section end face 76e of the large shaft section 76c of the first shaft section 76. Likewise, a damping mechanism for damping the compressive force of the second coil spring 82, for example an axle-mounted damping mechanism similar to a suspension mounted on a vehicle, can be arranged between the other end of the second coil spring 82 and the base of the spring-receiving tubular section 77a of the second shaft section 77. Furthermore, this damping mechanism can be incorporated into the large shaft section 76c of the first shaft section 76, the large shaft section 77b, or the projecting section 77d of the second shaft section 77.

[0094] The Fig. Figures 8A to 8C are explanatory diagrams that show the function or operation of the steering actuation input device when the third shaft 49 is rotated to the left. Fig. Figure 8A is an explanatory diagram showing the steering actuation input device when the third shaft 49 is rotated 180 degrees to the left from a neutral position. Fig. Figure 8B is an explanatory diagram showing the steering actuation input device when the third shaft 49 is rotated 60 degrees to the left from the neutral position. Fig. Figure 8C is an explanatory illustration showing the steering actuation input device in the neutral position. In the Fig. In Figures 8A to 8C, the position of the axial end surface 76e of the large shaft section 76c of the first shaft section 76 in the neutral position is indicated by a dashed line A, and the path (location) of the position of the axial end surface 76e of the large shaft section 76c when the third shaft 49 is rotated 180 degrees to the left from the neutral position is shown by a dashed line B. Furthermore, in Figures 8A to 8C, the position of the tip surface 77f of the preceding section 77d of the second shaft section 77 is indicated by a dashed line C. It should be noted that in Figures 8A to 8C, the position of the tip surface 77f is constant, i.e., it is a position of the tip surface 77f in the neutral position.

[0095] First, if the third wave 49 turns 60 degrees to the left (in Fig. 8B (shown as “-60°”) from the in Fig. 8C is rotated to the neutral position shown, as in Fig. As shown in Figure 8B, the nut 53 moves to the other end section side 49b, and through this movement, the first connecting half-section 72 moves together with the second connecting half-section 73 to the fourth closure cover element 48. Then, the third curved section 72d of the first connecting half-section 72 pushes the first pressure surface 76d of the middle shaft section 76b of the first shaft section 76 towards the fourth closure cover element 48, causing the first shaft section 76 to move towards the fourth closure cover element 48 and press the first coil spring 81 against the spring connecting element 80. At this point, the sixth curved section 73d of the second connecting half-section 73 is separated from the second pressure surface 77e of the large shaft section 77b of the second shaft section 77.The compressive force of the first coil spring 81 then acts on the nut 53 via the first shaft section 76, the first connecting half-section 72 and the limiting element 55. This results in a reaction force corresponding to the compressive force of the first coil spring 81 acting in a direction that rotates the third shaft 49 to the right.

[0096] If the third wave 49 from the in Fig. The position shown in 8B is rotated 180 degrees to the left (in Fig. 8A (shown as “-180°”), the nut 53 moves further to the other end section side 49b, and through and according to this movement the first connecting half section 72 together with the second connecting half section 73 moves further to the fourth closure cover element 48.

[0097] Here, the nut 53 moves to an axial end where the limiting element 55 on the other end section side 49b abuts the second stop rubber 67. Then, the third curved section 72d of the first connecting half-section 72 presses the first pressure surface 76d of the middle shaft section 76b of the first shaft section 76 further toward the fourth closure cover element 48, causing the first shaft section 76 to move further toward the fourth closure cover element 48. With this movement, the first shaft section 76 presses the first coil spring 81 further against the spring connecting element 80 and additionally presses the second coil spring 82 through the first coil spring 81 and the spring connecting element 80. At this point, the sixth curved section 73d of the second connecting half-section 73 is further separated from the second pressure surface 77e of the large shaft section 77b of the second shaft section 77.Since the axial section end surface 76e of the first shaft section 76 rests against the inclined section 79c of the second cylindrical guide tube element 79, the movement of the first shaft section 76 towards the fourth end cap element 48 is restricted. The compressive force generated by each compression of the first coil spring 81 and the second coil spring 82 then acts via the first shaft section 76, the first connecting half-section 72, and the limiting element 55 on the nut 53. This results in a reaction force, corresponding to the compressive force of the first coil spring 81 and the second coil spring 82, acting in one direction to rotate the third shaft 49 to the right.

[0098] The Fig. Figures 9A to 9C are explanatory diagrams that show the function or operation of the steering actuation input device when the third shaft 49 is rotated to the right. Fig. Figure 9A is an explanatory diagram showing the steering actuation input device in a neutral position. Fig. Figure 9B is an explanatory diagram showing the steering actuation input device when the third shaft 49 is rotated 60 degrees to the right from the neutral position. Fig. Figure 9C is an explanatory diagram showing the steering actuation input device during a rotation of the third shaft 49 by 180 degrees clockwise from the neutral position. In Figures 9A to 9C, the position of the axial section end surface 76e of the large shaft section 76c of the first shaft section 76 is indicated by a dashed line A. In Figures 9A to 9C, the position of the axial section end surface 76e is constant, i.e., it is the position of the axial section end surface 76e in the neutral position. Furthermore, in Figures 9A to 9C, the position of the tip surface 77f of the preceding section 77d in the neutral position is indicated by a dashed line C, and the path (location) of the position of the tip surface 77f of the preceding section 77d when the third shaft 49 is rotated 180 degrees clockwise from the neutral position is indicated by a dashed line D.

[0099] If the third wave 49 turns 60 degrees to the right (in Fig. 9B (shown as “+60°”) from the in Fig. When rotated to the neutral position shown in 9A, it moves as shown in Fig. As shown in Figure 9B, the nut 53 moves to one end section side 49a, and through and in accordance with this movement, the second connecting half-section 73 moves together with the first connecting half-section 72 to the third closure cover element 47. Then, the sixth curved section 73d of the second connecting half-section 73 presses the second pressure surface 77e of the large shaft section 77b of the second shaft section 77 towards the third closure cover element 47, causing the second shaft section 77 to move towards the third closure cover element 47 and compressing the first coil spring 81 via the second coil spring 82 and the spring connecting element 80. At this point, the third curved section 72d of the first connecting half-section 72 is separated from the first pressure surface 76d of the middle shaft section 76b of the first shaft section 76.Furthermore, the bottom of the spring-receiving tubular section 77a of the second shaft section 77 is separated from the bottom section 71a of the small tubular section 71 of the housing section 58 on the generating unit side. The compressive force of the first coil spring 81 then acts on the nut 53 via the second shaft section 77, the second connecting half-section 73, and the limiting element 55. This results in a reaction force corresponding to the compressive force of the first coil spring 81 acting in a direction that rotates the third shaft 49 to the left.

[0100] If the third wave 49 from the in Fig. The position shown in 9B is rotated 180 degrees to the right (in Fig. (9C shown as “+180°”), the nut 53 moves further towards the side of one end section 49a, and through and in accordance with this movement, the second connecting half-section 73, together with the first connecting half-section 72, moves further towards the side of the third closure cover element 47. Here, the nut 53 moves until one end, in an axial direction, abuts the first stop rubber 61 on one end section side 49a of the cap element 56. Then, the sixth curved section 73d of the second connecting half-section 73 pushes the second pressure surface 77e of the large shaft section 77b of the second shaft section 77 further towards the third closure cover element 47, causing the second shaft section 77 to move further towards the third closure cover element 47.With this movement, the second shaft section 77 further compresses the first coil spring 81 between the large shaft section 76c of the first shaft section 76 and the spring connecting device 80, and additionally presses the second coil spring 82 against the spring connecting device 80. At this point, the axial end face 76e of the first shaft section 76 abuts the inclined section 79c of the second cylindrical guide tube element 79. The compressive force generated by the first coil spring 81 and the second coil spring 82 then acts on the nut 53 via the second shaft section 77, the second connecting half-section 73, and the limiting element 55. This results in a reaction force corresponding to the compressive force of the first coil spring 81 and the second coil spring 82 acting in one direction to rotate the third shaft 49 to the left. [Effects of the second embodiment]

[0101] As described above, in the second embodiment, the steering actuation input device comprises the linear motion conversion mechanism 50, which converts the rotation of the third shaft 49 into the axial motion of the third shaft 49. The linear motion conversion mechanism 50 includes the nut 53, which moves in the axial direction of the third shaft 49. Furthermore, the first coil spring 81 and the second coil spring 82 exert a penetrating force on the nut 53 via the connecting unit 43 and the limiting element 55. Since the penetrating force is exerted on the movement of the nut 53 along the axial direction of the third shaft 49, the selection range for the type of penetrating element can be expanded.

[0102] Furthermore, in the present embodiment, the linear motion conversion mechanism 50 comprises the shaft-side ball screw groove 49h, which is the helical groove formed on the outer circumferential surface of the large-diameter cylindrical column section 49e of the third shaft 49; the nut-side ball screw groove 53a, which is the helical groove formed on an inner circumferential surface of the nut 53, which is the linear motion element; the multiple balls 54 arranged between the ball screw spiral grooves 49h and 53a; the limiting element 55, which limits the rotation of the nut 53 in the rotational direction of the third shaft 49 and allows movement of the nut 53 along the axial direction of the third shaft 49; and the cap element 56, which holds the nut 53 against the limiting element 55. That is to say, the linear motion conversion mechanism 50 is the ball screw mechanism.Since the nut 53 moves smoothly on the third shaft 49 by sliding over the multitude of balls 54 arranged between the ball recirculation grooves 49h and 53a, the rotation of the third shaft 49 can be quickly and efficiently converted into a linear motion.

[0103] Furthermore, in the present embodiment, the linear motion conversion mechanism is not a ball screw mechanism, but can be a linear motion conversion mechanism that uses a threaded connection. In this case, the linear motion conversion mechanism can be manufactured with fewer parts than the ball screw mechanism, thereby reducing manufacturing costs.

[0104] Furthermore, in the present embodiment, the first coil spring 81 and the second coil spring 82 are arranged on the outside in the radial direction of the third shaft 49 and run parallel to the third shaft 49. That is, the first coil spring 81 and the second coil spring 82 are not arranged on the third shaft 49, which is provided with the linear motion conversion mechanism 50. Therefore, it is possible to easily change the thrust force exerted on the steering actuation input device by simply replacing the first coil spring 81 and the second coil spring 82 at a position remote from the linear motion conversion mechanism 50.

[0105] In the present embodiment, as in the first embodiment, taking into account the friction generated by a sealing element between the third shaft 49 and the sealing element, the first coil spring 81 could be fitted with a preload corresponding to the torque caused by the friction exerted on the first coil spring 81. Furthermore, the spring constant of the first coil spring 81 and the spring constant of the second coil spring 82 can be the same or different. [Third embodiment]

[0106] Fig. Figure 10 is a diagram showing an actuating force as a function of an actuating angle according to a third embodiment.

[0107] In the third embodiment, two nonlinear coil springs are used as the actuating element instead of the first coil spring 81 and the second coil spring 82, which are linear springs of the second embodiment. The nonlinear coil spring is, for example, a barrel-shaped coil spring, a drum-shaped coil spring, or the like. In the third embodiment, the actuating force changes in three stages with respect to the actuating angle. More precisely, as in Fig.As shown in Figure 10, the actuating force increases with a nonlinear spring at a first rate of increase up to a first actuating angle α, and then increases with a second rate of increase, greater than the first, from the first actuating angle α to a second actuating angle β, which is greater than the first actuating angle α. With the other nonlinear spring, the actuating force increases after the second actuating angle β at a third rate of increase, which is smaller than the second rate of increase. [Effects of the third embodiment]

[0108] As described above, in the third embodiment the two nonlinear springs are used as thrust elements. Therefore, in the third embodiment as well, the actuation force decreases after the second actuation angle β, thereby reducing driver fatigue. Furthermore, if the driver operates the rotary knob in such a way as to exceed the second actuation angle β, for example, by rotating the third shaft 49 from a clockwise rotation to a counterclockwise rotation and adding to the counterclockwise rotation, the driver is less likely to experience a feeling of binding. QUOTES INCLUDED IN THE DESCRIPTION

[0000] This list of documents cited by the applicant was automatically generated and is included solely for the reader's convenience. The list is not part of the German patent or utility model application. The DPMA accepts no liability for any errors or omissions. Cited patent literature

[0000] JP 2015-082071

[0004]

Claims

[1] A steering control input device into which the steering input of the driver is entered via a steering control input element attached to a vehicle, wherein the steering control input device comprises: a shaft onto which a steering force is transmitted from the steering actuation input element and which rotates about an axis of rotation; and a pushing element that exerts a pushing force against the rotation of the shaft, wherein the pushing element comprises: a first pushing element that exerts a pushing force on the shaft regardless of the direction of rotation of the shaft; and a second pushing element, which is attached with a preload applied to the second pushing element and which, after the first pushing element exerts the pushing force, exerts a pushing force on the shaft regardless of the direction of rotation of the shaft. [2] The steering actuation input device according to claim 1, where The first pushing element continues to exert pushing force on the shaft even after the pushing force has been applied by the second pushing element. [3] The steering actuation input device according to claim 2, which further includes a position switching mechanism configured to switch between a non-fixed position and a fixed position of the end sections of the first thrust element and the second thrust element when the shaft is rotated. [4] The steering actuation input device according to claim 3, where The first pushing element and the second pushing element are each a torsion spring. [5] The steering actuation input device according to claim 4, where the wave comprises a first wave equipped with the first pushing element and a second wave equipped with the second pushing element, a coupling element that covers the first shaft and the first thrust element, is arranged on an outside in the radial direction of the first shaft, the coupling element is connected to the first shaft via the first thrust element and is also connected to the second shaft, and The second shaft rotates together with the coupling element when the first pushing element reaches a predetermined load. [6] The steering actuation input device according to claim 5, where The predetermined load is a load generated by the prestress applied to the second thrust element. [7] The steering actuation input device according to claim 5, where the outer diameter of the first shaft is smaller than the inner diameter of the first pushing element when the first pushing element generates the pushing force and deforms. [8] The steering actuation input device according to claim 5, where The coupling element and the second shaft are attached to each other via a D-shaped cutout. [9] The steering actuation input device according to claim 5, where The coupling element and the second shaft are attached to each other via a keyway section. [10] The steering actuation input device according to claim 1, where The first compression element and the second compression element are each a non-linear spring. [11] The steering actuation input device according to claim 1, which further includes a housing that accommodates part of the shaft and the thrust elements wherein the housing is provided with a sealing element that seals a gap between the housing and an outer circumferential surface of the shaft. [12] The steering actuation input device according to claim 1, which further includes a damping mechanism configured to exert a damping force on the pushing element. [13] The steering actuation input device according to claim 2, which further includes a linear motion conversion mechanism configured to convert the rotation of the shaft into an axial motion of the shaft, wherein the linear motion conversion mechanism includes a linear motion element and The first pushing element and the second pushing element exert the pushing force on the linear motion element. [14] The steering actuation input device according to claim 13, where the first pushing element and the second pushing element are arranged on an outside in a radial direction of the shaft and extend parallel to the shaft. [15] The steering actuation input device according to claim 13, where The linear motion conversion mechanism includes: a spiral-shaped first uneven section formed on an outer circumferential surface of the shaft; a movable element with a helical second uneven section which engages with the first uneven section, wherein the movable element is movable in the axial direction of the shaft in accordance with a rotational movement of the steering actuation input element; and a limiting element that limits the rotation of the movable element in the direction of rotation of the shaft and allows movement of the movable element along an axial direction of the shaft. [16] The steering actuation input device according to claim 13, where The linear motion conversion mechanism is a ball screw mechanism. [17] A steering device of the “steer-by-wire” type, which is provided with the steering actuation input device according to any one of the preceding claims 1 to 16.

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