TWI460364B - Speed changing apparatus for motors - Google Patents

Description

Motor shifting mechanism

BACKGROUND OF THE INVENTION 1. Field of the Invention This invention relates to a motor shifting mechanism, and more particularly to a multi-speed shifting mechanism that utilizes a motor to reversing and cooperate with a plurality of planetary gear sets to vary a reduction ratio.

The transmission is a very important component in general-purpose electric vehicles or electric hand tools. The entire transmission system accounts for about half of the production cost, so the development of the shifting mechanism in the electric vehicle or electric hand tool industry. It is a key project of each factory, and a good transmission can enable the rider to change the different speed ratios according to different environments, so as to achieve the appropriate speed or torque.

For variable speed electric vehicles, planetary gear sets are commonly used transmissions. The planetary internal transmission uses the planetary gear train as the main body of the shifting mechanism, and the shifting mechanism is disposed in the rear wheel housing, and the gear ratio of the planetary gear train is changed through different input parts, output parts and fixing parts to achieve Different speed ratios.

The internal transmission with the planetary gear train as the main body of the shifting mechanism has the following advantages: 1. Small size and precise structure, which is not limited by the limitation of installation and use space of the narrow rear wheel hub; 2. The shifting operation is stable, and the chain is not caused by Shifting and changing to connect with different sprockets can effectively improve the shortcomings of chain de-chaining and improve transmission efficiency; 3. The shifting mechanism has the outer casing protection of the wheel hub, which is not affected by the external environment and thus improves the service life; 4. The shifting mechanism is housed in the wheel hub, and does not generate as much noise as the external transmission during the shifting process.

According to the transmission principle of the planetary gear train as the transmission, the sun gear, the planetary gear and the outer ring gear respectively have one shaft, and the three gears are wound and rotated with each other. When the gears are in different gear positions, the three gear shafts must have one shaft fixed and not rotated. One axis is the drive axis and the other axis is the output shaft. Under different combinations, the gear ratio required for different gears such as deceleration, acceleration, and reverse gear can be achieved. Among them, the possibility of a total of six state combinations is as follows:

Therefore, the present invention takes the internal gear shifting mechanism of the planetary gear train as the core of the mechanical construction of the wheeled vehicle or the electric vehicle, and in recent years, the electric bicycle and the electric vehicle have been widely promoted due to environmental protection problems, and the current electric bicycle and electric bicycle Most of the cars are equipped with internal transmissions, so the internal transmission has gradually become the focus of research and development of major car manufacturers.

SUMMARY OF THE INVENTION The object of the present invention is to provide a motor shifting mechanism that utilizes a motor that rotates forward and reversely and cooperates with a plurality of planetary gear sets to achieve a multi-step shifting speed by varying the reduction ratio.

To achieve the above object, the motor shifting mechanism of the present invention is driven through a power input terminal, which includes: a first planetary gear set, a second planetary gear set, and a set of rings. The collar sleeve is attached to the periphery of the first and second planetary gear sets, and further includes: a first one-way clutch, a second one-way clutch, and a power output end.

Driving the first planetary gear set and the second planetary gear set in the collar by forward or reverse rotation of the power input end, and respectively engaging the first and second one-way clutches in the collar Engagement, different speed reduction ratios are generated, and the power of the power input end is decelerated and output through the collar to achieve the purpose of multi-stage speed switching.

In order to more clearly describe the motor shifting mechanism proposed by the present invention, the following will be described in detail with reference to the drawings.

Referring to FIG. 1 , the motor shifting mechanism 1 is driven through a power input end 2 and includes: a first planetary gear set 11 , a second planetary gear set 12 , and a third planetary gear. Group 13, a set of rings 14, and an electronically controlled clutch 15.

The first planetary gear set 11 further includes a first sun gear 111, a plurality of first planet gears 112, a first planet carrier 113, and a first outer ring gear 114. The second planetary gear set 12 further includes a second sun gear 121, a plurality of second planetary gears 122, a second planet carrier 123, and a second outer ring gear 124. The third planetary gear set 13 includes a third sun gear 131, a plurality of third planetary gears 132, a third planet carrier 133, and a third outer ring gear 134.

In the present invention, the first planetary gear set 11, the second planetary gear set 12, and the third planetary gear set 13, which are also called "Planetary gears", are also referred to as "star planetary gear reductions" on the market. Machine or "planetary gear reducer". In the above planetary gear reduction mechanism, the gear located at the center position is called "sun gear", that is, the first, second, and third sun gears 111, 121, and 131; the gear located at the outer ring position is called " The outer ring gears, that is, the first, second, and third outer ring gears 114, 124, and 134; the gears that respectively rotate around the first, second, and third sun gears 111, 121, and 131 are called "planetary gears". (planet pinion), that is, the first, second, and third planetary gears 112, 122, and 132.

The first, second, and third planetary gears 112, 122, and 132 in the first, second, and third planetary gear sets 11, 12, and 13 are mostly in groups of three or four, and respectively (Carrier Arm)", that is, the first, second, and third planet carriers 113, 123, 133 maintain the relative positions of the respective first, second, and third planetary gears 112, 122, 132 relative to each other, and the first and second When the three sun gears 111, 121, and 131 are respectively engaged with the first, second, and third planetary gears 112, 122, and 132, the rotation directions thereof must be opposite; however, the first, second, and third outer ring gears 114 When the 124, 134 and the first, second and third planetary gears 112, 122, 132 are engaged and rotated, the rotation directions of the two are the same.

The collar 14 is attached to the periphery of the first planetary gear 11 and the second planetary gear set 12, and further includes: a first one-way clutch 141, a second one-way clutch 142, and a power output end. 143. The first one-way clutch 141 is in mesh with one of the first protruding blocks 115 disposed on the outer ring gear 114 of the first planetary gear set 11; and the second one-way clutch 142 is coupled to the second One of the second projections 125 provided on the outer ring gear 124 of the planetary gear set 12 meshes with each other. The power output end 143 is coupled to the third sun gear 131 of the third planetary gear set 13. The first one-way clutch 141 and the second one-way clutch 142 of the collar 14 are one of a ratchet or a ratchet in the same direction, and, in the embodiment, the first and second one-way clutches Both 141 and 142 are one-way clutches that are in the same direction (can be driven in a clockwise direction and not driven in a counterclockwise direction).

When the first planetary gear set 11 or the second planetary gear set 12 is rotated forward, the first protruding block 115 or the second protruding block 125 is engaged with the first one-way clutch 141 in the collar 14 . Or the second one-way clutch 142, and in turn, the collar 14 is rotated forward. On the other hand, when the first planetary gear set 11 or the second planetary gear set 12 is reversed, the first one-way clutch 141 or the second one-way clutch 142 that are respectively engaged is limited to the one-way rotation characteristic, so that the first planetary gear set 11 or the second planetary gear set 12 is reversed. The first planetary gear set 11 or the second planetary gear set 12 is idling in the collar 14, that is, the collar 14 cannot be driven to perform the reverse operation.

The first sun gear 111 of the first planetary gear set 11 is coupled to the power input end 2, and the outer ring gear 114 of the first planetary gear set 11 and the second planetary gear set 12 are The two sun gears 121 are coaxially connected. When the power input end 2 is driven by the first planetary gear set 11 in the collar 14, at least one of the first planetary gear set 11 or the second planetary gear set 12 in the collar 14 is transmitted through The first one-way clutch 141 or the second one-way clutch 142 drives the collar 14 to rotate forward.

The third planet carrier 133 of the third planetary gear set 13 passes the power from the power output end 143 of the collar 14 through a third one-way clutch 16 to unidirectionally output the kinetic energy limit to a hub 3, That is, the one-way clutch 16 is used to control the third planet carrier 133 to ensure that the hub 3 is rotated in a single direction, and the hub 3 is disposed substantially on the drive wheel of a general wheeled vehicle. Since the third one-way clutch 16 is a commercially available component, it is not the focus of the present invention and will not be further described herein.

The electronically controlled clutch 15 is synchronized with the power input end 2, and may be a normally open solenoid valve. A predetermined current is input to cause an axial displacement of one of the fixed blocks 151 of the electronically controlled clutch 15 for controlling the A third protruding block 135 disposed on the third outer ring gear 134 of the third planetary gear set 13 is fixed or not to control the third outer ring gear 134 to be fixed while the power input end 2 is operating. The end, and thus the power of the power input end 2, is output from the third planet carrier 133 to the hub 3 . Since the electronically controlled clutch 15 is a commercially available component, it is not the focus of the present invention and will not be further described herein.

In the preferred embodiment of the present invention, the power input terminal 2 can be a DC direct current motor, and the DC motor can change the direction of the positive and negative poles of the input current, thereby driving the sun gear 111 of the first planetary gear set 11. Perform forward or reverse. The power input end 2 synchronously activates the electronically controlled clutch 15 during operation to fix the third outer ring gear 134; and when the power input end 2 stops operating, the electronically controlled clutch 15 connects the third outer ring The gear 134 is released, so that the third outer ring gear 134 can be freely rotated to prevent the third planet carrier 133 to which the hub 3 is coupled from locking the internal gear of the third planetary gear set 13 by rotation.

Of course, whether the power input terminal 2 (DC direct current motor) rotates forward or reverse the output, the first planetary gear set 11 or the second planetary gear set 12 can be used to drive the collar 14 to rotate in the same direction. The third planet carrier 133 of the third planetary gear set 13 is further driven to reduce the transmission of the hub 3 .

Referring to FIG. 2, FIG. 2 is a schematic diagram of a first deceleration mode of the motor shifting mechanism of the present invention, wherein the broken line A in FIG. 2 represents the power transmission path of the power input end 2, that is, the power of the first deceleration mode. Transmission path. When the power input terminal 2 (DC DC motor) rotates forward (the following figure rotates with the symbol: +, reverse is represented by the symbol: -), the first sun gear 111 of the first planetary gear set 11 is driven to perform positive The first planetary gear 112 meshed with the first sun gear 111 is operated (reversed) in the opposite direction.

Since the first planetary gear 112 is fixed by the first planet carrier 113, the power output by the first sun gear 111 is transmitted to the first outer gear through the first planetary gear 112 according to the planetary gear transmission principle. The ring gear 114 is coupled to the first planet gear 112 by the first outer ring gear 114. Therefore, the first outer ring gear 114 operates in the same reverse direction as the first planetary gear 112 (reverse rotation).

Because the first outer ring gear 114 is operated in the reverse direction (reverse rotation), the first protruding block 115 disposed on the periphery of the first outer ring gear 114 cannot drive the first single in the collar 14 Forward operation (forward rotation) to the clutch 141 causes the first one-way clutch 141 to assume an idling state (symbol × represents power transmission is invalid), that is, the kinetic energy of the first planetary gear set 11 cannot be transmitted through the first single The clutch 141 is transmitted to the collar 14, and the first outer ring gear 114 is coaxially connected to the second sun gear 121 of the second planetary gear set 12 through a concentric shaft 17 (see FIG. 1). The first outer ring gear 114 and the second sun gear 121 are operated in the same direction (reverse rotation), so that the kinetic energy of the power input end 2 can be directly transmitted to the second through the first planetary gear set 11 Above the planetary gear set 12.

Then, the second sun gear 121 (reverse rotation) of the second planetary gear set 12 transmits the kinetic energy from the first planetary gear set 11 to the meshed second planetary gear 122, so that the first The two planetary gears 122 and the second sun gear 121 operate in opposite directions with each other, and at this time, the second planetary gear 122 assumes a forward operation (forward rotation).

Further, since the second planetary gear 122 is fixed by the second carrier 123, the kinetic energy output by the second sun gear 121 is transmitted to the second through the second planetary gear 122 according to the planetary gear transmission principle. The outer ring gear 124 is coupled to the second planetary gear 122 by the second outer ring gear 124. Therefore, the second outer ring gear 124 and the second planetary gear 122 operate in the same forward direction (forward rotation).

In the above, since the second outer ring gear 124 is operated in the forward direction (forward rotation), the second protruding block 125 disposed on the periphery of the second outer ring gear 124 will drive the inner portion of the collar 14 The second one-way clutch 142 performs a forward operation (forward rotation), that is, the kinetic energy of the second planetary gear set 12 is transmitted to the collar 14 through the second one-way clutch 142, thereby the first planetary gear The kinetic energy after the accumulated deceleration of the group 11 and the second planetary gear set 12 is coaxially connected to the third sun gear 131 of the third planetary gear set 13 through the power output end 143, and further by the third planetary gear set 13 The third planet carrier 133 outputs the kinetic energy of the deceleration through the third one-way clutch 16 to the hub 3 in one direction.

That is, in the first deceleration mode of the present invention, the power input terminal 2 (DC DC motor) is a forward rotation output, and the input kinetic energy is transmitted through the sleeve through the first and second planetary gear sets 11 and 12. The power output end 143 of the ring 14 is transmitted to the third planetary gear set 13, but the first outer ring gear 114 (reverse) of the first planetary gear set 11 cannot drive the first one in the collar 14. The one-way clutch 141 performs forward rotation (in a reverse idling state), so that the kinetic energy of the first planetary gear set 11 is outputted to the second planetary gear set 12 through the concentric shaft 17, and the second outer ring is utilized. The gear 124 (forward rotation) drives the second one-way clutch 142 in the collar 14 to rotate forward, thereby driving the power output end 143 of the collar 14 to rotate forward, and the sleeve is transmitted through the power output end 143. The kinetic energy of the deceleration accumulated by the first and second planetary gear sets 11 and 12 in the ring 14 is transmitted to the third sun gear 131 (forward rotation) of the third planetary gear set 13 and is controlled by the electronically controlled clutch 15 Fixing the third outer ring gear 134 to fix the third planetary gear 132 (reverse) The kinetic energy of the carrier 133 will decelerate through the third one-way clutch 16 to the output of the unidirectional kinetic limit Hub Shell 3.

For example, in the preferred embodiment of the present invention, the power input terminal 2 (DC DC motor) rotates at 4000 rpm (number of revolutions per minute), and the first, second, and third planetary gear sets 11, 12 The number of teeth of the teeth 13 is as follows: the number of teeth of the first, second, and third sun gears 111, 121, and 131 is: 25 teeth; the number of teeth of the first, second, and third planetary gears 112, 122, and 132 is : 26 teeth; and the number of teeth of the first, second, and third outer ring gears 114, 124, and 134 are: 77 teeth.

It is calculated from the above data that the gear reduction ratio of the first and second planetary gear sets 11 and 12 is 3.08, and the gear reduction ratio of the third planetary gear set 13 is 4.08.

In the first deceleration mode of the motor shifting mechanism 1 of the present invention, the power input terminal 2 (DC DC motor) is fed in a forward direction, passing through the first and second planetary gear sets 11, 12 in the collar 14. After the deceleration of the third planetary gear set 13, the motor shifting mechanism 1 of a high torque and low rotation speed is obtained; wherein the calculation formula of the rotational speed rpm of the power input end 2 (DC direct current motor) outputted to the hub 3 is as follows:

3.08×3.08×4.08=38.7 [Gear reduction ratio accumulated through the first, second, and third planetary gear sets]

4000 (rpm) [power input speed] ÷ 38.7 = 103.35 (rpm) [flower shell speed]

Therefore, in the first deceleration mode, the power input terminal 2 (DC DC motor) is reduced from the original 4000 rpm output to the 103.35 rpm through the motor shifting mechanism 1 and output to the hub 3 to achieve the low speed and high torque.

Referring to FIG. 3, FIG. 3 is a schematic diagram of a second deceleration mode of the motor shifting mechanism of the present invention, wherein the broken line B in FIG. 2 represents the power transmission path of the power input end 2, that is, the power of the second deceleration mode. Transmission path. When the power input terminal 2, that is, the DC DC motor reverses (reverses) the output power (the following figure rotates with the symbol: +, reverses with the symbol: one), the first planetary gear set 11 is driven. The first sun gear 111 performs reverse operation (reversal), and the first planetary gear 112 meshed with the first sun gear 111 operates in a forward direction (forward rotation).

Since the first planetary gear 112 is fixed by the first planet carrier 113, the power output by the first sun gear 111 is transmitted to the first outer gear through the first planetary gear 112 according to the planetary gear transmission principle. The ring gear 114 is coupled to the first planet gear 112 by the first outer ring gear 114. Therefore, the first outer ring gear 114 operates in the same forward direction as the first planetary gear 112 (forward rotation).

Because the first outer ring gear 114 is in the forward direction (forward rotation), the first protruding block 115 disposed on the periphery of the first outer ring gear 114 will drive the first single in the collar 14 The forward operation (forward rotation) of the clutch 141 is performed such that the kinetic energy of the first planetary gear set 11 is transmitted to the collar 14 through the first one-way clutch 141.

The first outer ring gear 114 is coaxially connected to the second sun gear 121 of the second planetary gear set 12 through the concentric shaft 17 , so that the first outer ring gear 114 and the second sun gear 121 operate in the same direction ( Forward). The second sun gear 121 (forward rotation) of the second planetary gear set 12 transmits kinetic energy from the first planetary gear set 11 to the meshed second planetary gear 122 to make the second planet The gear 122 and the second sun gear 121 operate in opposite directions with each other, and the second planetary gear 122 assumes a forward operation (reverse rotation).

Further, since the second planetary gear 122 is fixed by the second carrier 123, the kinetic energy output by the second sun gear 121 is transmitted to the second through the second planetary gear 122 according to the planetary gear transmission principle. The outer ring gear 124 is coupled to the second planetary gear 122 by the second outer ring gear 124. Therefore, the second outer ring gear 124 operates in the same reverse direction as the second planetary gear 122 (reverse rotation).

Because the second outer ring gear 124 is operated in the reverse direction (reverse rotation), the second protruding block 125 disposed on the periphery of the second outer ring gear 124 cannot drive the second single in the collar 14 Forward operation (forward rotation) to the clutch 142 causes the second one-way clutch 142 to assume an idling state (symbol × represents power transmission is invalid), that is, the kinetic energy of the second planetary gear set 11 cannot be transmitted through the second single The clutch 141 is transmitted to the collar 14. At this time, only the first planetary gear set 11 in the collar 14 effectively decelerates the power input end 2 through the first one-way transmission 141, and further decelerates the first planetary gear set 11 The kinetic energy is coaxially connected to the third sun gear 131 of the third planetary gear set 13 through the power output end 143, and the kinetic energy after deceleration is passed through the third planet carrier 133 of the third planetary gear set 13 The three-way clutch 16 outputs a kinetic energy limit to the hub 3 in one direction.

That is, in the second deceleration mode of the present invention, the power input terminal 2 (DC DC motor) is an inverted output, and since the second planetary gear set 12 is in the reverse idling state in the collar 14, The collar 14 cannot be driven to perform a forward operation (forward rotation), and only the first planetary gear set 11 in the collar 14 transmits the input kinetic energy to the power output end 143 of the collar 14 to the first The third planetary gear set 13 transmits the kinetic energy of the first planetary gear set 11 in the collar 14 to the third sun gear 131 of the third planetary gear set 13 through the power output end 143 (forward rotation) And the third outer ring gear 134 is fixed by the electronically controlled clutch 15, so that the third planet carrier 133 that fixes the third planetary gear 132 (reverse) passes the decelerated kinetic energy through the third one-way. The clutch 16 outputs a kinetic energy restriction to the hub 3 in one direction.

In the second deceleration mode of the motor shifting mechanism 1 of the present invention, the power input terminal 2 (DC DC motor) reverses the input at 4000 rpm, and the first, second, and third planetary gear sets 11, 12, 13 The gear reduction ratio is the same as that of the first reduction module. After the first planetary gear set 11 in the collar 14 is decelerated by the third planetary gear set 13, the motor is shifted to a low torque and high speed. The mechanism 1; wherein the power input end 2 (DC DC motor) outputs the rotational speed rpm of the hub 3 is calculated as follows:

3.08×4.08=12.57 [Gear reduction ratio accumulated through the first and third planetary gear sets]

4000 (rpm) [power input speed] ÷ 12.57 = 318.22 (rpm) [flower shell speed]

Therefore, in the second deceleration mode, the power input end 2 (DC DC motor) is reduced from the original 4000 rpm output to the 318.22 rpm through the motor shifting mechanism 1 and output to the hub 3 to achieve high speed and low torque.

According to the above, the motor shifting mechanism 1 of the present invention shown in FIG. 2 and FIG. 3 can change the output speed of the power input end 2 by controlling the power input end 2, that is, the DC direct current motor is reversed, forming the first And the second deceleration mode alternately switches to provide different reduction ratios, further achieving the output of the transformation speed and the torsion, and selecting different gear positions (deceleration mode) according to different characteristics required for starting, climbing, and patrolling, and different road conditions. This makes the power input terminal 2 more efficient.

The power input end 2 is reversed and transmitted through the first planetary gear set 11, the second planetary gear set 12, and the third planetary gear set 13 for variable speed transmission, and another advantage is that during the shifting process In the conventional gear shifting, the friction generated by the clutch or the power path during switching is dealt with to reduce the wear loss between the transmission components, and the user can easily shift gears.

In summary, the motor shifting mechanism 1 of the present invention uses the power input terminal 2 (DC DC motor) to change the positive and negative poles of the input current, thereby changing the forward or reverse rotation of the power input terminal 2 to shift the motor. The mechanism 1 forms an output having a first and a second deceleration mode to provide different deceleration ratios for mutual switching, further achieving a transformation speed and a torque.

In the first deceleration mode, the power input terminal 2 (DC DC motor) is rotated forward and cooperates with the first and second planetary gear sets 11 and 12 in the collar 14 to perform cumulative deceleration, because the first The second planet carrier 113, 123 is a fixed end, and the first and second one-way clutches 141, 142 on the collar 14 are limited to the positive operation (forward rotation), so the first outer The ring gear 114 is reversely operated (reversed), further causing the first bump 115 on the first outer ring gear 114 to assume an idling state on the first one-way clutch 141, and accumulating the kinetic energy after deceleration and Passing to the second planetary gear set 12, and driving the second one-way clutch 142 through the second protruding block 125 on the second outer ring gear set 124 for forward operation (forward rotation), thereby making the collar The third sun gear 131 of the third planetary gear set 13 coaxially connected to the power output end 143 14 is operated in the forward direction (forward rotation), and the third outer ring gear 134 is controlled by the electronically controlled clutch 15 Fixing, the third planet carrier 133 fixing the third planetary gear 132 (reverse rotation) passes the kinetic energy after deceleration through the third The one-way clutch 16 outputs the kinetic energy restriction to the hub 3 in one direction.

In addition, in the second deceleration mode, the power input terminal 2 (DC DC motor) is used to reversely operate and cooperate with the first planetary gear set 11 in the collar 14 for deceleration, due to the first and second The planet carriers 113 and 123 are fixed ends, and the first and second one-way clutches 141 and 142 in the collar 14 are limited to operate in the forward direction (forward rotation), while the reverse direction is idling. The state cannot drive the collar 14 to rotate forward. Therefore, when the first outer ring gear 114 is in the forward direction (forward rotation), the first protrusion 115 on the first outer ring gear 114 is further caused by the The first one-way clutch 141 drives the collar 14 to perform forward operation (forward rotation).

The first outer ring gear 114 is coaxially connected with the second sun gear 121 of the second planetary gear set 12 by the concentric shaft 17, so that the second outer ring gear set 124 is reversely operated (reversed). The second protruding block 125 can not drive the second one-way clutch 142 to perform a forward operation (presenting an idling state), so that only the first planetary gear set 11 in the collar 14 can effectively transmit the power input end 2 The first one-way transmission 141 performs a deceleration operation, and the kinetic energy of the first planetary gear set 11 is further coaxially connected to the third sun gear 131 of the third planetary gear set 13 through the power output end 143 and is positive To the operation (forward rotation), the third outer ring gear 134 is fixed by the electronically controlled clutch 15, so that the third planet carrier 133 that fixes the third planetary gear 132 (reverse rotation) passes the kinetic energy after deceleration The third one-way clutch 16 outputs the kinetic energy restriction to the hub 3 in one direction.

The above-mentioned embodiments are not intended to limit the scope of application of the present invention, and the scope of the present invention should be based on the technical spirit defined by the content of the patent application scope of the present invention and the scope thereof. It is to be understood that the scope of the present invention is not limited by the spirit and scope of the present invention, and should be considered as a further embodiment of the present invention.

1‧‧‧Motor shifting mechanism

11‧‧‧First planetary gear set

111‧‧‧First sun gear

112‧‧‧First planetary gear

113‧‧‧First planet carrier

114‧‧‧First outer ring gear

115‧‧‧First protruding block

12‧‧‧Second planetary gear set

121‧‧‧second sun gear

122‧‧‧Second planetary gear

123‧‧‧Second planet carrier

124‧‧‧Second outer ring gear

125‧‧‧second protruding block

13‧‧‧The third planetary gear set

131‧‧‧ Third Sun Gear

132‧‧‧ Third planetary gear

133‧‧‧The third planet carrier

134‧‧‧ Third outer ring gear

135‧‧‧ third protruding block

14‧‧‧ collar

141‧‧‧First one-way clutch

142‧‧‧second one-way clutch

143‧‧‧Power output

15‧‧‧Electric clutch

151‧‧‧Fixed block

16‧‧‧ third one-way clutch

17‧‧‧ concentric axis

2‧‧‧Power input

3‧‧‧Flower shell

Figure 1 is a perspective exploded view of the motor shifting mechanism of the present invention.

Figure 2 is a schematic view of the first deceleration mode of the motor shifting mechanism of the present invention.

Figure 3 is a schematic view of the second deceleration mode of the motor shifting mechanism of the present invention.

1. . . Motor shifting mechanism

11. . . First planetary gear set

111. . . First sun gear

112. . . First planetary gear

113. . . First planet carrier

114. . . First outer ring gear

115. . . First protruding block

12. . . Second planetary gear set

121. . . Second sun gear

122. . . Second planetary gear

123. . . Second planet carrier

124. . . Second outer ring gear

125. . . Second protruding block

13. . . Third planetary gear set

131. . . Third sun gear

132. . . Third planetary gear

133. . . Third planet carrier

134. . . Third outer ring gear

135. . . Third protruding block

14. . . Collar

141. . . First one-way clutch

142. . . Second one-way clutch

143. . . Power output

15. . . Electronically controlled clutch

151. . . Fixed block

16. . . Third one-way clutch

17. . . Concentric axis

2. . . Power input

3. . . Flower shell

Claims (14)

A motor shifting mechanism is driven through a power input end, comprising: a first planetary gear set comprising: a first sun gear, a plurality of first planet gears, a first planet carrier, and a first An outer ring gear; wherein the power input end is coupled to the first sun gear to transmit power; and the first planet carrier is a fixed end such that the first planetary gear trains pass through the first planet carrier Fixed; a second planetary gear set comprising: a second sun gear, a plurality of second planet gears, a second planet carrier, and a second outer ring gear; wherein the first outer ring gear and the a second sun gear is coupled to transmit power; and the second planet carrier is a fixed end such that the second planet gear trains are fixed through the second planet carrier; and a set of rings to which the sleeve is attached The periphery of the first and second planetary gear sets includes: a first one-way clutch, a second one-way clutch, and a power output end; wherein the first one-way clutch is in engagement with the first outer ring gear And The second one-way clutch is meshed with the second outer ring gear, and the first and second one-way clutches are one-way clutches in the same direction; in addition, the power output end is connected to the collar to output power; Therefore, whether the power input end is forward or reverse, the first planetary gear set or the second planetary gear set can be used to drive the collar to perform forward rotation in the same direction. The motor shifting mechanism of claim 1, further comprising: a third planetary gear set comprising: a third sun gear, a plurality of third planet gears, a third planet carrier, and a a third outer ring gear; wherein the third sun gear train is coupled to the power output end, and the plurality of third planet gears are connected in series through the third planet carrier, and the kinetic energy is outputted to a hub. The motor shifting mechanism of claim 1, wherein the power input end is a DC motor. The motor shifting mechanism of claim 1, wherein the first one-way clutch and the second one-way clutch of the collar are one of a ratchet or a ratchet in the same direction. The motor shifting mechanism of claim 2, further comprising a third one-way clutch for controlling the third planet carrier to restrict the hub of the hub from rotating in a single direction. The motor shifting mechanism of claim 2, further comprising an electronically controlled clutch system operating synchronously with the power input end and controlling whether the third outer ring gear of the third planetary gear set is fixed. The motor shifting mechanism according to claim 6, wherein the electronically controlled clutch is a normally open solenoid valve, and a predetermined current is input to cause an axial displacement of the solenoid valve, thereby causing the third planetary gear The third outer ring gear of the set is fixed. A motor shifting mechanism is driven through a power input end, comprising: a first planetary gear set, further comprising: a first sun gear, a plurality of first planet gears, a first planet carrier, and a First outside a second planetary gear set, further comprising: a second sun gear, a plurality of second planet gears, a second planet carrier, and a second outer ring gear; a third planetary gear set including a third sun gear, a plurality of third planet gears, a third planet carrier, and a third outer ring gear; and a set of rings attached to the periphery of the first and second planetary gear sets, The method further includes: a first one-way clutch, a second one-way clutch, and a power output end; wherein the power input end is coupled to the first sun gear, thereby driving the plurality of fixed by the first planet carrier The first planetary gear indirectly drives the first outer ring gear to mesh the first outer ring gear with the first one-way clutch in the collar, and the first outer ring gear and the second sun gear The coaxial connection further drives the second planetary gear fixed by the second planet carrier to indirectly transmit the second outer ring gear, so that the second outer ring gear meshes with the second one-way clutch of the collar, and The power output end and the third too A gear connected to the third carrier and the use of a plurality of third planetary gears to be connected in series, and a hub shell to output the kinetic energy. The motor shifting mechanism of claim 8, wherein the power input end is a DC motor. The motor shifting mechanism of claim 8, wherein the first one-way clutch and the second one-way clutch of the collar are one of a ratchet or a ratchet in the same direction. The motor shifting mechanism of claim 8, wherein the electronically controlled clutch is a normally open solenoid valve, and a predetermined current is input to cause axial displacement of the solenoid valve, thereby causing the third planetary gear The third outer ring gear of the set is fixed. The motor shifting mechanism of claim 8, further comprising a third one-way clutch for controlling the third planet carrier to restrict the hub of the hub from rotating in a single direction. The motor shifting mechanism of claim 8, further comprising an electronically controlled clutch system operating synchronously with the power input end and controlling whether the third outer ring gear of the third planetary gear set is fixed. The motor shifting mechanism of claim 13, wherein the electronically controlled clutch is a normally open solenoid valve, and a predetermined current is input to cause an axial displacement of the solenoid valve, thereby causing the third planetary gear The third outer ring gear of the set is fixed.