阅读说明：本技术 传感器 (Sensor with a sensor element ) 是由 外山祐一 于 2020-01-07 设计创作，主要内容包括：本发明涉及一种传感器,其包括：主驱动齿轮,该主驱动齿轮安装在受到传感器检测的轴上,使得主驱动齿轮能够与轴一体地旋转；至少一个从动齿轮,所述至少一个从动齿轮与主驱动齿轮啮合；传感器壳体(31),该传感器壳体容纳主驱动齿轮和所述至少一个从动齿轮；偏置构件,该偏置构件将所述至少一个从动齿轮朝向主驱动齿轮偏置；以及转换机构,该转换机构构造成：当将轴插入到传感器壳体(31)中时所述至少一个从动齿轮的一部分与主驱动齿轮的一部分接触时,将与轴的轴向方向平行且作用在所述至少一个从动齿轮上的轴向力转换成使所述至少一个从动齿轮与主驱动齿轮分开的方向上的力。(The invention relates to a sensor, comprising: a main drive gear mounted on the shaft detected by the sensor such that the main drive gear is rotatable integrally with the shaft; at least one driven gear in mesh with the main drive gear; a sensor housing (31) that houses the main drive gear and the at least one driven gear; a biasing member biasing the at least one driven gear toward the main drive gear; and a conversion mechanism configured to: when a portion of the at least one driven gear comes into contact with a portion of the main drive gear when the shaft is inserted into the sensor housing (31), an axial force parallel to the axial direction of the shaft and acting on the at least one driven gear is converted into a force in a direction in which the at least one driven gear separates from the main drive gear.)

1. A sensor, characterized by comprising:

a main drive gear mounted on a shaft detected by the sensor such that the main drive gear is rotatable integrally with the shaft;

at least one driven gear in mesh with the main drive gear;

a sensor housing (31), the sensor housing (31) accommodating the main drive gear and the at least one driven gear, the sensor being configured to detect a rotation angle of the shaft based on rotation of the at least one driven gear rotating together with the main drive gear, the at least one driven gear being supported in the sensor housing (31) such that the at least one driven gear is rotatable and movable in a radial direction of the main drive gear, and being engaged with the main drive gear by inserting the shaft, to which the main drive gear is mounted, into the sensor housing (31);

a biasing member biasing the at least one driven gear toward the main drive gear; and

a conversion mechanism configured to: when a part of the at least one driven gear comes into contact with a part of the main drive gear with the shaft inserted into the sensor housing (31), an axial force parallel to the axial direction of the shaft and acting on the at least one driven gear is converted into a force in a direction in which the at least one driven gear is moved away from the main drive gear.

2. The sensor of claim 1, wherein:

two driven gears are mounted as the at least one driven gear;

each of the two driven gears includes a gear portion that meshes with the main drive gear and a shaft portion that is supported by the sensor housing (31); and is

The biasing member is a coil torsion spring (85), the coil torsion spring (85) includes a coil portion (85a), a first arm (85b), and a second arm (85c), the coil portion (85a) is supported in the sensor housing (31), the first arm (85b) biases the shaft portion of one of the two driven gears toward the main drive gear, and the second arm (85c) biases the shaft portion of the other of the two driven gears toward the main drive gear.

3. The sensor according to claim 1, wherein the conversion mechanism is an inclined surface (71b, 73b, 52b) provided in a portion of at least one of i) the main drive gear and ii) each of the at least one driven gear, which faces a portion of the other of i) the main drive gear and ii) each of the at least one driven gear in an axial direction of the shaft when the shaft is inserted into the sensor housing (31).

4. The sensor according to claim 2, wherein the conversion mechanism is an inclined surface (71b, 73b, 52b) provided in a portion of at least one of i) the main drive gear and ii) each of the two driven gears, which faces a portion of the other of i) the main drive gear and ii) each of the two driven gears in an axial direction of the shaft when the shaft is inserted into the sensor housing (31).

5. A sensor according to claim 1, characterized in that a torque sensor (41) configured to detect a torque acting on the shaft is mounted in the sensor housing (31).

6. The sensor according to any one of claims 1 to 5, wherein the shaft is a pinion shaft (13) that meshes with a guide shaft that steers a steered wheel of a vehicle.

Technical Field

The present invention relates to sensors.

Background

With the recent increased functionality of vehicles, various systems for improving driving stability, such as a vehicle stability control system and an electronically controlled suspension system, are sometimes mounted on the vehicles. These systems receive the steering angle of the steering wheel as part of the vehicle attitude information and control the vehicle based on the attitude information to stabilize the attitude of the vehicle. Therefore, a rotation angle sensor for detecting a steering angle of a steering wheel is mounted on a steering column of a vehicle, for example.

For example, the rotation angle sensor of japanese unexamined patent application publication (translation of PCT application) No.11-500828(JP 11-500828a) includes a main drive gear that rotates together with a steering shaft and two driven gears that mesh with the main drive gear. The number of teeth of one driven gear is different from that of the other driven gear, and therefore, the rotation angles of the two driven gears caused by the rotation of the main drive gear are different from each other. The rotation angle sensor detects rotation angles of the two driven gears using sensors corresponding to the two driven gears and calculates a rotation angle of the steering shaft based on the detected rotation angles.

Disclosure of Invention

The rotational angle sensor of JP 11-500828A is assembled by inserting a steering shaft, to which a main drive gear is mounted, into a housing that internally supports two driven gears. At this time, depending on the rotational positions of the main drive gear and the two driven gears, the teeth of the driven gears may interfere with the teeth of the main drive gear in the axial direction of the steering shaft. Such interference may hinder the assembly of the rotation angle sensor.

The invention provides a smoothly assembled sensor.

One aspect of the invention relates to a sensor comprising: a main drive gear mounted on the shaft detected by the sensor such that the main drive gear can rotate integrally with the shaft; at least one driven gear in mesh with the main drive gear; a sensor housing accommodating the main drive gear and the at least one driven gear, the sensor being configured to detect a rotation angle of the shaft based on rotation of the at least one driven gear rotating together with the main drive gear, the at least one driven gear being supported in the sensor housing such that the at least one driven gear is rotatable and movable in a radial direction of the main drive gear, and the at least one driven gear being engaged with the main drive gear by inserting the shaft mounted with the main drive gear into the sensor housing; a biasing member biasing the at least one driven gear toward the main drive gear; and a conversion mechanism configured to: when a portion of the at least one driven gear comes into contact with a portion of the main drive gear with the shaft inserted into the sensor housing, an axial force parallel to an axial direction of the shaft and acting on the at least one driven gear is converted into a force in a direction in which the at least one driven gear is away from the main drive gear.

When the shaft on which the main drive gear is mounted is inserted into the sensor housing in which the driven gear is supported, a portion of the driven gear may interfere with a portion of the main drive gear in the axial direction of the shaft depending on the rotational position of the driven gear or the main drive gear. In this case, according to the above configuration, the conversion mechanism converts the axial force parallel to the axial direction of the shaft and acting on the driven gear into a force in a direction to move the driven gear away from the main drive gear. Therefore, the driven gear moves in a direction away from the main drive gear against the biasing force of the biasing member. Therefore, it is possible to further push the shaft in the sensor housing while avoiding interference between a part of the driven gear and a part of the main drive gear. When the shaft is inserted to a predetermined position in the sensor housing, the driven gear moves toward the main drive gear under the biasing force of the biasing member, and thus, the driven gear meshes with the main drive gear. Therefore, since the operation of inserting the shaft into the sensor housing is not hindered by interference between a portion of the driven gear and a portion of the main drive gear, the sensor is smoothly assembled.

In the above sensor, two driven gears may be installed as the at least one driven gear; each of the two driven gears may include a gear portion engaged with the main drive gear and a shaft portion supported by the sensor housing; and the biasing member may be a coil torsion spring including a coil portion supported in the sensor housing, a first arm biasing a shaft portion of one of the two driven gears toward the main drive gear, and a second arm biasing a shaft portion of the other of the two driven gears toward the main drive gear.

According to such a configuration, the two driven gears are biased toward the main drive gear by the first arm and the second arm of the coil torsion spring. Since only one coil torsion spring is provided, an increase in the number of parts can be restricted.

In the above sensor, the conversion mechanism may be an inclined surface provided in a portion of at least one of i) the main drive gear and ii) each of the at least one driven gear, the portion facing a portion of the other of i) the main drive gear and ii) each of the at least one driven gear in an axial direction of the shaft when the shaft is inserted into the sensor housing. In other words, the inclined surface may be provided in the main driving gear or each of the at least one driven gear, or the inclined surface may be provided in the main driving gear and each of the at least one driven gear.

According to such a configuration, since the inclined surface is simply provided in at least one of i) the main drive gear and ii) each of the at least one driven gear, the configuration is simplified.

In the above sensor, the conversion mechanism may be an inclined surface provided in a portion of at least one of i) the main drive gear and ii) each of the two driven gears, the portion facing a portion of the other of i) the main drive gear and ii) each of the two driven gears in the axial direction of the shaft when the shaft is inserted into the sensor housing. In other words, the inclined surface may be provided in the main drive gear or each of the two driven gears, or the inclined surface may be provided in the main drive gear and each of the two driven gears.

According to such a configuration, since the inclined surface is simply provided in at least one of i) the main drive gear and ii) each of the two driven gears, the configuration is simplified.

In the above sensor, a torque sensor configured to detect torque acting on the shaft may be mounted in the sensor housing.

According to such a configuration, not only the rotation angle of the shaft but also the torque acting on the shaft is detected by a single sensor.

In the above sensor, the shaft may be a pinion shaft that meshes with a guide shaft that steers a steering wheel of the vehicle.

The sensor of the above aspect of the invention is smoothly assembled.

Drawings

Features, advantages, and technical and industrial significance of exemplary embodiments of the present invention will be described below with reference to the accompanying drawings, in which like reference numerals represent like elements, and in which:

fig. 1 is a configuration diagram of a steering device mounted with a sensor according to an embodiment;

FIG. 2 is a cross-sectional view of a torque angle sensor according to an embodiment taken along an axial direction of a pinion shaft;

FIG. 3 is a sectional view taken along line III-III in FIG. 2;

FIG. 4 is an exploded cross-sectional view of a torque angle sensor according to an embodiment;

fig. 5 is a sectional view of a main portion taken along a line V-V in fig. 2; and

fig. 6A is a sectional view showing a main portion where teeth of the main drive gear and teeth of the driven gear interfere with each other in the axial direction during assembly of the torque angle sensor, fig. 6B is a sectional view showing a main portion where the driven gear has moved in a direction away from the main drive gear, and fig. 6C is a sectional view showing a main portion where teeth of the driven gear mesh with teeth of the main drive gear.

Detailed Description

An embodiment in which the sensor is applied to a steering device of a vehicle will be described. As shown in fig. 1, a steering apparatus 10 of a vehicle includes a steering shaft 12 connected to a steering wheel 11. A pinion shaft 13 is mounted at an end of the steering shaft 12 opposite to the steering wheel 11. The guide shaft 14 extends in a direction intersecting the pinion shaft 13, and the pinion teeth 13a of the pinion shaft 13 mesh with the rack teeth 14a of the guide shaft 14. The left and right steered wheels 16 and 16 are connected to respective ends of the guide shaft 14 via tie rods 15.

The steering device 10 includes a motor 21, a speed reduction mechanism 22, a pinion shaft 23, a torque angle sensor (hereinafter referred to as "TAS 24"), and a control device 25 as a configuration for generating a steering assist force (assist force).

The motor 21 is a generation source of the steering assist force, and, for example, a three-phase brushless motor is used as the motor 21. The motor 21 is connected to a pinion shaft 23 via a speed reduction mechanism 22. The pinion teeth 23a of the pinion shaft 23 mesh with the rack teeth 14b of the guide shaft 14. The rotation speed of the motor 21 is reduced by the reduction mechanism 22, and the resulting rotational force is transmitted from the pinion shaft 23 to the pinion shaft 13 through the guide shaft 14 as a steering assist force.

The TAS 24 is mounted on the pinion shaft 13 (specifically, the TAS 24 is provided in a gear box that accommodates the guide shaft 14 and the pinion shaft 13). The TAS 24 includes a torque sensor and a rotation angle sensor in combination with each other. The TAS 24 detects torque applied to the pinion shaft 13 by an operation of rotating the steering wheel 11 as steering torque Th. The TAS 24 also detects a rotation angle θ pa of the pinion shaft 13 for a plurality of rotations exceeding 360 ° as a steering angle θ s.

The control device 25 receives the steering torque Th and the steering angle θ s both detected by the TAS 24. The control device 25 also receives a vehicle speed V detected by a vehicle speed sensor 26 mounted in the vehicle. The control device 25 executes assist control for generating a steering assist force (assist force) in accordance with the steering torque Th and the vehicle speed V by controlling the current applied to the motor 21. The control device 25 controls the supply of electric power (supply of electric power) to the motor 21 based on the steering torque Th detected by the TAS 24 and the vehicle speed V detected by the vehicle speed sensor 26.

Next, the configuration of TAS 24 will be described. As shown in fig. 2, the TAS 24 has a sensor housing 31. The sensor housing 31 is attached to the gear case 17 accommodating the guide shaft 14. The sensor housing 31 has an insertion hole 32 and a housing chamber 33. The pinion shaft 13 is inserted into the insertion hole 32. Although not shown in the drawings, the pinion shaft 13 includes an input shaft on the side of the steering shaft 12, an output shaft on the side of the guide shaft 14, and a torsion bar connecting the input shaft and the output shaft. The housing chamber 33 is in the shape of a box that is open in a direction intersecting the axial direction of the pinion shaft 13. The accommodation chamber 33 communicates with the insertion hole 32 and is open to the outside of the sensor housing 31. The opening 33a of the housing chamber 33 is closed by a cover 34.

A torque sensor 41 and a rotation angle sensor 51 are mounted inside the sensor housing 31. Although not shown in the drawings, the torque sensor 41 includes a permanent magnet, a yoke, a magnetism collecting ring, and a magnetic sensor. The permanent magnet is fixed to the input shaft of the pinion shaft 13. The yoke is fixed to an output shaft of the pinion shaft 13 and forms a magnetic path according to a magnetic field of the permanent magnet. The magnetism collecting ring is fixed in the sensor housing 31 and induces a magnetic flux from the yoke. The magnetic sensor detects magnetic flux induced by the magnetism collecting ring.

When the torsion bar of the pinion shaft 13 is torsionally deformed by the operation of the steering wheel 11, the relative positions of the permanent magnet and the yoke in the rotational direction are changed accordingly. Therefore, the density of the magnetic flux induced from the permanent magnet through the yoke to the magnetism collecting ring changes accordingly. The magnetic sensor generates an electric signal according to the magnetic flux density. The control device 25 detects torque acting on the torsion bar as steering torque based on an electric signal generated by the magnetic sensor.

As shown in fig. 3, the rotational angle sensor 51 has a main drive gear 52 and two driven gears 53, 54. The main drive gear 52 is fitted on the input shaft of the pinion shaft 13 such that the main drive gear 52 is rotatable integrally with the input shaft of the pinion shaft 13 (i.e., together with the input shaft of the pinion shaft 13). The two driven gears 53, 54 are rotatably supported in the accommodation chamber 33 of the sensor housing 31 by a support member 55. The two driven gears 53, 54 mesh with the main drive gear 52. Therefore, when the pinion shaft 13 rotates, the main drive gear 52 also rotates together with the pinion shaft 13, and the two driven gears 53, 54 rotate accordingly. The number of teeth of the driven gear 53 is different from that of the driven gear 54. Therefore, when the main drive gear 52 rotates together with the rotation of the pinion shaft 13, the rotation angles of the two driven gears 53 and 54 are different from each other with respect to the rotation angle of the main drive gear 52. The permanent magnets 57, 58 are mounted in the driven gears 53, 54, respectively, so that the permanent magnets 57, 58 are rotatable integrally with the driven gears 53, 54 (i.e., together with the driven gears 53, 54), respectively.

As shown in fig. 2, a substrate 61 is mounted on the inner bottom surface of the accommodating chamber 33 of the sensor housing 31. Two magnetic sensors (only one is shown in fig. 2) 62, 63 are mounted on a side surface of the base plate 61 on the side where the driven gears 53, 54 are located (i.e., the upper surface of the base plate 61 in fig. 2). The magnetic sensors 62, 63 face the permanent magnets 57, 58 (only one is shown in fig. 2) in the axial direction of the insertion hole 32 of the sensor housing 31. A hall sensor or a Magnetoresistive (MR) sensor is used as the magnetic sensors 62, 63. The magnetic sensors 62 and 63 generate electric signals in accordance with changes in magnetic field that occur with rotation of the driven gears 53 and 54. The control device 25 detects the rotation angle θ pa of the pinion shaft 13 as a steering angle θ s based on the electric signals generated by the magnetic sensors 62 and 63. The magnetic sensor of the torque sensor 41 is also mounted on the substrate 61.

Next, a process of assembling the TAS will be described. As shown in fig. 4, when attaching the TAS 24 to the gear case 17, the subassembly (unit) of the TAS 24 is first assembled. The driven gears 53, 54, the base plate 61, and the magnetism collecting ring of the torque sensor 41 are mounted in the sensor housing 31 so that these components can be handled together as a subassembly. The main drive gear 52 is attached to the input shaft of the pinion shaft 13. The yoke of the torque sensor 41 is attached to the output shaft of the pinion shaft 13. In this state, the distal end of the pinion shaft 13 is inserted into the subassembly of the TAS 24.

When the distal end of the pinion shaft 13 is inserted into the subassembly of the TAS 24, the driven gears 53, 54 are closer to the main drive gear 52 in the axial direction of the pinion shaft 13. Finally, the bottom portion 31a of the sensor housing 31 is fitted in the attachment hole 17a of the gear case 17, and the stepped portion 31b formed in the outer peripheral edge portion of the bottom portion 31a of the sensor housing 31 is in contact with the outer peripheral edge portion defining the attachment hole 17a of the gear case 17. At this time, the teeth of the driven gears 53, 54 mesh with the teeth of the main drive gear 52. In this state, bolts are inserted into the fastening portions of the sensor housing 31 and fastened to the gear case 17 to fix the sub-assembly of the TAS 24 to the gear case 17. Thereby completing the assembly of TAS 24.

When assembling the TAS 24, the following may occur. Upon insertion of the pinion shaft 13 into the subassembly of the TAS 24, depending on the rotational positions of the main drive gear 52 and the driven gears 53, 54, the teeth of the two driven gears 53, 54 may interfere with the teeth of the main drive gear 52 in the axial direction of the pinion shaft 13.

Therefore, in the present embodiment, the following configuration is adopted as a support structure for supporting the driven gears 53, 54 in the sensor housing 31. As shown in fig. 5, the driven gear 53 includes a gear portion 71 in a circular plate shape and a magnet holding portion 72 in a cylindrical shape. The outer diameter of the magnet holding portion 72 is smaller than the outer diameter of the gear portion 71. The magnet holding portion 72 is located at the center of the side surface of the gear portion 71. The side surface of the gear portion 71 is located on the side of the substrate 61 (i.e., the side surface is located on the viewer side in fig. 5). The driven gear 53 has a plurality of teeth 71a provided on the outer peripheral surface of the gear portion 71. The driven gear 53 also has a cylindrical holding hole 72a provided in a side surface of the magnet holding portion 72. The side surface of the magnet holding portion 72 is located on the side of the substrate 61. The permanent magnet 57 is fitted in the holding hole 72 a. Like the driven gear 53, the driven gear 54 has a gear portion 73 and a magnet holding portion 74. The driven gear 54 has a plurality of teeth 73a provided on the outer peripheral surface of the gear portion 73. The driven gear 54 also has a holding hole 74a provided in a side surface of the magnet holding portion 74. The side surface of the magnet holding portion 74 is located on the side of the substrate 61. The permanent magnet 58 is fitted in the holding hole 74 a.

As shown in fig. 2, an inclined surface 71b is formed on an end of each tooth 71a of the driven gear 53 on the side of the base plate 61. In the view shown in fig. 2, the inclined surface 71b of each tooth 71a is inclined such that the radial distance between the inclined surface 71b and the center of the driven gear 53 decreases in the direction toward the base plate 61. The driven gear 54 has a configuration similar to that of the driven gear 53. That is, as indicated by reference numerals in parentheses in fig. 2, an inclined surface 73b is formed on an end portion of each tooth 73a of the driven gear 54 on the side of the base plate 61. In the view shown in fig. 2, the inclined surface 73b of each tooth 73a is inclined such that the radial distance between the inclined surface 73b and the center of the driven gear 54 decreases in the direction toward the base plate 61. An inclined surface 52b is formed on an end portion (an upper end portion of each tooth 52a in fig. 2) of each tooth 52a of the main drive gear 52 opposite to the gear case 17. In the view shown in fig. 2, the inclined surface 52b of each tooth 52a is inclined such that the radial distance between the inclined surface 52b and the center of the main drive gear 52 decreases in a direction toward the side opposite to the gear case 17 (i.e., a direction away from the gear case 17).

As shown in fig. 5, the driven gears 53, 54 are rotatably supported in the sensor housing 31 (i.e., in the accommodation chamber 33) by a support member 55 having a rectangular plate shape. The support member 55 is mounted in the housing chamber 33 in a posture such that a long side surface of the support member 55 extends along a tangent of the main drive gear 52. The support member 55 has two support holes 81, 82. The support holes 81, 82 are formed in two corner portions 55d, 55e of the support member 55, where two short side surfaces 55a, 55b (upper and lower surfaces in fig. 5) of the support member 55 intersect with a long side surface 55c of the support member 55 on the side of the main drive gear 52 (i.e., a right side surface of the support member 55 in fig. 5) at the two corner portions 55d, 55 e. The support holes 81, 82 are long holes extending in the radial direction of the main drive gear 52. The support holes 81, 82 are formed such that the distance between the support holes 81, 82 increases in the direction away from the main drive gear 52.

As shown in fig. 2, the magnet holding portions 72, 74 of the driven gears 53, 54 are inserted into the support holes 81, 82. The magnet holding portions 72, 74 of the driven gears 53, 54 are inserted from the side of the support member 55 opposite to the base plate 61 (i.e., the magnet holding portions 72, 74 are inserted from the upper side in fig. 2), rather than being inserted into the support holes 81, 82 of the support member 55 from the side where the base plate 61 is provided. When the gear portions 71, 73 of the driven gears 53, 54 are in contact with the side surface of the support member 55 opposite to the base plate 61 (i.e., the upper surface of the support member 55 in fig. 2), the movement of the driven gears 53, 54 toward the base plate 61 is restricted. Thus, the distal end portions of the magnet holding portions 72, 74 (the end portions of the magnet holding portions 72, 74 opposite to the gear portions 71, 73) remain facing the magnetic sensors 62, 63 mounted on the substrate 61.

The driven gears 53, 54 can slide and rotate relative to the support member 55 via the gear portions 71, 73 (i.e., the driven gears 53, 54 are slidable and rotatable). The driven gears 53, 54 can move along the support holes 81, 82, respectively (i.e., the driven gears 53, 54 are movable). Each of the driven gears 53, 54 moves between a first position and a second position. The first position refers to a position where the magnet holding portions 72, 74 are engaged with first end portions (end portions closer to the main drive gear 52) of the support holes 81, 82, respectively. The second position refers to a position where the magnet holding portions 72, 74 are engaged with the second ends (ends farther from the main drive gear 52) of the support holes 81, 82, respectively.

A stopper 83 having a plate shape is provided on the support member 55 from the side of the support member 55 opposite to the base plate 61. The stopper 83 covers the side surfaces (upper surfaces of the driven gears 53, 54 in fig. 2) of the driven gears 53, 54 opposite to the base plate 61. When the gear portions 71, 73 contact the stopper 83, the movement of the driven gears 53, 54 toward the side opposite to the base plate 61 is restricted. The driven gears 53, 54 can slide and rotate relative to the stopper 83 via the gear portions 71, 73.

As shown in fig. 3, a support portion 84 having a cylindrical shape is provided on a side surface of the support member 55 opposite to the substrate 61 (a side surface of the support member 55 on the viewer side in fig. 3). The support portion 84 is located between the two support holes 81 and 82 in the long side direction of the support member 55. A coil torsion spring 85 is attached to the support portion 84.

As shown in fig. 5, the coil torsion spring 85 includes a coil portion 85a, a first arm 85b, and a second arm 85 c. The support portion 84 is inserted into the coil portion 85 a. The first arm 85b is engaged with a portion of the magnet holding portion 72 of the driven gear 53 opposite to the main drive gear 52. The second arm 85c engages with a portion of the magnet holding portion 74 of the driven gear 54 opposite to the main drive gear 52. Each of the driven gears 53, 54 is always biased toward the main drive gear 52 by the elastic force of the helical torsion spring 85. When the magnet holding portions 72, 74 are engaged with the first ends (ends closer to the main drive gear 52) of the support holes 81, 82, the movement of the driven gears 53, 54 toward the main drive gear 52 is restricted.

Next, the function of the support structure for the driven gears 53, 54 will be described. When the pinion shaft 13 is inserted into the sub-assembly of the TAS 24, when the teeth 52a of the main drive gear 52 are located at positions corresponding to the tooth grooves (spaces (grooves) between the teeth) of the driven gears 53, 54 in the rotational direction of the main drive gear 52 and the driven gears 53, 54, the teeth 52a of the main drive gear 52 smoothly enter the tooth grooves of the driven gears 53, 54 in the axial direction of the pinion shaft 13. In this case, the teeth 52a of the main drive gear 52 mesh with the teeth 71a, 73a of the driven gears 53, 54.

On the other hand, when the pinion shaft 13 is inserted into the subassembly of the TAS 24, the following event occurs in the case where the teeth 52a of the main drive gear 52 are not located at positions corresponding to the tooth grooves of the driven gears 53, 54 in the rotational direction of the main drive gear 52 and the driven gears 53, 54.

As shown in fig. 6A, as the pinion shaft 13 is inserted into the sub-assembly of the TAS 24, the teeth 71a, 73a of the driven gears 53, 54 come closer to the teeth 52a of the main drive gear 52. The inclined surfaces 71b, 73b of the teeth 71a, 73a of the driven gears 53, 54 eventually contact the inclined surface 52b of the teeth 52a of the main drive gear 52 in the axial direction of the pinion shaft 13.

As shown in fig. 6B, when the pinion shaft is further pushed in the subassembly of the TAS 24, a force acting on the driven gears 53, 54 in the axial direction of the pinion shaft 13 (a force attempting to move the subassembly of the TAS along the pinion shaft 13) is converted into a force in a direction to move the driven gears 53, 54 away from the main drive gear 52 due to the engagement between the inclined surfaces 71B, 73B of the teeth 71a, 73a and the inclined surface 52B of the tooth 52 a. This is because the pinion shaft 13 supported by the gear case 17 and the main drive gear 52 cannot move in the radial direction. Accordingly, the inclined surfaces 71b, 73b of the teeth 71a, 73a are guided laterally relative to the main drive gear 52 by the inclined surface 52b of the tooth 52a, and the driven gears 53, 54 are moved in a direction away from the main drive gear 52 against the elastic force of the helical torsion spring 85.

After the driven gears 53, 54 are moved in the direction away from the main drive gear 52 to a position where the inclined surfaces 71B, 73B of the driven gears 53, 54 are disengaged from the inclined surface 52B of the main drive gear 52, as the pinion shaft 13 is further inserted in the subassembly of the TAS 24, the driven gears 53, 54 are relatively moved in the direction in which the subassembly of the TAS 24 is moved relative to the pinion shaft 13 (downward direction in fig. 6B). The driven gears 53, 54 are finally relatively moved to a position such that the teeth 71a, 73a of the driven gears 53, 54 are located at the same position as the teeth 52a of the main drive gear 52 in the radial direction, or to a position such that the teeth 71a, 73a of the driven gears 53, 54 face the teeth 52a of the main drive gear 52 in the radial direction. Even during this movement, the driven gears 53, 54 are biased toward the main drive gear 52 by the elastic force of the helical torsion spring 85. Therefore, in the case where the teeth 71a, 73a of the driven gears 53, 54 are not located at the positions corresponding to the tooth grooves of the main drive gear 52, the teeth 71a, 73a of the driven gears 53, 54 slide with respect to the teeth 52a of the main drive gear 52 (contact the teeth 52a of the main drive gear 52). When the rotational positions of the driven gears 53, 54 are changed during this process and the teeth 71a, 73a of the driven gears 53, 54 are located at positions corresponding to the tooth grooves of the main drive gear 52, the driven gears 53, 54 are moved toward the main drive gear 52 by the elastic force of the coil torsion spring 85.

As shown in fig. 6C, the teeth 71a, 73a of the driven gears 53, 54 thus enter the tooth grooves of the main drive gear 52 in the radial direction, and thus, the teeth 71a, 73a of the driven gears 53, 54 mesh with the teeth 52a of the main drive gear 52 in the rotational direction.

As described above, even in the case where the teeth of the driven gears 53, 54 interfere with the teeth of the main drive gear 52 in the axial direction of the pinion shaft 13 when the pinion shaft 13 is inserted into the subassembly of the TAS 24, the subassembly of the TAS 24 can be attached to the gear case 17 in an appropriate manner, that is, the driven gears 53, 54 are meshed with the main drive gear 52, by simply inserting the pinion shaft 13 into the subassembly of the TAS 24. When the pinion shaft 13 is inserted into the subassembly of the TAS 24, it is not necessary to perform, for example, adjustment of the rotational positions of the driven gears 53, 54.

The effects of the present embodiment will be described. According to the present embodiment, the following effects can be obtained. (1) In the event that the teeth of the driven gears 53, 54 interfere with the teeth of the main drive gear 52 in the axial direction of the pinion shaft 13 when the pinion shaft 13 is inserted into the subassembly of the TAS 24, the driven gears 53, 54 move in the direction away from the main drive gear 52 due to the engagement between the inclined surfaces 71b, 73b of the driven gears 53, 54 and the inclined surface 52b of the main drive gear 52. With such a configuration, the pinion shaft 13 may be pushed further within the sub-assembly of the TAS 24 while avoiding damage to the teeth 52a of the main drive gear 52 or the teeth 71a, 73a of the driven gears 53, 54. When the pinion shaft 13 is inserted in the sub-assembly of the TAS 24 to a position such that the teeth 71a, 73a of the driven gears 53, 54 are located corresponding to the tooth grooves (spaces between the teeth 52a) of the main drive gear 52, the driven gears 53, 54 move toward the main drive gear 52 by the elastic force of the coil torsion spring 85. Therefore, the teeth 71a, 73a of the driven gears 53, 54 mesh with the teeth 52a of the main drive gear 52. Since the assembly of the TAS 24 (the operation of inserting the pinion shaft 13 into the subassembly of the TAS 24) is not hindered by interference between the teeth of the driven gears 53, 54 and the teeth of the main drive gear 52, the TAS 24 is smoothly assembled.

(2) When the driven gears 53, 54 interfere with the main drive gear 52 in the axial direction of the pinion shaft 13 during assembly of the TAS 24, a force acting on the driven gears 53, 54 in the axial direction of the pinion shaft 13 (an axial force parallel to the axial direction of the pinion shaft 13) is converted into a force in a direction to move the driven gears 53, 54 away from the main drive gear 52 due to engagement between the inclined surfaces 71b, 73b of the driven gears 53, 54 and the inclined surface 52b of the main drive gear 52. Since the inclined surfaces 71b, 73b are simply formed in the driven gears 53, 54 and the inclined surface 52b is simply formed in the main drive gear 52, the configurations of the driven gears 53, 54 and the main drive gear 52, and thus the configuration of the TAS 24, are simplified.

(3) The two driven gears 53, 54 are always biased toward the main drive gear 52 by the first arm 85b and the second arm 85c of the coil torsion spring 85. Since only one coil torsion spring 85 is provided, the increase in the number of parts of the TAS 24 is limited.

(4) The torque sensor 41 and the rotation angle sensor 51 are mounted in the sensor housing 31. Therefore, not only the rotation angle of the pinion shaft 13 but also the torque acting on the pinion shaft 13 can be detected by a single sensor (TAS 24).

(5) The rotation angle sensor 51 of the TAS 24 detects the rotation angle of the main drive gear 52 by detecting the rotation of the two driven gears 53, 54 meshed with the main drive gear 52. Accordingly, especially when the main drive gear 52 starts to rotate, or when the rotation direction of the main drive gear 52 is reversed, the backlash caused by the backlash at two positions, i.e., the backlash between the main drive gear 52 and the driven gear 53 and the backlash between the main drive gear 52 and the driven gear 54, may affect the calculation accuracy of the rotation angle of the main drive gear 52. In this regard, according to the present embodiment, in the assembled TAS 24, the driven gears 53, 54 are held pressed against the main drive gear 52 by the elastic force of the helical torsion spring 85. Therefore, the backlash between the teeth 71a, 73a of the driven gears 53, 54 and the teeth 52a of the main drive gear 52 is further reduced. Therefore, since the backlash due to the backlash is reduced, the calculation accuracy of the rotation angle of the main drive gear 52 is improved.

The present embodiment may be modified as follows. The main drive gear 52 may not have the inclined surface 52b, or the driven gears 53, 54 may not have the inclined surfaces 71b, 73 b. At least one of the main drive gear 52 and the driven gears 53, 54 needs to have an inclined surface. Also in this configuration, when the teeth 71a, 73a of the driven gears 53, 54 interfere with the teeth 52a of the main drive gear 52 in the axial direction of the pinion shaft 13 during assembly of the TAS 24, the force acting on the driven gears 53, 54 in the axial direction of the pinion shaft 13 can be converted into a force in a direction to move the driven gears 53, 54 away from the main drive gear 52.

The main drive gear 52 may have an arc-shaped curved surface instead of the inclined surface 52 b. The driven gears 53, 54 may have arc-shaped curved surfaces instead of the inclined surfaces 71b, 73 b. Also in this configuration, when the teeth 71a, 73a of the driven gears 53, 54 interfere with the teeth 52a of the main drive gear 52 in the axial direction of the pinion shaft 13 during assembly of the TAS 24, the force acting on the driven gears 53, 54 in the axial direction of the pinion shaft 13 can be converted into a force in a direction to move the driven gears 53, 54 away from the main drive gear 52.

In the above embodiment, the TAS 24 is described as an example of the sensor. However, the sensor may be a pure rotation angle sensor 51, i.e. TAS 24 omitting the torque sensor 41. This simple rotation angle sensor 51 can solve a problem similar to that solved by the TAS 24.

A configuration with a single driven gear 53 or 54 may be used for the TAS 24 or a simple rotational angle sensor. Configurations with three or more driven gears may be used for the TAS 24 or simple rotational angle sensor.

In the above embodiment, the device mounted with the TAS 24 or the simple rotation angle sensor is a steering device of a vehicle. However, the present invention may be applied to other in-vehicle devices having a shaft (rotation shaft). The TAS 24 or simple rotation angle sensor is not limited to the TAS 24 mounted in the vehicle or the simple rotation angle sensor mounted in the vehicle.