Throttle device

Abstract

To attain stable operational feeling while securing durability.SOLUTION: A rotor 40 includes a first projecting part 10 and a second projecting part 20 that project to a cover 60 side. A single friction pin 50 energizes the rotor 40 to the cover 60 side to generate friction. A sensor substrate 37 detects a rotating angle of the rotor 40. A predetermined arc region A1 has a range of a first angle θ1 that includes a maximum angle range θMAX of the rotor 40 enabling abutment on the friction pin 50 through rotation of the rotor 40 and that is less than 180°. The first projecting part 10 is provided to abut on the cover 60 at least at two points (PA, PB) at both end positions of the predetermined arc region A1. The second projecting part 20 is provided to abut on the cover 60 at least at one point (point PC) within the range of the second angle θ2. A first distance R1 is larger than a second distance RP (RP<R1).SELECTED DRAWING: Figure 5

Description

Technical Field

[0001] This technology relates to a throttle device.

Background Art

[0002] Conventionally, a throttle device that detects an operation of a throttle grip by a driver of a straddle-type vehicle and outputs it as an electrical signal is known. In this type of throttle device, some provide a good operating feeling by friction.

[0003] For example, in Patent Document 1, two friction pins are arranged to face each other with the center of rotation therebetween, and friction is generated by biasing a rotor toward the cover side.

[0004] In Patent Document 2, as a configuration corresponding to the friction pin, a set of a spring and a pressing component is provided, and miniaturization is achieved.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Patent Document 2

Summary of the Invention

Problems to be Solved by the Invention

[0006] However, in Patent Document 2, due to the reaction force associated with the biasing force of the spring and the pressing component, a rotational moment other than around the rotation axis acts on the interlocking member (rotor), and the force acting on the sliding portion between the interlocking member and the case may become uneven. As a result, depending on the quality of the product, variations may occur in the frictional force (operating feeling), or uneven wear may occur due to the uneven frictional force, which may reduce the operating durability performance. Therefore, there is room for improvement from the viewpoint of ensuring both durability and stability of the operating feeling.

[0007] The present technology aims to achieve a stable operating feel while ensuring durability.

Means for Solving the Problem

[0008] To achieve the above object, the throttle device of the present technology includes a case, a cover fixed to the case, a rotor that rotates relative to the case about a rotation center and has a first convex portion and a second convex portion that project toward the cover side in the axial direction of the rotation center, a single friction pin that is held by the case and generates friction by urging the rotor toward the cover side in the axial direction, and a detection unit that detects the rotation angle of the rotor. The first convex portion is provided so as to contact the cover at at least two points at both end positions of a predetermined arc region having a first angular range of less than 180° that includes the maximum angular range of the rotor where the first convex portion can contact the friction pin by the rotation of the rotor about the rotation center. The second convex portion is provided so as to contact the cover at at least one point within a second angular range that faces the first angular range with the rotation center interposed therebetween. A first distance in the radial direction from the rotation center to the predetermined arc region is larger than a second distance in the radial direction from the rotation center to the friction pin.

Advantages of the Invention

[0009] According to the present technology, a stable operating feel can be achieved while ensuring durability.

Brief Description of the Drawings

[0010]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Embodiments for Carrying Out the Invention

[0011] Hereinafter, embodiments of the present technology will be described with reference to the drawings.

[0012] FIG. 1 is a front perspective view showing the configuration around the handlebar of a saddle-riding type vehicle to which a throttle device according to an embodiment of the present technology is applied. A motorcycle is exemplified as the saddle-riding type vehicle. In FIG. 1, the right side portion of the handlebar 31 is shown.

[0013] At the right end of the handlebar 31 of the motorcycle, a throttle device 100 and a throttle pipe 33 are arranged. A grip 32 is attached to the outer peripheral surface of the throttle pipe 33. When the grip 32 is rotationally operated by the driver, the throttle pipe 33 rotates in conjunction therewith. The axial direction of the throttle pipe 33 is defined as the direction RH, and the tip side of the throttle pipe 33 is defined as the +RH side in the direction RH. The rotor 40 (described later in FIGS. 2 to 5) of the throttle device 100 is arranged to rotate integrally with the throttle pipe 33, and the rotation angle (or rotation amount) of the throttle pipe 33 can be detected by the throttle device 100.

[0014] FIG. 2 is an exploded perspective view of the throttle device 100. The throttle device 100 mainly includes a cover 60, a rotor 40, a case 30, and a return spring 70.

[0015] FIG. 3 is a longitudinal sectional view of the throttle device 100 taken along a cross section parallel to the direction RH. FIG. 4 is a perspective view of a part of the throttle device 100. In FIG. 4, the illustration of the cover 60 is omitted.

[0016] As shown in FIG. 2, in the throttle device 100, a return spring 70 and a rotor 40 are disposed in a case 30, and a cover 60 is fixedly attached to the case 30 from the +RH side. As an example, the cover 60 is made of, for example, metal, and the case 30 and the rotor 40 are made of, for example, resin.

[0017] The rotor 40 has a protrusion 44 that protrudes toward the -RH side (FIGS. 2 and 4). The case 30 is formed with a housing chamber 39 that houses the protrusion 44 (FIGS. 2 and 3).

[0018] The rotor 40 is engaged with a throttle pipe 33 and rotates integrally with the throttle pipe 33 relative to the case 30 about a rotation center C0. The counterclockwise direction as viewed from the +RH side is the forward rotation direction FF of the rotor 40. A second contact portion 42 is provided at an end of the protrusion 44 in the forward rotation direction FF of the rotor 40, and a first contact portion 41 is provided at an end of the protrusion 44 in the reverse rotation direction (FIG. 4). In the rotation stroke of the rotor 40, the protrusion 44 moves within the housing chamber 39.

[0019] As shown in FIG. 2, the return spring 70 is engaged with the -RH side of the rotor 40. The case 30 is provided with a locking projection 36. A first locking portion 71 of the return spring 70 is locked to the locking projection 36. A second locking portion 72 of the return spring 70 is engaged with an end face (near the second contact portion 42) of the protrusion 44 in the forward rotation direction FF (FIG. 4). Thereby, the return spring 70 biases the rotor 40 rotated in the forward rotation direction FF in the direction of closing the throttle pipe 33, that is, in the reverse rotation direction.

[0020] As shown in FIG. 2, a first regulating portion 34 and a second regulating portion 35 are provided in the case 30. The rotation angle of the rotor 40 in the forward rotation direction FF is regulated by the second contact portion 42 (FIG. 4) coming into contact with the second regulating portion 35. On the other hand, the rotation angle of the rotor 40 in the reverse rotation direction is regulated by the first contact portion 41 (FIG. 4) coming into contact with the first regulating portion 34. Therefore, the maximum angular range θMAX (described later in FIG. 5) of the rotatable rotor 40 is regulated by the first regulating portion 34 and the second regulating portion 35.

[0021] A sensor substrate 37 (detection portion) is fixed to the case 30 (FIG. 2). A magnet 43 is fixed to the rotor 40 (FIG. 4). The magnet 43 is configured in an arc shape centered on the rotation center C0 and rotates integrally with the rotor 40. A magnetic flux detection device (not shown) composed of a Hall sensor, an MR (magnetoresistive) sensor, etc. is attached to the sensor substrate 37. The sensor substrate 37 detects the rotation angle of the rotor 40 from the change in the magnetic flux of the magnet 43.

[0022] As shown in FIG. 3, a housing portion 38 is formed in the case 30, and a single friction pin 50 is held in the housing portion 38. The housing portion 38 is formed in an oval shape when viewed from the +RH side, and the friction pin 50 is restricted from moving in the circumferential direction and the radial direction centered on the rotation center C0 with respect to the case 30.

[0023] A coil spring 51 is inserted into the friction pin 50. The -RH side end of the coil spring 51 abuts against the bottom surface of the housing portion 38. In a state where the cover 60 and the rotor 40 are attached to the case 30, the +RH side end of the friction pin 50 abuts against the rotor 40, and the coil spring 51 is in a compressed state.

[0024] Therefore, due to the biasing force of the coil spring 51, the friction pin 50 biases the rotor 40 toward the +RH side. In other words, the rotor 40 is elastically sandwiched between the friction pin 50 and the cover 60. The friction pin 50 generates friction (frictional force) between the rotor 40 and the cover 60 to provide a good operating feel. Note that the coil spring 51 is an example of an elastic member.

[0025] As shown in FIGS. 2 and 3, the rotor 40 has a first convex portion 10 and a second convex portion 20 that protrude toward the cover 60 side (+RH side) in the axial direction of the rotation center C0 as sliding portions that slide with respect to the cover 60. The first convex portion 10 and the second convex portion 20 are provided in an arc shape (a predetermined arc region A1) and an arc shape A2 that are continuous in the circumferential direction centered on the rotation center C0, respectively. The detailed configurations of the first convex portion 10 and the second convex portion 20 will be described with reference to FIG. 5.

[0026] FIG. 5 is a schematic diagram of the rotor 40 and the like as viewed from the +RH side. It is the rotor 40 that actually rotates, and the position of the friction pin 50 does not change. As the rotor 40 rotates, the contact position of the friction pin 50 with respect to the rotor 40 changes. FIG. 5 relatively shows the contact position of the friction pin 50 with respect to the rotor 40. As described above, the rotor 40 is rotatable within an angular range in which it contacts the first restricting portion 34 or the second restricting portion 35, and this angular range is the maximum angular range θMAX of the rotor 40 that can contact the friction pin 50 due to the rotation of the rotor 40.

[0027] The rotor 40 is in the neutral position when the grip 32 is not being rotated. In the neutral position, the rotor 40 is not biased by the return spring 70 and can be rotated slightly not only in the forward rotation direction FF but also in the reverse rotation direction. The position of the friction pin 50 that abuts on the rotor 40 in the neutral position is shown as the friction pin 50-N. The position of the friction pin 50 that abuts on the rotor 40 at the maximum rotation position in the forward rotation direction FF is shown as the friction pin 50-F. The position of the friction pin 50 that abuts on the rotor 40 at the maximum rotation position in the reverse rotation direction is shown as the friction pin 50-R.

[0028] The first angle θ1 is an angle range less than 180° that includes the maximum angle range θMAX. The first convex portion 10 is provided in an arc shape that is continuous over the entire predetermined arc region A1 at the first angle θ1. The angle range that faces the rotation center C0 across the first angle range θ1 is the second angle θ2. The second convex portion 20 is provided in an arc shape A2 that is continuous within the range of the second angle θ2 with the rotation center C0 as the center. Note that the magnet 43 (FIG. 4) is arranged within a predetermined arc region A1 in the circumferential direction, contributing to miniaturization.

[0029] As shown in FIGS. 3 and 5, the distance in the radial direction from the rotation center C0 to the predetermined arc region A1 is defined as the first distance R1. The distance in the radial direction from the rotation center C0 to the center of the friction pin 50 is defined as the second distance RP. The distance in the radial direction from the rotation center C0 to the second convex portion 20 (arc shape A2) is defined as the third distance R2.

[0030] The first distance R1 is greater than the second distance RP (RP < R1). If R1 < RP, a rotational moment that causes the second convex portion 20 to move away from the cover 60 acts about the first convex portion 10 as a fulcrum, and the sliding between the second convex portion 20 and the cover 60 may become unstable. However, since RP < R1, the first convex portion 10 and the second convex portion 20 slide stably with respect to the cover 60. As a result, a stable operating feeling can be realized while ensuring durability. Further, since both the convex portions 10 and 20 have a continuous arc shape, stable friction can be obtained.

[0031] As shown in FIG. 5, virtual lines connecting both ends (the centers of the friction pins 50-F and 50-R) of the first angle range θ1 and the rotation center C0 are straight lines LF and LR, respectively. Since the second angle θ2 is opposite to the first angle range θ1, in the entire stroke of the rotation of the rotor 40, the second convex portion 20 is located on an extension of a virtual line (a line belonging to these ranges bounded by the straight lines LF and LR) connecting the first convex portion 10 and the rotation center C0 in the radial direction. Thereby, since the convex portions 10 and 20 bias both side positions of the cover 60 in the radial direction with the rotation center C0 interposed therebetween, stable friction can be obtained.

[0032] Here, from the viewpoint of realizing a stable operating feeling while ensuring durability, it is not essential that both the convex portions 10 and 20 have an arc shape. For example, the first convex portion 10 may be provided so as to contact the cover 60 at at least two points (point PA and point PB) at both end positions of a predetermined arc region A1 among the predetermined arc region A1. That is, a plurality of protruding portions (portions that contact at points) constituting the first convex portion 10 may be arranged in the circumferential direction in the predetermined arc region A1. That is, contact may be made at three or more intermittent points. On the other hand, the second convex portion 20 may be provided so as to contact the cover 60 at at least one point (for example, point PC) within the range of the second angle θ2.

[0033] The maximum angle range θMAX, the first angle θ1, and the second angle θ2 are determined assuming a configuration in which the first convex portion 10 contacts the cover 60 at two points (point PA and point PB) and the second convex portion 20 contacts the cover 60 at one point (point PC) as described above.

[0034] First, the first convex portion 10 needs to contact the cover 60 at at least two points (PA, PB) at both end positions of a predetermined arc region A1. In order to contact the cover 60 at the two points PA and PB which are the both end positions of the predetermined arc region A1, it is necessary that the angular range of the predetermined arc region A1 is equal to or greater than the maximum angular range θMAX. Therefore, the first angle θ1 is set to an angular range that includes the maximum angular range θMAX. Further, in order for the rotor 40 to stably contact the cover 60 at the three points PA, PB, and PC, it is necessary that the rotation center C0 is located within the triangle connecting the three contact points (PA, PB, PC). Therefore, the first angle θ1 is set to be less than 180°.

[0035] Also, when the second convex portion 20 contacts the cover 60 at a single point PC, the point PC needs to contact the cover 60 within the second angle θ2. In this case as well, the position of the point PC only needs to be within the second angle θ2 and does not necessarily have to be on the arc shape A2.

[0036] By the way, the third distance R2 is smaller than the first distance R1. This contributes to the miniaturization of the product. That is, since the friction pins 50, the magnets 43, and the restricting portions 34 and 35 are collectively arranged on the side of the predetermined arc region A1, there is no need to arrange these elements within the second angle θ2. As a result, particularly on the side of the second convex portion 20, it becomes easy to miniaturize the outer diameters of the rotor 40 and the case 30. The effect is further enhanced because the third distance R2 is smaller than the second distance RP.

[0037] According to the present embodiment, the first convex portion 10 is provided so as to contact the cover 60 at at least two points (PA, PB) at both end positions of a predetermined arc region A1, and the second convex portion 20 is provided so as to contact the cover 60 at at least one point (point PC) within the range of the second angle θ2. The first distance R1 is larger than the second distance RP. Thereby, it is possible to realize a stable operating feeling while ensuring durability.

[0038] In particular, the first convex portion 10 is provided in an arc shape that is continuous across the entire predetermined arc region A1, and the second convex portion 20 is provided in an arc shape A2 that is continuous within the range of the second angle θ2. Moreover, throughout the entire rotation stroke of the rotor 40, the second convex portion 20 is positioned on the extension of the virtual straight line connecting the first convex portion 10 and the rotation center C0 in the radial direction. Thereby, more stable friction can be obtained.

[0039] Also, the magnet is disposed within the predetermined arc region A1. Also, the third distance R2 is smaller than the first distance R1 and smaller than the second distance (RP). Thereby, it contributes to miniaturization.

[0040] As described above, the present technology has been described in detail based on its preferred embodiments. However, the present technology is not limited to these specific embodiments, and various forms within the scope not departing from the gist of this technology are also included in the present technology.

Explanation of Reference Numerals

[0041] 10 First convex portion, 20 Second convex portion, 37 Sensor substrate, 40 Rotor, 50 Friction pin, 60 Cover, 100 Throttle device, A1 Predetermined arc region, θMAX Maximum angle range, θ1 First angle, θ2 Second angle, PA, PB, PC Points, R1 First distance, RP Second distance, R2 Third distance

Claims

1. A case, a cover fixed to the case, a rotor that rotates relative to the case about a rotation center and has a first convex portion and a second convex portion that protrude toward the cover side in the axial direction of the rotation center, a single friction pin that is held by the case and generates friction by biasing the rotor toward the cover side in the axial direction, a detection unit that detects the rotation angle of the rotor, and the first convex portion is provided so as to contact the cover at at least two points at both end positions of a predetermined arc region having a first angle range of less than 180° that includes the maximum angle range of the rotor that can contact the friction pin due to the rotation of the rotor about the rotation center, the second convex portion is provided so as to contact the cover at at least one point within a second angle range that faces the first angle range with the rotation center therebetween, a throttle device in which a first distance in the radial direction from the rotation center to the predetermined arc region is greater than a second distance in the radial direction from the rotation center to the friction pin.

2. The throttle device according to claim 1, wherein the first convex portion is provided in an arc shape that is continuous over the entire predetermined arc region.

3. The throttle device according to claim 2, wherein the second convex portion is provided in an arc shape that is continuous within the second angle range about the rotation center.

4. The throttle device according to claim 3, wherein the second convex portion is located on an extension of a virtual straight line connecting the first convex portion and the rotation center in the radial direction throughout the entire rotation stroke of the rotor.

5. comprising a magnet that rotates integrally with the rotor and is used for detecting the rotation angle, the throttle device according to claim 1, wherein the detection unit is fixed to the case.

6. The throttle device according to claim 5, wherein the magnet is disposed within the predetermined arc region.

7. The throttle device according to claim 1, wherein a third distance in the radial direction from the rotation center to the second convex portion is smaller than the first distance.

8. The throttle device according to claim 1, wherein a third distance in the radial direction from the rotation center to the second convex portion is smaller than the second distance.

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