JPH0735164A - One-way clutch - Google Patents

Abstract

PURPOSE:To embody the promotion of miniaturization and lightweightiness in forming a jaw type one-way clutch, using no steel ball and reduce the manhour necessary for assembling. CONSTITUTION:An engaging tooth 33 is formed in an outer ring 34, installing each jaw piece 35 in an inner ring 32, and plural pieces of projections 37 slidingly contacting with this engaging tooth 33 are formed along the circumferential direction. With this constitution, it is so structured to support the outer ring 34 free of rotation by these projections 37. Thus, each projection 37 serves as a bearing in substance, whereby a steel ball falls into disuse. Therefore, a steel ball installing space is omitted and miniaturization is made achievable and the lightweightiness and cost reduction are well promotable in this way. In this connection, as both these inner and outer rings 32 and 34 are separately assembled, manhours necessary for assembling are thus reducible.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a one-way clutch in which a claw piece biased by a spring toward an engaging tooth is interposed between an outer ring member and an inner ring member.

[0002]

As a conventional one-way clutch of this type, there is, for example, a freewheel for bicycles. This free wheel allows the rear wheels to rotate without turning the pedal when the bicycle is run by inertia. This bicycle freewheel will be described with reference to FIG.

FIG. 10 is a view showing a bicycle freewheel as a conventional one-way clutch. FIG. 10A is a partially enlarged side view, and FIG. 10B is an X side view in FIG.
It is a X-ray sectional view. In these drawings, 101 is an inner wheel fixed to a bicycle rear wheel (not shown), 102 is a sprocket as an outer wheel around which a rear wheel drive chain (not shown) is wound, and the sprocket 102 is a steel ball. 1
It is rotatably supported on the outer peripheral portion of the inner ring 101 via 03. Further, the sprocket 102 has an engagement tooth 104 formed in the axially central portion of the inner peripheral portion. The steel balls 103 are attached to the inner peripheral portion of the sprocket 102 on both sides in the axial direction of the engaging teeth 104.

Reference numeral 105 denotes a claw piece that engages with the engagement tooth 104. The claw piece 105 is mounted on the outer peripheral portion of the inner ring 101, and the engaging portion 105a is provided at the inner ring 101 by a spring (not shown).
Is urged radially outward with respect to. 106 is the inner ring 1
This steel ball pressing member 1 is a steel ball pressing member screwed to 01.
By changing the screwing position of the No. 06 with respect to the inner ring 101, the clearances between the steel balls 103 located on both sides of the engaging teeth 104 and the respective contact surfaces can be adjusted. Note that the steel balls 103 are arranged on both sides of the engaging teeth 104 in this manner because the sprocket 102 is attached to the inner ring 10
1 rotatably supported by the sprocket 1
This is because the axial center of 02 matches the axial center of the inner ring 101.

In the free wheel for a bicycle constructed as described above, the claw piece 105 is generated by rotating the sprocket 102 clockwise with respect to the inner ring 101 in FIG. 10 (a).
Engages with the engaging teeth 104, and power is transmitted from the chain to the rear wheels. On the other hand, when the inner wheel 101 rotates clockwise with respect to the sprocket 102 together with the rear wheel, the claw piece 10
Sprocket 10 for sliding 5 along engagement teeth 104
No power is transmitted to 2.

[0006]

However, the free wheel for a bicycle constructed as described above has a limit in reducing its size and weight. This is because the steel balls 103 are arranged on both sides of the engaging teeth 104 as shown in FIG. 10B, and the mounting space for the steel balls 103 must be secured in the axial direction and the radial direction. .

When the free wheel is mounted on the rear wheel, the free wheel itself must be preassembled so that the steel ball 103 does not drop out from between the inner ring 101 and the sprocket 102, which requires a lot of man-hours. There was also the problem of taking it.

The present invention has been made in order to solve such a problem, and a claw type one-way clutch is formed without using a steel ball to reduce the size and weight of the one-way clutch and to install the clutch. The purpose is to reduce man-hours.

[0009]

SUMMARY OF THE INVENTION A one-way clutch according to the present invention has an engagement tooth formed on one of an outer ring member and an inner ring member, and the other side of which has a sliding contact protrusion slidably contacting the top of the engaging tooth. A plurality of parts are formed in the circumferential direction, and the sliding contact projection rotatably supports the member on the engagement tooth side.

[0010]

Since the sliding contact protrusion serves as a substantial bearing, the steel ball is not required when the outer ring member and the inner ring member are rotatably provided to each other.

[0011]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described in detail below with reference to FIGS. This embodiment shows an example in which the one-way clutch according to the present invention is incorporated in an auxiliary power unit for an electric bicycle. 1 is a side view of an electric bicycle in which a one-way clutch according to the present invention is incorporated in an auxiliary power unit, FIG. 2 is an enlarged plan view of a part of the electric bicycle, and FIG. 3 is a side view of a power unit and a motor. 4 is a sectional view taken along line IV-IV of the power unit in FIG. 3, FIG. 5 is a sectional view taken along line VV of the one-way clutch according to the present invention in FIG. 4, and FIG. 6 is shown in FIG.
VI-VI sectional view, FIG. 7 is an enlarged perspective view showing an essential part of the one-way clutch according to the present invention, FIG. 8 is an enlarged side view showing a battery case mounting portion, and FIG. 9 is power of an electric bicycle. It is a figure which shows a transmission path.

In these figures, 1 is an electric bicycle, 2
Is a frame of the electric bicycle 1. This frame 2
Is a front fork 4 having a front wheel 3 rotatably provided.
And a down tube 2b that extends rearward and downward from the head pipe 2a that supports the vehicle in a steerable manner.
A seat tube 2c connected to the rear portion of the down tube 2b through the middle lug 5 and a hanger lug 6 at the rear end of the down tube 2b extending rearward from the middle lug 5.
A pair of left and right chain stays 2d connected via
The upper part of the seat tube 2c and the chain stay 2
It is composed of a pair of left and right seat stays 2e and the like connecting the rear end portion of d.

A steering handle 7 is attached to the upper end of the front fork 4. A rear wheel bracket 2f for rotatably supporting the rear wheel 8 is integrally provided at the rear end of the chain stay 2d and the lower end of the seat stay 2e.

Reference numeral 9 denotes an auxiliary power unit for the electric bicycle 1.
The one-way clutch according to the present invention is attached to the auxiliary power unit 9. The auxiliary power unit 9 is supplied with electric power from a battery 11 housed in a battery case 10 and also has a motor 12 controlled by a control unit described later,
It includes a power unit 14 having a crankshaft 13, a crank gear 15 (FIG. 4) mounted on the right end of the vehicle body of the crankshaft 13, a crank 16 and a pedal 17.

In the auxiliary power unit 9, the power unit 14 is formed around the crankshaft 13, and the motor 12 is arranged in front of the crankshaft 13 and below the downtube 2b along the downtube 2b. It is connected to the middle lug 5 and the hanger lug 6 via connecting brackets 18 and 19. In the embodiment, the auxiliary power unit 9 is mounted on the frame 2 such that a rotation shaft 12a of the motor 12 described later is parallel to the down tube 2b.

In the auxiliary power unit 9, a crank gear 15 located on the right side of the vehicle body is connected to a free wheel (not shown) of the rear wheel 8 via a chain 20. The free wheel is composed of a known one-way clutch that transmits power only from the chain 20 to the rear wheel 8. In addition, in FIG. 1, a reference numeral 20a provided along the chain 20 is a chain cover.

A control unit 21 and a main switch 22 mounted on the down tube 2b are connected to the motor 12 of the auxiliary power unit 9. The control unit 21 rotates the motor 12 so that the crankshaft 13 receives the power from the motor 12 only when the pedal 17 exerts a pedaling force on the crankshaft 13 when the main switch 22 is in the ON state. Is configured to convey. That is, when the pedal 17 is stepped on, the crankshaft 13 is provided with a rotational torque from the motor 12 in addition to the pedaling force. The output of this motor 12 is the pedal 1
It is controlled by the control unit 21 so as to be approximately proportional to the pedaling force applied to 7. The pedaling force is detected by a pedaling force detection mechanism in the power unit 14, which will be described later.

The mounting positions of the control unit 21 and the main switch 22 are below the down tube 2b and in front of the motor 12. Therefore, the main switch 22, the control unit 21, the motor 1
2 and the power unit 14 will be arranged in a line in the front-back direction along the down tube 2b.

When a key (not shown) is inserted and the main switch 22 is turned clockwise, for example, from the neutral position in FIG. 1, the control unit 21 and the battery 1 are turned on.
1 and 1 are electrically connected to each other, and when rotated counterclockwise, a lock mechanism for a battery case described later is released.

Here, the structure of the above-described auxiliary power unit 9 will be described in more detail with reference to FIGS. The auxiliary power unit 9 rotatably supports the crankshaft 13 in the case 23 of the power unit 14, fixes the motor 12 at one end of the case 23 so that the axial direction thereof is orthogonal to the crankshaft 13, and Shaft 13 and motor 1
A planetary gear type speed reducer 24, a planetary roller type speed reducer 25, etc. are interposed between the two rotary shafts 12a.
Further, in this auxiliary power unit 9, all of the rotating parts arranged coaxially with the crankshaft 13 have an outer diameter smaller than that of the crank gear 15 for the purpose of downsizing and ensuring a minimum ground clearance.

As shown in FIG. 4, the case 23 has a cylindrical portion through which the crankshaft 13 penetrates and which houses the planetary gear type speed reducer 24, and extends from the cylindrical portion in a direction orthogonal to the crankshaft. A case body 23a integrally formed with a motor mounting portion for housing the planetary roller reducer 25;
Of the openings at both ends of the tubular portion, the left side opening of the vehicle body having the larger opening diameter is fixed by a mounting screw 23b, and the opening is closed and the left end of the crankshaft 13 is rotatably supported by a bearing 23c. It is formed of a lid body 23d. In this embodiment, a cover 26 having a substantially circular shape in a side view is fixed to the outside of the lid 23d.

The main constituent members (motor 12, planetary gear type speed reducer 24, planetary roller type speed reducer 25, etc.) of the auxiliary power unit 9 are all attached to the case body 23a. With this configuration, the main constituent members can be connected with high accuracy and the assembling strength can be secured.

The planetary gear type speed reducer 24 includes the planetary gear 2
7 is a one-way clutch 28 according to the present invention on the crankshaft 13.
The sun gear 29 is rotatably supported by the crankshaft 13, and the outer peripheral gear 30 is formed in a substantially tubular shape extending in the vehicle width direction and is riveted to the tubular output shaft 31. The outer peripheral portion of the outer peripheral gear 30 has a smaller diameter on the cylindrical output shaft 31 side than the portion where the planetary gear 27 meshes, so that the planetary gear type speed reducer 24 does not needlessly increase in size. The one-way clutch 28 is configured so that power is transmitted from the crankshaft 13 to the planetary gear reducer 24 only when the crankshaft 13 rotates counterclockwise in FIG. 3 with respect to the planetary gear reducer 24. ing.

This one-way clutch 28 is shown in FIGS.
As shown in FIG. 2, a substantially annular inner ring 32 fixed to the crankshaft 13 by spline fitting, a hollow portion for housing the inner ring 32 are formed, and an engagement tooth 33 having a substantially saw-tooth cross section is formed on the inner peripheral portion. An outer ring 34 formed over the entire circumference, a claw piece 35 interposed between the inner ring 32 and the outer ring 34, and a spring 36 for urging the claw piece 35 to engage the engaging tooth 33. Are formed from. Further, a support shaft 27a that rotatably supports the planetary gear 27 is erected on the outer ring 34.

The inner ring 32 has four projections 37, which function as sliding contact projections, which project radially outward and extend in the circumferential direction on the outer circumferential portion and are spaced apart in the circumferential direction. A claw piece supporting recess 38 formed by recessing the outer peripheral surface of the inner ring 32 in an arcuate cross-section is formed in the space. Further, the projecting side end surface 37a of each of the projections 37 is an arc surface centered on the axial center of the inner ring 32, and the inner ring 3
2 is loaded in the hollow portion of the outer ring 34, all the projections 37
The protruding side end surface 37a of the above is configured to be in sliding contact with the top of the engaging tooth 33. Moreover, the spring 3 is attached to the protrusion 37.
A groove 39 for inserting 6 is formed along the circumferential direction.

The claw piece 35 has a recess 38 in the inner ring 32.
A base portion 35a formed with a convex curved surface having an arcuate cross-section slidably fitted to the inner ring 3 during power transmission from the base portion 35a.
The engaging portion 35b extends forward in the rotation direction of 2 (counterclockwise in FIG. 5) and has an extended end that engages with the engaging tooth 33. The engagement tooth 33 is relatively gently inclined on the front side in the rotational direction of the inner ring 32 during power transmission with respect to the top and steeply inclined on the opposite side. A notch 35c into which the spring 36 is inserted is formed in the claw piece 35 from the extending end toward the base 35a. The bottom surface of the notch 35c is formed flat and is inclined with respect to the extending direction of the engaging portion 35b as shown in FIG.

The inclination angle of the bottom surface is such that, in the state shown in FIG. 5 in which the base portion 35a is fitted in the concave portion 38 and the engaging portion 35b is engaged with the engaging teeth 33, the inner ring 32 at the time of power transmission on the bottom surface. The rear end in the rotation direction is set to project radially outward from the front end. The spring 36 is in contact with the protruding end portion of the bottom surface. The spring 36 is formed in an annular shape with a part cut, and is elastically mounted on the inner ring 32 so as to expand its diameter. That is, the end portion of the bottom surface of the notch 35c that is in contact with the spring 36 is pushed toward the center of the inner ring 32 in the radial direction, and the pawl piece 35 is biased clockwise in FIG. 5 about the base portion 35a. . Therefore, the engagement portion 35b is always pressed against the engagement teeth 33.

The one-way clutch 28 thus constructed
Then, the outer ring 34 is arranged on the same axis as the inner ring 32 by sliding all the protrusions 37 of the inner ring 32 on the tops of the engaging teeth 33, and the outer ring 34 rotates without using steel balls or the like for the inner ring 32. It will be supported freely. And
The crankshaft 13 and the inner ring 32 are shown in FIG.
The power (the pedaling force generated by stepping on the pedal 17) is applied from the inner ring 32 to the claw piece 35 only when the wheel turns counterclockwise.
Will be transmitted to the outer ring 34 via. Also, turn the crank 16 in the direction opposite to that when moving forward,
When the outer ring 34 rotates counterclockwise faster than the inner ring 32 by the power of, the one-way clutch 28 does not transmit power.

In the planetary gear type speed reducer 24, when the outer ring 34 rotates together with the inner ring 32, the sun gear 29 is prevented from rotating with respect to these members, so that the outer peripheral gear 30 is rotated in a predetermined direction in the same direction. It rotates at an increased speed. Then, the cylindrical output shaft 31 to which the peripheral gear 30 is riveted and the crank gear 15 fixed to the shaft end of the cylindrical output shaft 31 rotate,
The power of the crankshaft 13 is transmitted to the rear wheel 8 via the chain 20 and the freewheel. As shown in FIG. 4, in the cylindrical output shaft 31, a ring gear 40, to which power is transmitted from a planetary roller reducer 25, which will be described later, is riveted together with the peripheral gear 30, and is attached to the case body 23 a via a bearing 41. It is rotatably supported.
Further, the hollow portion of the tubular output shaft 31 rotatably supports the shaft end portion of the crankshaft 13 on the right side of the vehicle body through a bearing 42.

In restricting the rotation of the sun gear 29, in this embodiment, a stopper indicated by reference numeral 43 in FIG. 3 and a pedaling force detection mechanism indicated by 44 are used. The stopper 43 is screwed to the case body 23a so that the tip inside the case abuts on the lower end surface of the arm 29a of the sun gear 29. In addition, the pedaling force detection mechanism 44 is a potentiometer device 46 that comes into contact with the contact plate member 45 riveted to the protruding end of the arm 29a from above.
And a pressure device 47 for urging the potentiometer device 46 toward the contact plate member 45. In addition,
The contact plate member 45 is formed wider than the arm 29a to reduce the surface pressure.

The potentiometer device 46 of the pedaling force detection mechanism 44 is composed of a lever 46a whose swing end contacts the contact plate member 45, and a potentiometer body 46b connected to the lever 46a, and is supported by the case body 23a. It is fixed. The potentiometer body 46b is
An input shaft 46c connected to the lever 46a is provided so as to be rotatable about a direction orthogonal to the plane of FIG. 3 as an axis.
The lead wire 46d is detected by detecting the rotation angle of the input shaft 46c.
It is configured to output to the control unit 21 via the. The input shaft 46c is rotatably supported by the case body 23a by a bearing 46e.

The pressurizing device 47 supports a pusher 47a that abuts the swinging end of the lever 46a, and supports the pusher 47a so that it can move back and forth with respect to the lever 46a.
The case 47b supported and fixed to 3a and the pressing element 47
and a compression coil spring 47c that biases a toward the lever 46a.

That is, the planetary gear 2 together with the outer ring 34.
When 7 rotates counterclockwise in FIG. 3, the sun gear 29 is rotationally urged counterclockwise by the rotational reaction force from the peripheral gear 30, and the force is applied to the backing plate member 45 and the lever 46a.
Is transmitted to the pressurizing device 47 via the and is absorbed by the pressurizing device 47. Therefore, the sun gear 29 is prevented from rotating in a state in which the sun gear 29 is allowed to rotate by an amount corresponding to the movement amount of the pressing element 47a of the pressure device 47.

When the sun gear 29 rotates in this way, the potentiometer body 46b detects the amount of rotation and outputs it to the control unit 21. At this time, the control unit 21 controls the motor 12 according to the detection signal from the potentiometer body 46b. The control of the motor 12 is performed so that the rotation speed of the motor 12 is proportional to the rotation amount of the sun gear 29. More specifically, the rotation speed of the outer peripheral gear 30 is detected by a rotation sensor indicated by reference numeral 48 in FIG.
The rotation speed of the peripheral gear 30 and the potentiometer body 4
As shown in FIG. 9, the control unit 21 calculates the motor driving force from the rotation amount of the sun gear 29 detected by 6b to drive the motor 12. Therefore, the motor 12 is controlled so that the torque is approximately proportional to the pedaling force generated by stepping on the pedal 17. The rotation speed sensor 48 is screwed to the case main body 23a, the inner end of the case faces the left end of the outer gear 30 on the vehicle body side with a small gap, and a large number of teeth are formed on the outer gear 30. Part 3
A known one is used which utilizes the fact that the magnetic resistance changes depending on 0a. When the rotation speed is detected by using the tooth portion 30a formed at the end portion of the outer peripheral gear 30 as described above, no special rotation speed detection component is required when the rotation speed is detected by the rotation speed sensor 48. .

Next, the structure of the power transmission system connected to the motor 12 will be described. As shown in FIG. 4, the motor 12 has the rotation shaft 12 a thereof connected via the planetary roller reducer 25, the motor-side one-way clutch 51, the output gear member 52, and the ring gear 40 meshing with the output gear member 52. It is connected to the cylindrical output shaft 31.

The planetary roller speed reducer 25 is formed in a cylindrical shape having a diameter larger than that of the rotating shaft 12a of the motor 12 which is a round bar, and an outer ring 53 fixed to the shaft end of the motor 12 coaxially with the rotating shaft 12a. A plurality of planetary rollers 54 are arranged between the outer ring 53 and the rotary shaft 12a and are in contact with both of them, respectively, and a pin 55 for rotatably holding the planetary rollers 54 and a one-way clutch on the motor side. And an output shaft member 56 that transmits power to the output gear member 52 via 51.

The outer ring 53 has guide plates 57 and 58 for restricting the axial movement of the planetary roller 54 attached to both axial end portions thereof and fixed to the motor 12 by fixing bolts 59. The holes through which the fixing bolts 59 penetrate the outer ring 53 and the guide plates 57 and 58 are formed to have a larger diameter than the fixing bolts 59, so that the fixing bolts 59 do not restrict the position in the radial direction. Further, as shown in FIG. 6, the circular fitting portion 60 of the case body 23a is fitted to the outer peripheral portion of the outer ring 53. The motor 12 is connected to the case main body 23a by the connecting bolt 61 as shown in FIG. 3 with the outer ring 53 fitted in the circular fitting portion 60 in this way.

The planetary roller 54 is shown in FIG. 6 in this embodiment.
As shown in FIG. 5, four outer rings 53 are mounted at equal intervals in the circumferential direction, and each of them is rotatably supported by a pin 62 of the output shaft member 56 by a bearing 62. The output shaft member 56 that holds the planetary roller 54 has the pin 5 at the bottom.
5 is formed in a cylindrical shape having a bottom and protrudingly provided, and a motor-side one-way clutch 51 and an output gear member 52 are mounted in the hollow portion.

In the planetary roller reducer 25 thus constructed, the rotation shaft 12a of the motor 12 rotates clockwise as shown by the arrow in FIG. While rotating on the opposite side, it rolls on the inner peripheral surface of the outer ring 53 and revolves clockwise. This causes the output shaft member 56 to rotate clockwise with a predetermined reduction ratio in FIG.

The motor side one-way clutch 51 mounted in the hollow portion of the output shaft member 56 outputs the rotation only when the output shaft member 56 rotates clockwise with respect to the output gear member 52 in FIG. It is configured to transmit to the gear member 52. Further, the output gear member 52 is rotatably supported by the case body 23a by the bearing 63 in a state in which the movement in the axial direction is restricted, and the motor-side shaft end is connected to the motor-side one-way clutch 51. A bevel gear is formed at the shaft end portion on the opposite side to this and meshes with the ring gear 40.

That is, when the output shaft member 56 rotates as described above, the power of the motor 12 is applied to the output shaft member 5.
6 is transmitted to the cylindrical output shaft 31 via the output gear member 52 and the ring gear 40.

In this way, the one-way clutch 51 on the motor side is interposed in the power transmission path of the motor 12 because the electric power of the battery 11 is insufficient and the rotation of the motor 12 is slowed or the power of the motor 12 is reduced. To prevent the driving resistance from increasing due to the power from the crankshaft 13 being transmitted from the ring gear 40 to the motor 12 via the output gear member 52 and the planetary roller reducer 25 when the vehicle is intentionally turned and travels only by human power. Is.

Incidentally, the rotary shaft 12a and the output shaft member 56.
And 64 provided between the bottom surface of the output shaft member 56 and between the inner bottom surface of the output shaft member 56 and the shaft end of the output gear member 52 when the thrust force in the axial direction is applied to the output shaft member 56. The output shaft member 56 includes the rotating shaft 12a and the output gear member 5
It is a ball for preventing it from abutting on 2. These balls 64, 65 are engaged in a circular hole formed in the rotary shaft 12a or the shaft end of the output gear member 52, which is recessed.

Now, a procedure for assembling the motor 12 and the planetary roller reducer 25 into the case body 23a will be described. In assembling, first, the output shaft member 56 is attached to the outer ring 53. At this time, the guide plate 58 is interposed between the output shaft member 56 and the outer ring 53, and the bearing 62 and the planetary roller 54 are mounted on the pin 55 to be housed on the inner peripheral side of the outer ring 53. Then, the outer ring 53 to which the output shaft member 56 is attached in this manner is fixed to the motor 12 with the guide plate 57 interposed between the outer ring 53 and the motor 12.
At this time, the rotary shaft 12a of the motor 12 is engaged between the planet rollers 54 so that the planet roller 54 and the output shaft member 56 can rotate with respect to the rotary shaft 12a.
At the same time, the ball 64 is attached to the rotary shaft 12a and the output shaft member 5
It is inserted between 6 and. By doing so, the outer ring 53 and the output shaft member 5 are attached to the rotating shaft 12a.
6 are located on the same axis.

Next, the outer ring 53 and the guide plates 57 and 58.
Are fixed to the motor 12 with fixing bolts 59. As a result, the planetary roller reducer 25 is attached to the motor 12. That is, the planetary roller reducer 25 can be connected to the motor 12 without using a special fitting structure.

Thereafter, the outer peripheral portion of the outer ring 53 is fitted into the circular fitting portion 60 of the case body 23a. At this time, the hollow portion of the output shaft member 56 or the output gear member 5
The motor-side one-way clutch 51 is attached to the motor 2 in advance, and the motor-side one-way clutch 51 is attached simultaneously with the attachment of the motor 12. Further, the ball 65 is also the output gear member 5
Attach it to 2 in advance.

Then, the motor 12 is fixed to the case main body 23a by the connecting bolt 61, and the assembling of the motor 12 and the planetary roller reducer 25 is completed. To mount the auxiliary power unit 9 on the frame 2, the bolt holes 66 and 67 formed in the case body 23a are aligned with the bolt holes of the connecting brackets 18 and 19 as shown in FIG. 23a is bolted to the connecting brackets 18 and 19.

Next, the structure of the battery case 10 accommodating the battery 11 for supplying power to the motor 12 will be described. The battery case 10 is formed in a vertically elongated box shape, and has a battery 1 inside as shown in FIGS. 1 and 8.
It has a structure to store two 1's, and a seat tube 2
It is arranged between c and the rear wheel 8. That is, as shown in FIG. 2, the battery case 10 has a dimension in the vehicle width direction that is passed between the left and right seat stays 2e, and a dimension in the front-rear direction that is left and right with respect to the seat tube 2c. The size is set so as to pass through between the pair of auxiliary seat tubes 71. The auxiliary seat tube 71 is bridged between the left and right seat stays 2e and the rear end of the down tube 2b substantially in parallel with the seat tube 2c.

Further, as shown in FIG. 2, the battery case 10, the auxiliary power unit 9 and the control unit 21 described above.
Are all housed between the left and right cranks 16, 16.

In the structure for mounting the battery case 10 on the vehicle body, a support box 72 having a bottomed rectangular tube opening upward is provided at the rear end of the down tube 2b.
The structure is such that the lower end portion of the battery case 10 is fitted into the inside from above. The lower front part of the support box 72 is connected to the bracket 73 of the middle lug 5 and is supported by the frame 2 via the bracket 73 and the middle lug 5. Therefore, the battery case 10 is detachably attached to the vehicle body in the vertical direction. A male connector 72a electrically connected to a female connector 10a provided at the lower end of the battery case 10 is attached to the bottom of the support box 72, and the battery case 10 is removed from the vehicle body by a third party. A lock mechanism 74 is attached to prevent the lock.

The male connector 72a is electrically connected to the control unit 21 and the motor 12 via the main switch 22, and has a structure in which the contacts project into the support box 72. That is, by fitting the battery case 10 into the support box 72 from above, the female connector 10a on the battery case 10 side is electrically connected to the male connector 72a, and the main switch 22 and other electric devices are powered from the battery 11. Will be done.

The lock mechanism 74 is provided with a locking claw 74a which is rotatably provided on the support box 72 and is engageable with and disengageable from the battery case 10, so that the battery case 10 can be fitted into the support box 72. The structure is locked by. The locking claw 74a is connected to the main switch 22 through the operation wire 74b, and the lock is released when the key of the main switch 22 is turned to the unlock side (counterclockwise in FIG. 1). Has become.

In the state shown in FIG. 1, when the battery case 10 is pulled up, the saddle 75 located at the upper end of the seat tube 2c becomes an obstacle, but the saddle 75 is moved by the seat tilting mechanism 76 described later. It is separated from the attachment / detachment path of the battery case.

The saddle 75 is the seat pillar tube 7
7 is attached to the upper end of the sheet pillar tube 7
It is attached to the frame 2 by inserting 7 into the seat tube 2c. This saddle 75 has a cushion in this embodiment. The seat pillar tube 77 has a saddle 7 depending on the physique of the occupant.
The sheet tilting mechanism 76 is formed at a lower end so that the height of the sheet 5 can be changed. In addition, in order to change the height of the saddle 75, first,
The seat pin 78 provided at the upper end of the seat tube 2c for changing the upper end opening diameter of the seat tube 2c is loosened, the saddle 75 is pulled, and the seat pillar tube 77 is pulled out upward from the seat tube 2c. And saddle 75
Is positioned at a desired height, the seat pin 78 is tightened, and the seat pillar tube 77 is tightly bound at the upper opening of the seat tube 2c.

The seat tilting mechanism 76 has an upper member 76a inserted and fixed to the lower end of the seat pillar tube 77.
And a lower member 76c which is swingably connected to the upper member 76a via a pivot pin 76b and which is fitted and inserted into the seat tube 2c. The pivot pin 76b is attached with its axis oriented in the vehicle width direction. For this reason, the upper member 7 is lower than the lower member 76c.
Although 6a swings in the front-back direction, in the present embodiment, the upper member 76a is configured to incline only to the front side with respect to the lower member 76c.

That is, the seat tilting mechanism 76 is inserted into the seat tube 2c as shown in FIG. 1 during traveling with the seat pillar tube 77 fixed to the seat tube 2c. Further, in a state in which all of the seat pillar tubes 77 are drawn onto the seat tube 2c and the upper portion of the lower member 76c is projected from the upper opening of the seat tube 2c, the seat pillar tube 77 and It becomes possible to incline the saddle 75 from the upper pull-out position shown by the two-dot chain line in FIG. 8 to the front side as shown by the solid line.

In FIG. 1, reference numeral 79 is a vehicle body cover. The vehicle body cover 79 is composed of cover bodies 80 and 81 that are divided into upper and lower parts.
The down tube 2b and the electrical components (main switch 22,
The control unit 21, the auxiliary power unit 9 and the like) are sandwiched so as to cover them. Further, the lower cover body 81 is opened at a portion corresponding to the lower front surface of the control unit 21 (this portion is indicated by reference symbol A in FIG. 1), and the lower portion of the control unit 21 faces this opening. In this way, the traveling wind can be applied to the control unit 21 through the opening, so that the control unit 21 that easily generates heat can be efficiently cooled.

Next, the operation of the electric bicycle 1 configured as described above will be described with reference to FIG. Main switch 22
When is OFF, the auxiliary power from the motor 12 is not applied, and the rotation of the crankshaft 13 causes the one-way clutch 28 on the crankshaft side, the planetary gear reducer 24, the tubular output shaft 31, the chain 20, and the rear wheel side to rotate. Transmitted to the freewheel,
The rear wheel 8 is driven only by the pedaling force generated by stepping on the pedal 17.

When the main switch 22 is ON,
Auxiliary power proportional to the pedal effort is applied from the motor 12 to the cylindrical output shaft 3
1 is added to the rear wheel 8 by the combined force of pedaling force and auxiliary power.
Will be driven. At this time, the pedal effort detected by the pedal effort detection mechanism 44 and the rotation speed of the outer peripheral gear 30 (cylindrical output shaft 31) detected by the rotation sensor 48 are input to the control unit 21, and the torque becomes proportional to the pedal effort. Thus, the control unit 21 controls the motor 12. That is, the power of the motor 12 is transmitted from the planetary roller reducer 25 connected to the rotary shaft 12 to the tubular output shaft 31 via the motor-side one-way clutch 51, the output gear member 52, and the ring gear 40, and the tubular output shaft 31. The output force of the crankshaft 13 is combined with the output shaft 31 and is transmitted to the rear wheels via the chain 20 and the freewheel.

Therefore, in the one-way crankshaft-side clutch 28 constructed as described above, the protrusion 37 provided on the inner ring 32 serves as a substantial bearing and the outer ring 34 serves as the inner ring 32.
Will be rotatably supported. Therefore, the inner ring 3
When the 2 and the outer ring 34 are rotatably provided to each other, a steel ball becomes unnecessary. Moreover, since the outer ring 34 is arranged on the same axis with respect to the inner ring 32 by the projection 37, it is possible to similarly engage the plurality of arranged claw pieces 35 with the engaging teeth 33 in the same manner.

The one-way clutch 2 on the crankshaft side
Since 8 does not use steel balls, it is not necessary to preassemble before assembling, and the inner ring 32 and the outer ring 34 can be individually assembled when the auxiliary power unit 9 is assembled. That is, the number of assembling steps can be reduced.

Further, as shown in this embodiment, the motor 1
2 below the down tube 2b, the motor 1
2 and the power unit 14 can be continuously arranged in a wide space below the down tube 2b. Therefore, the power transmission path of the motor 12 is simple and short.

Furthermore, when the battery 11 is arranged above the down tube 2b, the weight of the battery 11 is easily received by the down tube 2b. Moreover, the battery 11
Is disposed behind the seat tube 2c, the foot passage space in front of the seat tube 2c can be widened, and the battery 11 does not interfere when getting on and off.

In addition, as shown in the present embodiment, if the peripheral gear 30, the ring gear 40 and the cylindrical output shaft 31 of the power unit 14 are formed separately and are joined by rivets, each member will be used. The cost can be kept low because it can be formed of a material most suitable for the function and does not cause excess quality.

In this embodiment, the claw piece 35 is attached to the inner ring 32 and the projection 37 is formed, and the engaging tooth 33 is formed on the outer ring 34. However, the claw piece 35 and the projection 37 are shown.
May be provided on the outer ring 34 and the inner ring 32 may be provided with engaging teeth.
Even in this case, the same effect as that of the above embodiment can be obtained.

[0066]

As described above, in the one-way clutch according to the present invention, the engaging tooth is formed on one of the outer ring member and the inner ring member, and the other side is in sliding contact with the top of the engaging tooth. Since a plurality of protrusions are formed along the circumferential direction and the sliding contact protrusion rotatably supports the member on the engagement tooth side, the sliding contact protrusion serves as a substantial bearing. When the member and the inner ring member are rotatably provided with each other, a steel ball becomes unnecessary.

Therefore, the space for mounting the steel balls can be saved and the size can be reduced, and the weight and cost can be reduced. In addition to this, in assembling the one-way clutch according to the present invention into the drive shaft or the driven shaft, the inner ring member and the outer ring member can be individually assembled, so that the number of steps required for the assembly can be reduced. .

[Brief description of drawings]

FIG. 1 is a side view of an electric bicycle in which a one-way clutch according to the present invention is incorporated in an auxiliary power unit.

FIG. 2 is an enlarged plan view showing a part of the electric bicycle.

FIG. 3 is a side view of a power unit and a motor.

FIG. 4 is a sectional view taken along line IV-IV of the power unit in FIG.

FIG. 5 is a diagram showing the V of the one-way clutch according to the present invention in FIG.
It is a -V line sectional view.

6 is a sectional view taken along line VI-VI in FIG.

FIG. 7 is an enlarged perspective view showing a main part of the one-way clutch according to the present invention.

FIG. 8 is an enlarged side view showing a battery case mounting portion.

FIG. 9 is a diagram showing a power transmission path of the electric bicycle.

FIG. 10 is a view showing a freewheel for a bicycle as a conventional one-way clutch.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Electric bicycle 9 Auxiliary power device 28 Crankshaft side one-way clutch 32 Inner ring 33 Engaging tooth 34 Outer ring 35 Claw piece 36 Spring 37 Protrusion

Claims (1)

[Claims] 1. A one-way clutch in which a pawl piece biased toward an engaging tooth side by a spring is interposed between an outer ring member and an inner ring member, and is engaged with either one of the outer ring member and the inner ring member. A plurality of sliding contact projections are formed along the circumferential direction on the other side to form a compound tooth, and the sliding contact projections that are in sliding contact with the tops of the engaging teeth are rotatably supported by the sliding contact projections. A one-way clutch characterized by having a structure.