TWM448447U - Output mechanism of central shaft continuous variable transmission - Google Patents

Description

Middle shaft stepless speed output mechanism

The present invention relates to a power output mechanism for a bicycle, and more particularly to a stepless speed output mechanism for a bicycle center shaft.

Some electric assist bicycles will have a power output mechanism in the middle shaft. This mechanism can mix the pedal power and motor power to drive the gear tray for output. Generally speaking, in the case where the resistance of the bicycle is increased, it is desired to increase the deceleration. In order to achieve the purpose of labor saving, and in the case where the resistance is small, it is desirable to reduce the reduction ratio to increase the speed. If the change of the speed ratio is continuous, it is called stepless speed change.

However, when the overall reduction ratio of the shifting system of the power output mechanism is low, the power output of the motor needs to be decelerated in advance through another deceleration system, which may result in an increase in the overall volume and weight of the power output mechanism.

In view of this, the main purpose of the present invention is to provide a mid-shaft stepless shifting output mechanism with a relatively large deceleration of the shifting mechanism, so that the motor power can be directly transmitted to the shifting mechanism without passing through the speed reducing mechanism, thereby reducing the overall volume and weight.

In order to achieve the above and other objects, the present invention provides a center shaft stepless speed output mechanism including a spindle, a motor, a toothed disc drive seat, a second one-way bearing, a toothed disc and a shifting mechanism, the spindle Rotating by a pedal power driven by a pair of cranks, the motor has a rotor that can be driven to rotate, the gear drive base is coaxial with the spindle, and the second one-way bearing is disposed at the core Between the shaft and the toothed disc drive seat, the spindle is driven only in a relative rotational direction The disk drive base rotates together, and the toothed disk is coaxially disposed on the toothed disc drive base. The shifting mechanism transmits the power input by the rotor and the spindle to the toothed disc drive base. Wherein, the shifting mechanism comprises a spindle input disc, a first one-way bearing, a motor output seat, a third one-way bearing, at least one planetary gear, a plurality of drive pins and a ring gear, and the spindle input disk system The spindle is coaxial and has a plurality of first pin holes. The first one-way bearing is disposed between the spindle and the spindle input disk, so that the spindle rotates the spindle input disk only in a relative rotational direction. The motor output seat is rotatably coaxially disposed on the spindle, the motor output seat has at least one eccentric portion disposed between the rotor and the motor output seat, so that the rotor is only in a relative rotational direction Driving the motor output seat to rotate together, the planetary gear system is rotatably sleeved on the eccentric portion and has a plurality of planetary teeth and a plurality of insertion holes, wherein the transmission pin shafts are respectively inserted into one of the first pin holes and each of the planets One of the insertion holes of the gear, the outline of each of the insertion holes is slightly larger than the outer diameter of each of the drive pins, the ring gear is coaxially disposed on the spindle and interlocked with the gear drive base, the ring gear has a plurality of internal teeth for engaging For the planet teeth.

Since the shifting mechanism integrally forms a planetary gear system with a large reduction ratio, the motor power can be directly input to the shifting mechanism without deceleration, so that the central shaftless shifting output mechanism of the present invention does not need to be additionally equipped with a speed reducing mechanism, so that Reducing the overall volume and weight, in line with the industry's lightweight trend.

Referring to the first to third figures, in a preferred embodiment of the present invention, a bicycle intermediate shaft stepless speed output mechanism includes a spindle 10, a motor 20, a toothed disc drive base 30, and a second one-way bearing 40. a toothed disc 50, a shifting mechanism 60 and a housing 70 for covering the motor 20, the second one-way bearing 40 and the shifting mechanism 60 and other components.

Both ends of the mandrel 10 are connected to a pair of cranks 80 that are rotatable in synchronism, and the pair of cranks 80 transmit the pedaling force applied by the user to drive the spindle 10 to rotate.

The motor 20 has a stator 21, a plurality of magnets 22, and a rotor 23 that is electrically drivable.

The spur gear carrier 30 is coaxial with the spindle 10, and the second unidirectional bearing 40 is disposed between the spindle 10 and the spur gear carrier 30, so that the spindle 10 drives the teeth only in a relative rotational direction. The disk drive base 30 rotates together. For example, when the spindle 10 rotates relative to the disk drive carrier 30, power can be transmitted to the disk drive carrier 30 via the second one-way bearing 40, and when the spindle 10 is reversed relative to the disk drive carrier 30. At this time, power is not transmitted to the spur gear base 30 via the second one-way bearing 40.

The spurs 50 are coaxially and synchronously rotatably disposed on the spur gear base 30 for winding around a chain (not shown), thereby transmitting power to the rear wheel of the bicycle (not shown).

The shifting mechanism 60 transmits the power input from the rotor 23 and the spindle 10 to the chain drive base 30. More specifically, the shifting mechanism 60 includes a spindle input disk 61, a first one-way bearing 62, a motor output seat 63, a third one-way bearing 64, at least one planetary gear 651, 652, and a plurality of drive pins. 66 and a ring gear 67.

The mandrel input disk 61 is coaxial with the mandrel 10, and the mandrel input disk 61 has a plurality of first pin holes 611 arranged around the mandrel 10.

The first one-way bearing 62 is disposed between the spindle 10 and the spindle input disk 61 such that the spindle rotates only in a relative rotational direction (for example, relative to normal rotation) to drive the spindle input disk 61.

The motor output seat 63 is rotatably coaxially disposed on the spindle 10, and the motor is driven. The outlet 63 has at least one eccentric portion, such as a first eccentric portion 631 as shown in FIG. 4 and a second eccentric portion 632 as shown in FIG. 5, wherein the first and second eccentric portions 631, 632 are The cross section of the vertical mandrel 10 has a circular contour, and the centers of the first and second eccentric portions 631, 632 are preferably respectively located on opposite sides of the axis C of the mandrel 10, in other words, the axis C is first, The center of symmetry of the second eccentric portions 631, 632.

The third one-way bearing 64 is disposed between the rotor 23 and the motor output seat 63 such that the rotor 23 rotates the motor output base 63 only in a relative rotational direction (for example, relative to normal rotation).

The at least one planetary gears 651 and 652 preferably include a first planetary gear 651 and a second planetary gear 652. The first planetary gear 651 is rotatably sleeved on the first eccentric portion 631 through the bearing 653. The second planetary gear 652 is rotatably sleeved on the second eccentric portion 632 through the bearing 654. The first and second planetary gears 651, 652 have a plurality of planetary teeth 655, 656 and a plurality of insertion holes 657, 658.

The driving pins 66 are respectively inserted into one of the first pin holes 611 and one of the insertion holes 657 and 658 of the planetary gears 651 and 652. The outlines of the insertion holes 657 and 658 are slightly larger than the driving pins. The outer diameter of the shaft 66.

The ring gear 67 is coaxially disposed on the spindle 10 and is coupled to the spur gear carrier 30. The ring gear 67 has a plurality of internal teeth 671 for engaging the planetary teeth 655, 656.

In addition, in order to improve the stability of the drive pin 66, the shifting mechanism 60 of the present invention may further include a support plate 68 rotatably coaxially disposed on the motor output seat 63 and having a plurality of second pins. Hole 681, the drive pin 66 can be inserted into one of the second pin holes 681 to improve the stability.

With the above design, when the pedal power and the motor power are transmitted to the shifting mechanism 60 via the spindle 10 and the rotor 23, respectively, the spindle 10 drives the spindle output disc 61 to rotate synchronously through the first one-way bearing 62, and the spindle output is The disk 61 drives the first and second planetary gears 651 and 652 to "rotate" by the driving pin 66, and the rotor 23 drives the motor output seat 63 to rotate synchronously through the third one-way bearing 64. First, the second eccentric portions 631, 632 can respectively push the first and second planetary gears 651, 652 to "revolve"; in other words, the pedal power and the motor power can be synchronously merged into the planetary gears 651, 652, and the planetary teeth 655 and 656 are engaged with the internal teeth 671 and drive the ring gear 67 to rotate, thereby driving the sprocket drive base 30 and the spur 50 to rotate and output power. The overall reduction ratio of the shifting mechanism 60 is determined by the spindle 10 and the rotor 23. The speed is determined.

Since the present invention uses a small-tooth differential planetary gear system as a shifting mechanism, the structure is relatively simple and the overall deceleration is relatively large, so that the motor power can be directly output to the shifting mechanism without using other speed reducing mechanisms, so the central shaft has no step shifting output mechanism. The overall volume and weight can be greatly reduced. The number of the planetary teeth 655 and 656 of each of the planetary gears 651 and 652 is preferably 1 to 12 less than the number of the internal teeth 671 of the ring gear 67. If the difference in the number of teeth is smaller, the reduction ratio is larger, but attention should be paid to the gears. The tooth-shaped stem involves vibration problems, and if the difference in the number of teeth is large, the reduction ratio is smaller, but the tooth-shaped interference and vibration between the opposing gears are smaller; and if the difference in the number of teeth exceeds 12 teeth, the deceleration is relatively small. Then the motor 20 may need to be additionally speeded down with an additional speed reduction mechanism.

On the other hand, when the bicycle is just starting or the motor 20 is not running, the pedal power can be transmitted to the spindle 10 by the crank 80, and the spindle 10 will pass through the first The two-way bearing 40 directly drives the toothed disc drive base 30 to rotate the toothed disc 50 for power output. At the same time, the mandrel 10 also drives the spindle input disk 61, and drives the motor output seat 63 through the transmission pin 66 and the planetary gears 651 and 652. However, the third one-way bearing 64 can function at this time. The rotor 23 remains stationary. Of course, the second and third one-way bearings 40, 64 may be omitted if it is ensured that the motor 20 can continue to operate.

It should be noted that the shifting mechanism of the present invention can transmit power as long as there are more than one set of eccentric portions and planetary gears, and in principle, the more the eccentric portion and the planetary gears have better power transmission stability, but the number of groups is too large. There is a problem of an increase in volume and weight, and therefore it is preferable to have a combination of two sets of symmetrical eccentric portions and planetary gears in this embodiment. Finally, it must be stated that the constituent elements disclosed in the foregoing embodiments are merely illustrative and are not intended to limit the scope of the present invention. Alternatives or variations of other equivalent elements should also be applied for in this case. Covered by the scope.

10‧‧‧ mandrel

20‧‧‧Motor

21‧‧‧ Stator

632‧‧‧Second eccentric

64‧‧‧ Third one-way bearing

651, 652‧‧‧ planetary gear

22‧‧‧ magnet

23‧‧‧Rotor

30‧‧‧Rear drive base

40‧‧‧Second one-way bearing

50‧‧‧ toothed disc

60‧‧‧Transmission mechanism

61‧‧‧ spindle input tray

611‧‧‧first pin hole

62‧‧‧First one-way bearing

63‧‧‧Motor outlet

631‧‧‧First eccentric

653, 654‧ ‧ bearing

655, 656‧‧ ‧ planet teeth

657, 658‧‧‧ jack

66‧‧‧Drive pin

67‧‧‧ring gear

671‧‧‧ internal teeth

68‧‧‧Support disk

681‧‧‧Second pin hole

70‧‧‧shell

80‧‧‧ crank

C‧‧‧Axis

The first figure is a perspective view of a preferred embodiment of the present invention.

The second drawing is an exploded view of a preferred embodiment of the present invention.

The third drawing is a cross-sectional view of a preferred embodiment of the present invention.

The fourth figure is a cross-sectional view of 4-4 of the third figure.

The fifth figure is a sectional view of 5-5 of the third figure.

10‧‧‧ mandrel

20‧‧‧Motor

23‧‧‧Rotor

30‧‧‧Rear drive base

40‧‧‧Second one-way bearing

50‧‧‧ toothed disc

60‧‧‧Transmission mechanism

61‧‧‧ spindle input tray

611‧‧‧first pin hole

62‧‧‧First one-way bearing

63‧‧‧Motor outlet

631‧‧‧First eccentric

632‧‧‧Second eccentric

64‧‧‧ Third one-way bearing

651, 652‧‧‧ planetary gear

653, 654‧ ‧ bearing

655, 656‧‧ ‧ planet teeth

657, 658‧‧‧ jack

66‧‧‧Drive pin

67‧‧‧ring gear

671‧‧‧ internal teeth

68‧‧‧Support disk

681‧‧‧Second pin hole

70‧‧‧shell

80‧‧‧ crank

Claims (6)

A mid-shaft stepless speed output mechanism includes: a spindle that is driven to rotate by a pedal power transmitted by a pair of cranks; a motor having a rotor that is electrically driven to rotate; a toothed disk drive seat, and the core The shaft is coaxial; a toothed disc is coaxially disposed on the toothed disc drive base; and a shifting mechanism transmits power input by the rotor and the spindle to the toothed disc drive base; wherein the shifting mechanism comprises: a spindle input a disk coaxial with the mandrel, the spindle input disk having a plurality of first pin holes; a first one-way bearing disposed between the spindle and the spindle input disk, such that the spindle is only in a relative rotational direction The upper input shaft is rotated together; a motor output seat is rotatably coaxially disposed on the spindle, the motor output seat has at least one eccentric portion; at least one planetary gear is rotatably sleeved on the eccentric portion and Having a plurality of planet teeth and a plurality of jacks; a plurality of drive pins are respectively inserted into one of the first pin holes and one of the ones of the planet gears, each of the jacks having a profile slightly larger than each of the drive pins Outer diameter; and a ring Wheel train disposed coaxially with the mandrel and the interlocking tooth plate driving seat, the ring gear having a plurality of internal teeth for engaging teeth on the plurality of planet. The shaftless stepless speed output mechanism of claim 1, wherein the at least one eccentric portion of the motor output seat comprises a first eccentric portion and a second eccentric portion The at least one planetary gear includes a first planetary gear and a second planetary gear. The first planetary gear is rotatably sleeved on the first eccentric portion, and the second planetary gear is rotatably sleeved on the first Two eccentric parts. The shaftless stepless speed output mechanism of claim 2, wherein the centers of the first and second eccentric portions are respectively located on opposite sides of the spindle axis. The shaft-less step-variable output mechanism of claim 1, wherein the shifting mechanism further comprises a support disc rotatably coaxially disposed on the motor output seat, the support disc having a plurality of second pin holes, the drive pins The shafts are respectively inserted into one of the second pin holes. The shaft non-segment shifting output mechanism according to claim 1, further comprising a second one-way bearing disposed between the spindle and the toothed disc drive seat, so that the spindle drives the toothed disc drive seat only in a relative rotational direction. And rotating, wherein the shifting mechanism further comprises a third one-way bearing disposed between the rotor and the motor output seat, so that the rotor drives the motor output seat to rotate together only in a relative rotational direction. The shaftless stepless speed output mechanism according to claim 1, wherein the number of planetary teeth of each of the planetary gears is 1 to 12 teeth less than the number of inner teeth of the ring gear.