TWI444546B - Power transmission system with a rear clutching apparatus - Google Patents

Description

Power transmission system with rear clutch device

The present invention relates to a power transmission system with a clutch device, and more particularly to a power transmission or supply system that utilizes a rear clutch device for external force intervention or not to control a power output mode.

Press, generally the power supply system of the transmission (or transmission) and the clutch, the power output system and the power transmission system are generally arranged as shown in Figure 1; wherein the power (from the original power source output or other power conversion device) The output is input from one end of the clutch 1, and the clutch 1 controls whether or not the power is output or transmitted to the second transmission 2, and the power is converted to the torque and torque via the transmission 2, and then directly outputted from the end thereof.

In the prior art, the operation of the clutch 1 relay power is usually a single speed input and output, and is not used as a shifting function. The transmission 2 transmits the power (rotation, direction and torque) of the appropriate demand to the subsequent power application system after receiving the power input controlled by the clutch 1 and selecting (manual or automatic) via the appropriate shift speed. And device (not shown). Basically, the operation of the clutch 1 is not involved in the function of changing the nature of the output power.

The power transmission system as described above is a system in which the clutch 1 is disposed in front of the transmission 2; and in the prior art, there is also a system as shown in Fig. 2, in which the setting of the clutch 1 is provided. The position is after the transmission 2, that is, the power input is directly shifted by the transmission 2, and then the output is determined by the clutch 1.

The power output system of the present invention is similar to the system with the rear clutch device shown in Fig. 2, but the power output path is completely out of the clutch 1, and the application range is better in the light load power system. (such as electric bicycles, lawn mowers, and even bicycles, etc.), especially the power transmission system hidden in the hub of the flower drum.

The main object of the present invention is to provide a power transmission system having a rear clutch device which can be integrated into a hub and can be controlled by external force input to achieve power output or not (open or interrupt power transmission) clutch type Power transmission.

Another object of the present invention is to provide a power transmission system having a rear clutch device, the clutch of which only provides a force fulcrum of the power transmission system, so that the power transmission path of the power transmission system does not pass through the clutch, thereby reducing The load of the clutch is to meet the needs of the light load power system.

In the present invention, the power transmission system having the rear clutch device is disposed according to a fixed axis, and includes a power source, a transmission, a clutch, and a clutch transmission group controlled by an external force.

The transmission is connected to the power source for direct speed conversion of the power output from the power source, and may also include a terminal planetary gear train as the output end of the power. The planetary gear train may further include a sun gear pivoted on the shaft and driven by the power source, a planet carrier, a ring gear, and a plurality of pivoting on the planet carrier and meshing between the sun gear and the ring gear. Planetary gear.

The clutch is controlled by the external force through the clutch transmission group to determine whether to open or interrupt the output path of the power source; when there is no external force input, the clutch is in a state of structural slippage and non-engagement with the planetary gear train, that is, the clutch is not Providing any force fulcrum of the planetary gear train, the planetary gear of the planetary gear train (driven by the sun gear) is in an idling state; and when an external force is transmitted through the clutch transmission, the clutch is in a structural engagement with the planetary gear train. The planetary gear train has an appropriate force fulcrum to open the output path of the power source, and the planetary gear train can output power to the hub by one of the planet carrier or the ring gear.

When there is no external force, the clutch system does not form a fulcrum relationship with the carrier and the ring gear. At this time, the planetary carrier and the ring gear of the planetary gear train are in an idling state, so that the power cannot be output to the hub. When the external force intervenes, the clutch is in a proper fulcrum relationship with the carrier and the ring gear. Therefore, the power transmitted by the power source to the sun gear will be determined by the steering of the sun gear to pass through the planetary gear drive ring. The gear is either output via one of the planet carriers.

In an embodiment of the present invention, the power transmission system having the rear clutch device may further include a hub, and the power source, the transmission, the clutch, and the clutch transmission are mostly disposed in the hub, and the ring gear and the carrier The one-way clutch combination is formed by one of the hub shells of the hub of the flower drum shell.

In an embodiment of the present invention, the clutch of the power transmission system having the rear clutch device may further include a ring gear control cam mechanism for controlling the fulcrum operation of the ring gear, and a planet for controlling the fulcrum operation of the carrier. The frame controls the cam mechanism.

In an embodiment of the present invention, in the clutch of the power transmission system having the rear clutch device, the ring gear control cam mechanism and the carrier control cam mechanism are two interlocking but discrete cam and follower pairs. In the ring gear control cam mechanism, the cam profile is controlled by one of the external forces to control the chute, and the follower is a fixed fulcrum pawl. In the planetary frame control cam mechanism, the cam profile is a bump guiding arm that is activated by an external force, and the driven component is a telescopic bump of the planet carrier disposed on the planet carrier.

In an embodiment of the invention, the ring gear control cam mechanism and the carrier control cam mechanism of the power transmission system having the rear clutch device are mainly two cam and follower pairs built in the same plate body. In the ring gear control cam mechanism, the cam profile is controlled by one of the external forces to control the chute, and the follower is a fixed fulcrum pawl; and in the carrier control cam mechanism, the cam profile is matched with The external force acts on one of the bump guiding arms, and the driven member is one of the planet carrier telescopic bumps on the planet carrier.

In an embodiment of the present invention, the clutch of the power transmission system having the rear clutch device may further include a fulcrum mount fixedly coupled with the shaft center, and the ring gear control cam mechanism may further include a pedestal mount a side ring gear control cam, a plurality of pawl through holes provided at an inner edge of the rib ring of the fulcrum fixing seat, and a fulcrum pawl individually pivoted in the pawl through hole and exposed on both sides of the rib ring, the ring gear The control cam may further comprise a plurality of control chutes corresponding to the pawl through holes on the fulcrum mounts and the fulcrum pawls; when the external force intervenes to make the clutch perform a point operation, the drive ring gear control cam performs the forward rotation At this time, the fulcrum pawl is slid from the first end of one of the control chutes to the second end of the other side to urge the fulcrum pawl to jack up and form a unidirectional consolidation state with the ring gear, thereby Make the ring gear in a single In the direction of rotation (reverse rotation), the fulcrum pawl abuts and becomes the fulcrum of the operation of the planetary gear train, so that the sun gear can output power through the planetary carrier in a single rotation (forward rotation) direction. When the external force on the clutch is removed, the return torsion spring, that is, the drive ring gear control cam returns to the original one end position, so that the fulcrum pawl is closed downward and no longer meshes with the ring gear, whereby the ring gear is even subjected to the planet When the gear is driven, whether it is forward or reverse, it will be in an idling state and the power cannot be output from the carrier.

In an embodiment of the present invention, the clutch of the power transmission system having the rear clutch device may further include a fulcrum mount fixedly coupled with the shaft center, and the carrier control cam mechanism may further include a pedestal mount adjacent to the planet a planet carrier control cam, a plurality of planet carrier telescopic bumps disposed on the planet carrier and elastically protruding toward the planet carrier control cam, and a plurality of bump cards disposed on the fulcrum mount and corresponding to the telescopic bumps of the planet carrier The hole, the position of the telescopic bump of the planet carrier, and the outer edge of the planet carrier control cam are further protruded and provided with a plurality of fulcrum guiding arms, and the configuration of the bump guiding arm is outward and toward one side of the fulcrum fixing seat, and Extend a predetermined length in one direction. When the clutch is not subjected to an external force, the return torsion spring provides a restoring force to drive the bump guiding arm of the carrier control cam to rotate to the front edge of the corresponding planetary telescopic bump, and the pushing and guiding action of the bump guiding arm The "shovel" of the telescopic bump of the self-anchored bump is separated from the anchor hole to separate the planet carrier from the fulcrum mount, resulting in no force fulcrum on the planet carrier; at this time, the power input by the sun gear, That is, because the planet carrier is not subjected to the force fulcrum, it is idling and cannot output power from the ring gear. When the external force drives the clutch to rotate forward, the bump guiding arm of the carrier control cam rotates forward to a position away from the corresponding convex hole, so that the telescopic protrusion of the carrier is seated (engaged). In the corresponding bump hole, the fixing relationship between the clutch and the carrier is stabilized in one direction, so that the carrier is caught by the convex hole in the single rotation (reverse rotation) direction and becomes a planetary gear. The fulcrum of the operation; at this time, the power input by the sun gear on a single (reverse rotation) steering can be forward-rotated through the planetary gear drive ring gear.

In an embodiment of the present invention, the clutch transmission set of the power transmission system having the rear clutch device may further include a transmission member for external force input, a transmission pawl holder driven by the transmission member, and a power transmission directly to The transmission component of the clutch; wherein a C-shaped torsion spring is disposed between the transmission pawl seat and the transmission member as a linkage buffer between the two.

In order to enable the reviewing committee to have a further understanding and understanding of the features, objects and functions of the present invention, the detailed description of the drawings is as follows: Please refer to Figure 3 for the power transmission of the rear clutch device of the present invention. Schematic diagram of system configuration of the system; compared with the system shown in FIG. 2, the clutch 1 of the power transmission system of the present invention is disposed at a position after the transmission 2, that is, the power input is directly shifted by the transmission 2, and then the clutch 1 decide whether to output, the difference is that the transmission 2 of the present invention is a transmission structure having the output of the final planetary gear train 3, and the edge is the output which can be generated at three different positions: the idle state of the state N is not output. The state, the output of the sun gear when it is rotating forward (state +), and the output of the sun gear when it is reversed (state -), and the clutch 1 of the present invention is used to determine or control whether the power of the power source will pass through the planetary gear train. Output 』? Obviously, the focus of the present invention is: because the planetary gear train 3 is changing The setting of the terminal 2 of the speeder 2 is such that the clutch 1 device and the overall power transmission system have the meaning of "determining the opening and closing of the power path by controlling the supply or not of the fulcrum of the planetary gear train 3".

Please refer to FIG. 4, which is a schematic structural view of a preferred embodiment of a power transmission system having a rear clutch device according to the present invention. In this embodiment, the power transmission system of the present invention is implemented in a hub of a rotatable wheel. It is known to those skilled in the art that the application of the present invention can be similarly implemented in other transmission systems after a slight change. in.

As shown in the figure, in this embodiment, the power transmission system of the present invention is built in a hub 5 for driving the hub 5 to rotate, which is disposed according to a fixed axis 10, which may include a A power source 100, a transmission 2 having a terminal planetary gear train 3, and a clutch 1.

The power source 100 is used to provide power for the rotation of the hub, and the implementation can provide a structure for an electric motor or other similar power.

The transmission 2 is configured to perform a speed change (generally deceleration) of the power output from the power source 100, and includes a plurality of rotatable transmission portions therein. In the present embodiment, the plurality of transmission portions of the transmission 2 further include a terminal planetary gear train 3 as an output of power. The planetary gear train 3 includes a sun gear 31 pivotally mounted on the shaft core 10 and driven by the power source 100 directly or indirectly (depending on the structural composition of the transmission 2), a carrier 32, a ring gear 34, and The planetary carrier 32 is pivoted and meshed with a plurality of planetary gears 33 that are rotated between the sun gear 31 and the ring gear 34. As shown, the planetary gear train 3 can output power to the outer rotating drum shell 5 by the ring gear 34 (when the sun gear 31 is reversed) or the planet carrier 32 (when the sun gear 31 is rotating forward), and thus Drive the flower drum shell 5 forward.

The clutch 1 controls the internal components by a pedal, manual, electric or other means to control whether the power of the planetary gear train 3 can be output to the hub 5 or can only be idling, in other words, Clutch 1 is a "Switch" role that acts as a power output without transmitting power. In the present invention, the clutch 1 is capable of successfully performing its "closing power path", and both the ring gear 34 of the planetary gear train 3 and the carrier 32 are simultaneously in a state of no force fulcrum, so that the sun gear 31 is The different power paths transmitted by both the forward rotation and the reverse rotation can only cause the idling motion of the ring gear 34 and the carrier 32 to rotate the hub 5 (i.e., the rotational power cannot be output to the hub 5).

In the present invention, when no external force is applied to the clutch 1, the clutch 1 is in the position of "closing the power path". At this time, the ring gear 34 of the planetary gear train 3 and the carrier 32 are both in the axial center. 10 Freewheeling (ie, idling) state of consolidation. Therefore, regardless of whether the sun gear 31 is rotated forward or reverse by the driving of the power source 100, the rotational power of the sun gear 31 can only cause the ring gear 34 and the carrier 32 to idle without any rotational power being transmitted to the hub 5 . That is, when the clutch 1 is in the position of "closing the power path", the planetary gear train 3 cannot generate any power that can be output to the hub 5 .

When the external force is actuated by the clutch 1 to "turn on the power path", the ring gear 34 of the planetary gear train 3 and the carrier 32 are both fixed in the single direction (reverse direction) with the axis 10, and the other direction ( Forward direction) One-way locked state of slippage. In the present embodiment, when the external force is transmitted through the clutch 1 to "turn on the power path", the ring gear 34 is reversed in itself. In the direction of rotation, it will be locked by the one-way of the clutch 1, and will slip forward with the clutch 1 in the forward direction and can be rotated forward; at the same time, the carrier 32 will also be subjected to the single of the clutch 1 in its own reverse direction. When it is locked and in the forward direction, it will slip off the clutch 1 and can be rotated forward.

Thereby, when the power source 100 drives the sun gear 31 to rotate forward, the ring gear 34 will be locked by the clutch 1 and cannot be reversely rotated, but at this time, the carrier 32 is not locked by the clutch 1 because it is rotating in the forward direction. Therefore, the clutch 1 can provide a force fulcrum to the ring gear 34, so that the forward rotational power of the sun gear 31 is outputted to the outer rotating rat shell 5 by the forwardly rotating planet carrier 32. When the power source 100 drives the sun gear 31 to reverse, the ring gear 34 is not locked by the clutch 1 because it is rotating in the forward direction, but at this time, the carrier 32 will be locked by the clutch 1 and cannot be reversely rotated. Therefore, the clutch 1 will provide a force fulcrum to the carrier 32, so that the reverse rotation power of the sun gear 31 is outputted to the outer rotating drum shell 5 by the forwardly rotating ring gear 34.

In the present invention, the ring gear 34 and the one-way clutch connection between the carrier 32 and the hub 5 can adopt a mechanism of a ratchet ring ratchet ring and a one-way pawl as an intermediary combination of the one-way clutch 200. Clutch 200 is a skill that is familiar to those skilled in the art, and the details of its implementation are not described herein.

The implementation of the transmission 2 of the present invention is not strictly limited to a shifting mechanism that must be completely composed of a planetary gear train, but only a planetary gear that is defined as a planetary gear train in its terminal transmission phase, and this terminal shifting gear The input is the sun gear, and the output is the planet carrier. Or one of the ring gears. In the following embodiment of the invention of the present invention, a planetary gear train is employed as a single structure of the transmission 2, omitting any conduction mechanism that may exist between the terminal planetary gear train and the power source 100, thereby simplifying the familiarity of those skilled in the art. Understanding of technology. However, those skilled in the art should also know that a terminal planetary gear train is not a necessary condition for the implementation of the transmission 2 in the present invention. The transmission 2 only in the form of a single planetary gear train is not the only implementation of the transmission 2 of the present invention. . In the case of being implemented in a non-terminal planetary gear train, the present invention "clutch closing/opening the power path mode downstream of the transmission" can also be easily applied thereto, for example, in a single output mode transmission state, the clutch of the present invention It is only necessary to "lock" the single power path, and it is not necessary to "lock" the ring gear 34 of the planetary gear train 3 and the carrier 32 in the reverse direction as in the disclosed embodiment.

Please refer to Fig. 5 and Fig. 6 (see also Fig. 4), which are exploded views of the detailed description of the components of the embodiment shown in Fig. 4, and a schematic cross-sectional view of the combination. The embodiment is implemented in a hub 5, and the power source 100, the transmission 2, the clutch 1 and the clutch transmission group 4 are sequentially constructed according to the fixed axis 10 on the center line of the flower drum shell 5, in cooperation with the power transmission system of the present invention. The arrangement between the flower drum shell 5 and the system as the rotational output comprises a right ratchet ring 51, a hub shell ratchet ring 53 fixed in the hub 5 as a system output intermediate member, and a left side bead on the other side. The bowl 55, and one of the other side seals, is a left side cover 57 of the hub.

As shown in the figure, the power source 100 implemented by the motor in this embodiment is constructed on one side (left side) of the hub 5, and includes a motor stator bracket. 101 and a motor rotor 103.

The transmission 2 connected to the power source 100 is implemented by a single planetary gear train 3, and further includes a sun gear 31 pivotally mounted on the shaft core 10 and directly driven by the power source 100, a carrier 32, a ring gear 34, and The planetary carrier 32 is pivoted and meshed with a plurality of planetary gears 33 (three shown) that are rotated between the sun gear 31 and the ring gear 34.

Referring to FIG. 6 and FIG. 7, FIG. 7 is for showing the corresponding relationship between the carrier 32, the ring gear 34 and the hub shell ring 53 of the hub. As shown in the figure, the output of the planetary gear train 3 can be output from one of the ring gear 34 or the carrier 32 to the rotary drum of the rotating drum through the hub of the ratchet ring 53 to the outer rotating drum. Shell 5. In terms of design, in order to be able to use a single component, that is, a flower ratchet ratchet ring 53, as a common output member of the ring gear 34 and the carrier 32, the outer diameter of the ring gear 34 or the carrier 32 is constructed. The power output end is approximately the same size so that the selective output between the two and the hub ratchet ring 53 can be conveniently implemented. In this embodiment, the combination of the ring gear 34 and the hub shell ratchet ring 53 and the combination of the planet carrier 32 and the hub shell ratchet ring 53 are in the form of a ratchet ring with a pawl and a one-way bite. The one-way clutch 200 is the same.

As shown in Fig. 7, the ring gear 34 of the present invention may further include a ring gear tooth portion 341 that meshes with the planet gears 33, and a ring gear ratchet portion 343 that is adjacently controlled by the clutch 1.

Please refer to FIG. 8 , which is an exploded perspective view of the main components of the clutch 1 of the power transmission system of the rear clutch device of the present invention; as described above, the clutch 1 of the present invention is operated by external force control to determine the planet. The output mode of the gear train 3. In addition, the force is input by the clutch transmission group 4, and the implementation direction is the feed from the second direction of the figure to the first direction. The feed operation also stores the potential energy in the return torsion spring 19 to After the external force is removed, the state of the clutch 1 is automatically restored (inward from the first direction to the second direction) to the "closed power path" position of "while the carrier 32 and the ring gear 34 are idling".

As shown in the figure, the clutch 1 in this embodiment mainly includes a fulcrum fixing seat 11 which is fixedly coupled with the shaft core 10 and cannot rotate, and a ring gear control cam 13 which is disposed on the fulcrum fixing seat 11 and the clutch transmission group 4. a planet carrier control cam 15 disposed on the other end surface of the fulcrum mount 11 , a plurality of planet carrier telescopic bumps 17 disposed on the planet carrier 32 and elastically protruding or contracting toward the planet carrier control cam 15 (shown as Three), and a set of return torsion springs 19 provided on the center flange of the fulcrum mount 11 (see Figure 6).

The fulcrum mount 11 is a fixed ring body, and is provided with a central peripheral rib ring 111, a plurality of pawl through holes 113 (three shown) disposed on the inner edge of the rib ring 111, and a plurality of corresponding planets. The bump holes 115 (three are shown) of the telescopic bumps 17 and the fulcrum pawls 201 that are individually pivoted in the pawl through holes 113 and exposed on both sides of the rib ring 111.

The ring gear control cam 13 is disposed on one side of the transmission member 45 of the fulcrum fixed seat 11 near the clutch transmission group 4, and is coupled with the transmission member 45, and further includes driving of the driving cylinder 451 on the plurality of corresponding transmission members 45. The input member 131 (three shown) and a plurality of control chutes 133 (three shown) corresponding to the pawl through holes 113 on the fulcrum mount 11 and the fulcrum pawls 201. The driving cylinder 451 and the driving input member 131, and the fulcrum pawl 201 (or the pawl through hole 113) and the control chute 133 are in phase. Corresponding configuration, its implementation is based on the principle of pairing. In the present invention, the control chute 133 is constructed in the form of a control cam, and its configuration design principle is to determine the opening of the fulcrum pawl 201 according to its pivot position with the fulcrum pawl 201 limited to slide therein. The state of (uplifting) or closing (retracting) determines whether the ring gear 34 is in a fulcrum state in which it is locked in its own reverse direction. As shown, the control chute 133 can further include a chute first end 1331 and a chute second end 1333.

The carrier control cam 15 is disposed on the other end surface of the pedestal fixing base 11 close to the planetary gear train 3, and is a circular plate body configuration. In conjunction with the position of the telescopic bump 17 of the carrier, a plurality of fulcrum guiding arms 151 are protruded from the outer edge of the carrier control cam 15, and the guiding arm 151 is outwardly directed from the circular plate body toward the fulcrum fixing seat. One side of the elbow is extended by a predetermined length from the first end 1331 of the chute to the second end 1333 of the chute, and the free end of the lug guiding arm 151 is defined as a mouth end 1511.

The telescopic protrusion 17 of the planet carrier is disposed in the convex accommodating hole of the carrier 32 and elastically protrudes toward the carrier control cam 15 , and the relative position thereof corresponds to the convex hole 115 on the fulcrum fixing seat 11 . .

In the clutch 1 of the foregoing embodiment, the ring gear control cam 13 and the carrier control cam 15 are in limited connection with the transmission member 45 of the clutch transmission group 4, and the fulcrum fixing seat 11 is fixed to the shaft core 10; in other words, The combination of the gear control cam 13 and the carrier control cam 15 is in a relatively angular relationship with the fulcrum mount 11, and the range of rotation is the same as the length of the control chute 133.

As shown, the direction from the first end 1331 of the chute to the second end 1333 of the chute is defined as the second direction (this direction can also be referred to as the reverse side). The direction from the second end 1333 of the chute to the first end 1331 of the chute is defined as the first direction (this direction may also be referred to as the forward direction).

Referring to FIG. 10, it is an exploded perspective view of the main components of the clutch transmission set 4 of the power transmission system of the present invention having a rear clutch device. The clutch transmission set 4 includes a transmission member 41 for external force input, a transmission pawl holder 43 driven by the transmission member 41, and a transmission member 45 provided with at least one one-way clutch on the periphery of the transmission pawl holder 43. 200. The one-way clutch 200 is engaged with a one-way ratchet of the inner ring surface of the right ratchet ring 51. When the power transmission system of the present invention is disposed on an electric bicycle, the transmission member 41 may be coupled to the pedal of the electric bicycle, whereby when the rider begins to step on the pedal An external force input to the transmission member 41 is provided to cause it to rotate forward. When the transmission member 41 drives the transmission pawl seat 43 to rotate forward and the power source 100 does not provide power (that is, the planetary gear train 3 has no power output), the one-way clutch 200 of the transmission pawl seat 43 will engage and drive the right ratchet ring. 51 is rotated forward together with the hub 5 which is fixedly fitted to the right ratchet ring 51. In other words, the external force input by the transmission member 41 will be directly used to drive the hub 5 to rotate. When the transmission member 41 drives the transmission pawl seat 43 to reverse, the one-way clutch 200 of the transmission pawl holder 43 will slip with the right ratchet ring 51 regardless of whether the power source 100 provides power. As for the power source 100 to provide power, and the transmission member 41 drives the transmission pawl seat 43 to rotate forward, the power output from the power source 100 through the planetary gear train 3 will assist in driving the hub 5 forward; When the driving speed of the flower drum shell 5 is greater than the forward rotation speed of the driving pawl seat 43, the one-way clutch 200 of the driving pawl seat 43 is slipped; if the planetary gear train 3 drives the flower drum shell 5 to rotate forward faster than the transmission When the pawl seat 43 rotates at a forward speed, the power outputted by the power source 100 can provide a torque, so that the force input from the transmission member 41 has a labor-saving effect.

The transmission member 45 is disposed in a central recess 431 of the transmission pawl seat 43 and drives the drive input member 131 on the ring gear control cam 13 through the drive cylinder 451 therethrough. A C-shaped torsion spring 47 is provided between the transmission pawl seat 43 and the transmission member 45 as a linkage buffer between the two. The C-shaped torsion spring 47 is sleeved in the annular groove provided on the outermost annular surface of the transmission member 45, and one of the protruding ends of the C-shaped torsion spring 47 is engaged with the torsion spring of one side of the central recess 431. The positioning point 433 is combined with the transmission pawl holder 43. The C-shaped torsion spring 47 can provide a function similar to the one-way clutch. When the transmission member 41 drives the transmission pawl seat 43 to rotate forward, since the C-shaped torsion spring 47 has a tendency to reduce the inner diameter, the transmission member 45 can be applied. Provide a tight grip and drive it to follow the forward rotation. In contrast, when the transmission member 41 drives the transmission pawl seat 43 to reverse, since the C-shaped torsion spring 47 will have a tendency to enlarge the inner diameter, the tightening force to the transmission member 45 will be reduced and the slippage may be caused. Piece 45 does not follow the tendency to reverse. However, whether it is forward or reverse, once the transmission member 45 cannot continue to rotate for some reason (for example, but the clutch transmission 4 and the planetary gear train 3 are not locked), the transmission member 41 drives the transmission ratchet. When the claw seat 43 rotates forward or reverse, it will slip with the transmission member 45 (that is, the C-shaped torsion spring 47 will slip in the annular groove of the transmission member 45).

Please refer to Figure 4, Figure 7, Figure 8, and Figure 9. In the present invention, when an external force is input to the clutch transmission group 4 to perform the rotation operation in the first direction (forward rotation direction) (that is, the actuation of the opening power path by the external force intervention), the component actuation is performed by the transmission member 41. Point to the first direction Rotating at a certain angle, interlocking the transmission pawl seat 43, buffering the transmission member 45 to input the forward rotation operation to the clutch 1; at the same time, the external force can also be stored in the return torsion spring 19. In the clutch 1, the ring gear control cam 13 also rotates in the first direction by the action of the transmission member 45. At this time, the fulcrum pawl 201 is relatively slid toward the chute by the first end 1331 of the chute. Two ends 1333. At this time, the fulcrum pawl 201 is located at the other end of the rib ring 111, that is, the ring gear ratchet portion 343 on the ring gear 34 forms an upwardly open unidirectional consolidation state, which causes the ring gear 34 of the planetary gear train 3 to reverse itself. The direction will be locked by the fulcrum pawl 201 to form a force fulcrum for the operation of the planetary gear train, thereby opening the action output of the planet carrier 32 during forward rotation, that is, opening the planet carrier 32 in its forward direction. Power output path on. At the same time, the bump guiding arm 151 of the interlocking planet carrier control cam 15 is rotated by the forward rotation by the corresponding convex point hole 115 of the protruding point, and under the leading edge of the planetary telescopic bump 17 (the first 9 bottom side of the figure) exit. The planet telescopic projection 17 is again projected into the bump hole 115 of the fulcrum mount 11 by the pushing action of the bump guiding arm 151 and the elastic restoring force inside the planetary telescopic bump 17. That is, the planet carrier 32 and the fulcrum mount 11 are unidirectionally consolidated in the reverse direction of the carrier 32 itself, causing the planet carrier 32 of the planetary gear train 3 to be anchored by the planetary telescopic bump 17 in its own reverse direction. Fixed by the locking action of the bump card hole 115 to form a force fulcrum for the operation of the planetary gear train, thereby opening the actuating output of the ring gear 34 during forward rotation, that is, opening the ring gear 34 in its forward direction. Power output path. Briefly, when an external force is involved to cause the transmission member 45 of the clutch transmission set 4 to rotate forward, both the ring gear 34 and the carrier 32 will be subjected to the reverse direction of their own. The clutch 1 is unidirectionally consolidated to provide a force fulcrum and can output power both in the forward direction of the ring gear 34 and the carrier 32.

At this time, the direction of rotation of the sun gear 31 driven by the power source 100 determines whether the power will be output by the ring gear 34 or the carrier 32. When the sun gear 31 inputs a positive rotational force, the planetary carrier 32 will have a tendency to rotate forward, and at the same time, the ring gear 34 has a tendency to reverse; therefore, the ring gear 34 will be abutted by the fulcrum pawl 201 of the clutch 1. The lock becomes a fulcrum, and the power is output from the forward-rotating planet carrier 32 to the hub 5 for forward rotation. At this time, the planetary telescopic bump 17 and the bump hole 115 will be in a slip state. In contrast, when the sun gear 31 inputs a reverse rotation force, the planetary carrier 32 will have a tendency to reverse, and the ring gear 34 has a tendency to rotate forward; therefore, the carrier 32 will be anchored by the planetary expansion and convexity 17 The fulcrum of the planetary gear train is formed by the locking action of the bump hole 115, and the power is output from the forward ring gear 34 to the hub 5 for forward rotation. At this time, the ring gear 34 and the fulcrum pawl 201 will be in a slipping state.

On the other hand, when no external force is input to the clutch transmission group 4 (that is, the operation of the closing power path without external force intervention), the position in the return torsion spring 19 can be released, and the clutch transmission group 4 is directed to the second direction (reverse rotation). ) The return on the rotation. At this time, the component is actuated by: the transmission member 41 performs a return rotation at a certain angle in the second direction, interlocks the transmission pawl holder 43, and buffers the transmission member 45, and further controls the ring gear control cam 13 to point in the second direction. Reverse rotation.

In the clutch 1, the ring gear is actuated by the reversal of the transmission member 45. The wheel control cam 13 also performs a reverse rotation in the second direction. At this time, the fulcrum pawl 201 is relatively slid toward the first end 1331 of the chute by the second end 1333 of the chute. At this time, the fulcrum pawl 201 is located at the other end of the rib ring 111, that is, the ring gear ratchet portion 343 on the ring gear 34 is in a downwardly closed slip state, and the ring gear 34 of the planetary gear train 3 is urged in its own right. Both the turning and reversing directions will be in a slipping state with the fulcrum pawl 201 and cannot constitute a force fulcrum. At the same time, the bump guiding arm 151 of the interlocking planet carrier control cam 15 protrudes into the corresponding convex card hole 115 due to the reverse rotation, and under the leading edge of the planetary telescopic bump 17 (as shown by the dotted line in FIG. 9) By the push-pull action of the bump guiding arm 151, the planetary telescopic bump 17 is "shoveled out" from the anchoring hole 115 of the anchor, that is, the carrier 32 is separated from the fulcrum mount 11 to promote the planet. The carrier 32 of the gear train 3 will be in a slip-off state with the carrier control cam 15 in its forward or reverse direction, and cannot constitute a force fulcrum. Thereby, since the entire planetary gear train 3 does not have any component that can become a force fulcrum; even if the power source 100 still provides power input at this time, regardless of whether the power input by the sun gear 31 is forward or reverse, The entire planetary gear train 3 is idling, and the ring gear 34 or the carrier 32 cannot be driven to output power to the hub 5 .

In other words, in the present invention, when there is no external force to actuate the transmission member 41 of the clutch transmission set 4, the clutch 1 is in the position of "closing the power path", at this time, the ring gear 34 of the planetary gear train 3 and the planet The frame 32 is in a freely rotating state in which it is not consolidated with the shaft center 10, so that the planetary gear train 3 cannot transmit any power that can be output to the hub 5 .

In the foregoing embodiments of the present invention, it includes two interlocking but discrete convex One of the wheel and follower pairs is used to control the fulcrum operation of the ring gear 34 (ring gear control cam mechanism), and the other is to control the fulcrum operation of the carrier 32 (the carrier control cam mechanism). In the ring gear control cam mechanism, the cam profile is the configuration of the control chute 133, and the follower is the fulcrum pawl 201; and in the carrier control cam mechanism, the cam profile is the bump guide arm 151 In configuration, the follower is a planet carrier telescopic bump 17. In the prior art, a wide variety of such combined cams are available, such techniques being familiar to those skilled in the art, in accordance with the foregoing disclosure of the present invention, and easily implemented; for example, in another embodiment not shown The ring gear control cam 13 and the carrier control cam 15 can be combined into a plate body, and disposed on the same side of the rib ring 111, and then combined with the space and the action interference elimination processing of other parts, the foregoing embodiment can be achieved. The functions of the present invention, which are equivalent to such equivalents, are familiar to those skilled in the art and are not beyond the scope of the present disclosure and are not described herein.

In the following embodiments, since the components and functions of the components are the same as those of the foregoing embodiments, the same or similar components will be given the same component names and numbers, and the details thereof will not be described again.

Please refer to FIG. 11 , which is a structural diagram of a second preferred embodiment of a power transmission system with a rear clutch device according to the present invention. The power transmission system of this embodiment is generally similar to the previous embodiment and is also constructed in a hub 5 for driving the hub 5 to rotate. Also, and likewise provided in accordance with a fixed axis 10, it also includes a power source 100, a transmission 2, a clutch 1, and a clutch transmission set 4. The transmission 2 includes a plurality of rotatable transmission portions, and the transmission portions further include a terminal planetary gear train 7 coupled to the hub 5 as a power by the one-way clutch 200. The output. Similarly, at least a portion of the clutch 1 is affixed to the shaft 10 and functions as a "switch" for power output without transmitting power. When no external force is applied to the clutch 1 from the clutch transmission group 4, the clutch 1 is in the position of "closing the power path"; at this time, the clutch 1 is formed with all of the transmission portions in the transmission 2 In the released state of the consolidation, all of the transmission portions of the transmission 2 are free of any force fulcrum, thereby making the power unable to be transmitted through the terminal planetary gear train 7 of the transmission 2. That is, when the clutch 1 is in the position of "closing the power path", the terminal planetary gear train 7 can only idle at most and cannot generate any power that can be output to the hub 5 . When the external force drives the clutch 1 to actuate to "turn on the power path" through the clutch transmission group 4, the terminal carrier 72 of the terminal planetary gear train 7 and the shaft center 10 are consolidated in one direction (forward rotation direction), and the other is One-way locked state in which the direction (reverse direction) slips off. That is, when the clutch 1 enters the "open power path" state, the clutch 1 is formed with at least one of the transmission portions of the transmission 2 (that is, the terminal carrier 72 of the terminal planetary gear train 7). The knot is such that the fixed transmission portion (terminal carrier 72) becomes the fulcrum of the transmission 2, and the power thereof is transmitted through the other unconsolidated transmission portion of the transmission 2 (that is, disposed on the terminal planet) The one-way clutch 200) between the terminal ring gear 74 of the gear train 7 and the hub 5 is driven to output.

The difference between the second preferred embodiment of the present invention shown in Fig. 11 and the foregoing embodiment will be described below.

In the embodiment shown in Fig. 11, the power source 100 is a motor in which the outer casing is fixed and the inner rotor 104 is rotatable in the forward and reverse directions. The move The inner rotor 104 of the force source 100 (motor) is sleeved on the shaft 10 in a relatively rotatable manner and is rotatable in a forward or reverse direction with respect to the fixed axis 10 . The transmission 2 includes two sets of planetary gear trains (one of which is the aforementioned terminal planetary gear train 7). The set of planetary gears adjacent to the power source 100 may be referred to as a front planetary gear train, and includes a front end sun gear 61, a front end planet carrier 62, a plurality of (usually three) front end planetary gears 63, and a front end ring. Gear 64. A one-way clutch 105 is provided between the front end sun gear 61 and the inner rotor 104 for one-way engagement (the inner rotor 104 is engaged during forward rotation and slipped during reverse rotation). The front end carrier 62 is an element that is fixed to the outer casing of the power source 100 and is stationary. The front end ring gear 64 is coupled to the terminal sun gear 71 of the terminal planetary gear train 7 and rotates in conjunction therewith.

The terminal planetary gear train 7 is adjacent to and controlled by the clutch 1 to determine whether or not the rotational power can be output to the hub 5 . The terminal planetary gear train 7 also includes a terminal sun gear 71, a terminal planet carrier 72, a number of (usually three) terminal planet gears 73, and a terminal ring gear 74. In addition to being rotatable by the front end ring gear 64, the terminal sun gear 71 is also provided with a one-way clutch between the inner rotor 104 and the inner rotor 104 (the inner rotor 104 is engaged when reversing, and slipped during forward rotation). 106. The terminal carrier 72 is coupled to the clutch 1, and whether the external carrier can drive the clutch 1 through the clutch transmission group 4 to determine whether the terminal carrier 72 is consolidated by the clutch 1 and becomes the force of the transmission 2. Pivot. A one-way clutch 200 is provided between the terminal ring gear 74 and the hub 5 for the one-way engagement (the terminal ring gear 74 is engaged during forward rotation and slipped during reverse rotation). With the foregoing structure, the second preferred embodiment can be the same The shifting of two different speed ratios is provided by the forward and reverse rotation of the rotor 104 in the power source 100, and whether the terminal planetary gear train 7 can be determined by whether an external force is applied to the clutch 1 by the clutch transmission group 4 The power is output to the function of the hub 5 .

As for the clutch 1 of the second preferred embodiment, the specific structure and operation mode are substantially similar to the embodiment shown in FIG. 8, which is different in the clutch 1 of the second preferred embodiment. It is only necessary to consolidate the terminal carrier 72, and only one set of one-way clutches (the occlusion in the forward rotation and the slip-off in the reverse rotation) between the clutch 1 and the shaft center 10 is required.

Please refer to FIG. 12A and FIG. 12B , which are respectively schematic structural diagrams of the third preferred embodiment of the power transmission system with the rear clutch device of the present invention (closed power path state and open power path state). Most of the components of the third preferred embodiment are the same as the second preferred embodiment shown in FIG. 11, and therefore will not be described again. The only difference is that the one-way clutch between the clutch 1 and the shaft 10 is changed to a keyway design. For example, between the clutch 1 and the shaft core 10, it is designed to be axially slidable relative to each other in a meshing position and a The slide key 202 is separated from the position. When no external force is applied to the clutch 1 from the clutch transmission group 4, the slide button 202 is held in the disengaged position (that is, the "closed power path" state as shown in Fig. 12A), resulting in the terminal planetary gear train 7 At most, it can only be idling and cannot generate any power that can be output to the hub 5 . When an external force is applied to the clutch 1 by the clutch transmission group 4, the sliding button 202 is switched to the engaged position (that is, the "opening power path" state as shown in FIG. 12B), and the clutch 1 is terminated with the terminal. The terminal carrier 72 of the planetary gear train 7 is consolidated to become a force fulcrum, thereby making the power available. It is output through the transmission of the one-way clutch 200 between the terminal ring gear 74 and the hub 5 .

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‧‧‧Clutch

2‧‧‧Transmission

3‧‧‧ planetary gear train

4‧‧‧Clutch Transmission Group

5‧‧‧Flower shell

7‧‧‧Terminal planetary gear train

10‧‧‧Axis

11‧‧‧ fulcrum mount

13‧‧‧Ring gear control cam

15‧‧‧Carriage control cam

17‧‧‧ Planetary telescopic bumps

19‧‧‧Restoring torsion spring

31‧‧‧Sun Gear

32‧‧‧ planet carrier

33‧‧‧ planetary gear

34‧‧‧ring gear

41‧‧‧ Transmission parts

43‧‧‧Drive pawl seat

45‧‧‧ Transmission parts

47‧‧‧C-shaped torsion spring

51‧‧‧Right ratchet ring

53‧‧‧Flower shell ratchet ring

55‧‧‧Left bead bowl

57‧‧‧The left side cover of the flower drum shell

61‧‧‧ front end sun gear

62‧‧‧ front-end planet carrier

63‧‧‧ front planetary gear

64‧‧‧ front ring gear

71‧‧‧ Terminal Sun Gear

72‧‧‧End planet carrier

73‧‧‧Terminal planetary gears

74‧‧‧Terminal ring gear

100‧‧‧Power source

101‧‧‧Motor stator bracket

103‧‧‧Motor rotor

104‧‧‧ Inner rotor

105‧‧‧Clutch

111‧‧‧ Rib ring

113‧‧‧Pawl through hole

115‧‧‧Bump card hole

131‧‧‧Drive input

133‧‧‧Control chute

151‧‧‧Bump guide arm

200‧‧‧ one-way clutch

201‧‧‧ fulcrum pawl

202‧‧‧Sliding key

341‧‧‧Ring gear tooth profile

343‧‧‧Ring gear ratchet

431‧‧‧ center pocket

433‧‧‧torsion spring positioning point

451‧‧‧ drive cylinder

1331‧‧ ‧ first end of chute

1333‧‧‧The second end of the chute

1511‧‧‧ Sealing end

1 is a schematic diagram of a system configuration of a conventional power transmission system; FIG. 2 is a system configuration diagram of another power transmission system having a rear clutch device; and FIG. 3 is a power transmission system having a rear clutch device according to the present invention; FIG. 4 is a schematic structural view of a preferred embodiment of a power transmission system having a rear clutch device according to the present invention; and FIG. 5 is a detailed implementation of the components of the embodiment shown in FIG. Explosion diagram; Figure 6 is a schematic cross-sectional view of the combination of Figure 5; Figure 7 is a three-dimensional enlarged schematic view of the carrier, ring gear and hub shell ratchet ring; Figure 8 is the power of the invention with the rear clutch device An exploded perspective view of the main components of the clutch of the transmission system; FIG. 9 is a schematic view of the operation of the control cam of the carrier of the present invention; And Fig. 10 is an exploded perspective view of the clutch transmission set of the power transmission system of the rear clutch device of the present invention.

Figure 11 is a schematic view showing the configuration of a second preferred embodiment of the power transmission system having the rear clutch device of the present invention.

Fig. 12A is a schematic view showing the configuration of a third preferred embodiment of the power transmission system of the rear clutch device of the present invention (closed power path state).

Figure 12B is a schematic view showing the configuration of a third preferred embodiment of the power transmission system of the rear clutch device of the present invention (opening power path state).

1‧‧‧Clutch

2‧‧‧Transmission

3‧‧‧ planetary gear train

4‧‧‧Clutch Transmission Group

5‧‧‧Flower shell

10‧‧‧Axis

31‧‧‧Sun Gear

32‧‧‧ planet carrier

33‧‧‧ planetary gear

34‧‧‧ring gear

41‧‧‧ Transmission parts

100‧‧‧Power source

200‧‧‧ one-way clutch

Claims (20)

A power transmission system having a rear clutch device is provided according to a fixed axis, comprising: a power source; and a transmission connected to the power source for performing speed conversion on the power outputted by the power source, A planetary gear train is further included as a power output; the planetary gear train further includes a sun gear pivoted on the shaft and driven by the power source, a planet carrier, a ring gear, and a hub a plurality of planetary gears that are coupled to rotate between the sun gear and the ring gear; and a clutch that is actuated by an external force to determine an output mode of the planetary gear train, and the selection of the free "power path" a state, and an "open power path" state in which the external force is involved; when the external force is intervened to cause the clutch to enter the "open power path" state, the clutch is the ring gear of the planetary gear train and the planet At least one of the two forms a consolidation with the axis in its own reversal direction, such that the ring gear and the planet carrier One of the fewer may become a force fulcrum of the planetary gear train in operation in its reverse direction such that the power input by the sun gear transmits the planet carrier and the ring gear through the planetary gear. Outputting for the forwarder; and when the external force is removed, the clutch is elastically restored to the "closed power path" state, at which time the clutch releases the carrier of the planetary gear train and the ring gear to enable Both the planet carrier and the ring gear cannot be the fulcrum of the force of the planetary gear train. At this time, the sun gear The input power cannot be transmitted through the planetary gear train. The power transmission system with a rear clutch device according to claim 1, further comprising a hub, the power source, the transmission and the clutch are disposed in the hub, wherein the ring gear and the carrier And forming a single one-way clutch combination with one of the hub shells of the hub of the flower drum. A power transmission system having a rear clutch device according to claim 1, wherein the clutch further includes a ring gear control cam mechanism for controlling a fulcrum operation of the ring gear, and a control unit The planet carrier control cam mechanism of the fulcrum operation of the planet carrier. The power transmission system with a rear clutch device according to claim 3, wherein the clutch further comprises a ring gear control cam mechanism and the carrier control cam mechanism are two interlocking but separate cam and follower pairs. In the ring gear control cam mechanism, the cam profile is controlled by one of the external forces to control the chute, and the follower is a fixed fulcrum pawl; and in the carrier control cam mechanism, The mating cam profile is a bump guiding arm that is actuated by the external force, and the follower is one of the planet carrier telescopic bumps disposed on the planet carrier. The power transmission system with a rear clutch device according to claim 3, wherein the ring gear control cam mechanism and the carrier control cam mechanism are mainly two cam and follower pairs built in the same plate body. In the ring gear control cam mechanism, the cam profile is controlled by one of the external forces to control the chute, and the follower is a fixed fulcrum pawl; and in the carrier control cam mechanism, The cam profile is configured to act as a bump guiding arm with the external force, and the follower It is a telescopic bump of one of the planets provided on the planet carrier. A power transmission system having a rear clutch device according to claim 3, wherein the clutch further includes a fulcrum mount fixedly coupled to the shaft center, the ring gear control cam mechanism further comprising a fulcrum disposed at the fulcrum a ring gear control cam on one side of the fixing seat, a plurality of pawl through holes provided in an inner edge of the rib ring of the fulcrum fixing seat, and an individual pivoting in the pawl through hole and being exposed on both sides of the rib ring a fulcrum pawl, the ring gear control cam further comprising a plurality of control chutes corresponding to the pawl through holes on the fulcrum mount and the fulcrum pawls; when the clutch enters the "open power path" state When the fulcrum is actuated, the ring gear control cam is driven to rotate in a forward direction to slide the fulcrum pawl from the first end of the control chute to the second end of the other side of the control chute, The fulcrum pawl forms a unidirectional consolidation with the ring gear, causing the ring gear of the planetary gear train to become a fulcrum of the planetary gear train operation in its own reverse direction; and when the clutch enters the "power off" When the path state is actuated, the ring gear control cam is driven to perform a reverse rotation to slide the fulcrum pawl from the second end toward the first end, so that the fulcrum pawl and the ring gear form an actuation separation Therefore, the ring gear of the planetary gear train cannot be used as a fulcrum of the planetary gear train operation in its forward or reverse direction. A power transmission system having a rear clutch device according to claim 3, wherein the clutch further includes a fulcrum mount fixedly coupled to the shaft center, the carrier control cam mechanism further comprising a fulcrum disposed at the fulcrum a planet carrier control cam fixed to the planet carrier, a plurality of planets disposed on the planet carrier and elastically projecting cams to the planet carrier a telescopic bump and a plurality of bump holes disposed on the fulcrum mount corresponding to the telescopic bumps of the planet carrier, and the position of the telescopic bump of the carrier is matched with the outer edge of the carrier control cam Providing a plurality of fulcrum guiding arms extending outwardly and toward a side of the fulcrum fixing seat for a predetermined length; when the clutch is engaged in the fulcrum of the "opening power path" state, driving the The forward guiding arm of the carrier control cam is rotated downward from the leading edge of the protruding slot of the planet, and the removal of the protruding guiding arm is to expand and contract the planet The bump re-converges into the bump hole of the fulcrum mount, and the unidirectional consolidation of the planet carrier and the fulcrum mount in the reverse direction of the carrier itself, so that the planet carrier is on its own The reverse direction becomes the fulcrum of the operation of the planetary gear train; and when the clutch enters the "closed power path" state, the bump guiding arm of the carrier control cam is reversely coupled to the corresponding corresponding The bump card Under the front edge of the telescopic bump of the planet, by the push-pull action of the bump guiding arm, the planetary telescopic bump is self-anchored in the bump hole to "shovel out" to make the planet carrier and The fulcrum mount is disengaged, thereby releasing the planet carrier from the clutch, thereby causing the planet carrier of the planetary gear train to be unable to function as a fulcrum for operation of the planetary gear train, either in its forward or reverse direction. The power transmission system with a rear clutch device according to claim 1, wherein the external force is transmitted to the clutch by a clutch transmission group, and the clutch transmission group further includes a first input for the external force. a transmission member, a transmission pawl seat driven by the first transmission member, and a second transmission member for transmitting power directly to the clutch, the transmission A C-shaped torsion spring is disposed between the pawl seat and the second transmission member as a linkage buffer between the two. A power transmission system having a rear clutch device according to claim 1, wherein the power source is a motor in which the outer casing is fixed and the inner rotor is rotatable in the forward and reverse directions; the inner rotor of the power source Rotating in a relatively rotatable manner on the shaft and rotating in a forward or reverse direction with respect to the fixed axis; the transmission includes a front planetary gear train and the terminal planetary gear train The front planetary gear train includes a front end sun gear, a front end planet carrier, a plurality of front end planetary gears, and a front end ring gear; a one-way clutch having a one-way engagement between the front end sun gear and the inner rotor; The front end carrier is a stationary component: the front end ring gear is coupled to and rotates with a terminal sun gear of the terminal planetary gear train; the terminal planetary gear system is adjacent to the clutch and controlled by the same to determine whether a rotary power output; the terminal planetary gear train includes the terminal sun gear, a terminal planet carrier, and a plurality of terminal planetary gears And a terminal ring gear; the terminal sun gear is driven by the front end ring gear, and is also provided with a one-way clutch between the inner rotor and the inner rotor; the terminal planet carrier is coupled to The clutch can determine whether the terminal carrier is fixed by the clutch by the external force to drive the clutch to act as a force fulcrum of the transmission. The power transmission system with a rear clutch device according to claim 1, wherein one of the following is further disposed between the clutch and the shaft: at least one one-way clutch, and a keyway design a sliding button; wherein the sliding button is slidable relative to each other in an axial direction between a snapping position and a disengaged position; when no external force is applied to the clutch to actuate, the sliding button is held in a disengaged position, that is, the "closed" The power path state; when an external force is applied to the clutch, the sliding button is switched to a meshing position, that is, the "open power path" state. A power transmission system with a rear clutch device is provided according to a fixed axis, comprising: a power source; a transmission connected to the power source for receiving power and outputting the power output to the power source And then outputting; and comprising at least a plurality of transmission portions in the transmission; and a clutch is actuated by an external force to determine an output mode of the transmission, wherein the valve has a "closed power path" state, and a "opening the power path" state; at least a portion of the clutch is consolidated with the shaft; wherein, when the clutch enters the "open power path" state, the clutch is formed with at least one of the transmission portions of the transmission Consolidating, the fixed transmission portion becomes a force fulcrum of the transmission, and the power is output through the transmission of the other unconsolidated transmission portion of the transmission; wherein, when the clutch enters the When the power path is turned off, The clutch is in an unconsolidated release state with all of the transmissions in the transmission such that all of the transmissions in the transmission are free of any force fulcrum, thereby rendering the power untransmittable through the transmission. A power transmission system having a rear clutch device according to claim 11, wherein: the plurality of transmission portions of the transmission further include a terminal planetary gear train as an output of power; the planetary gear train further includes a pivot a sun gear disposed on the shaft and driven by the power source, a planet carrier, a ring gear, and a plurality of planet gears pivoted on the planet carrier and meshed between the sun gear and the ring gear; When the external force intervenes in the clutch, the clutch enters the "open power path" state, and at this time, the clutch is at least one of the ring gear of the planetary gear train and the carrier is itself Forming a consolidation with the axis in a reversal direction such that at least one of the ring gear and the planet carrier can become a force fulcrum of the planetary gear train in operation in a reverse direction of its own direction to enable The power input by the sun gear is driven by the planetary gear to drive a forward rotation of the carrier and the ring gear; and when the external force is removed, the clutch That is, the elastic return to the "closed power path" state, at which time the clutch releases the carrier of the planetary gear train and the ring gear so that neither the carrier nor the ring gear can become the planetary gear train. The force fulcrum during operation, at this time, the power input by the sun gear cannot be output through the planetary gear train. The power transmission system with a rear clutch device according to claim 12, further comprising a hub, the power source, the transmission and the clutch are disposed in the hub, wherein the ring gear and the carrier And forming a single one-way clutch combination with one of the hub shells of the hub of the flower drum. A power transmission system having a rear clutch device according to claim 12, wherein the clutch further includes a ring gear control cam mechanism for controlling a fulcrum operation of the ring gear, and a control The planet carrier control cam mechanism of the fulcrum operation of the planet carrier. The power transmission system with a rear clutch device according to claim 14, wherein the clutch further comprises a ring gear control cam mechanism and the carrier control cam mechanism are two interlocking but discrete cam and follower pairs. In the ring gear control cam mechanism, the cam profile is controlled by one of the external forces to control the chute, and the follower is a fixed fulcrum pawl; and in the carrier control cam mechanism, The mating cam profile is a bump guiding arm that is actuated by the external force, and the follower is one of the planet carrier telescopic bumps disposed on the planet carrier. The power transmission system with a rear clutch device according to claim 14, wherein the clutch further includes a fulcrum fixed seat fixedly coupled to the shaft center, the ring gear control cam mechanism further comprising a fulcrum disposed at the fulcrum a ring gear control cam on one side of the fixing seat, a plurality of pawl through holes provided in an inner edge of the rib ring of the fulcrum fixing seat, and an individual pivoting in the pawl through hole and being exposed on both sides of the rib ring a fulcrum pawl, the ring gear control cam further comprising a plurality of control chutes corresponding to the pawl through holes on the fulcrum mount and the fulcrum pawls; when the clutch is engaged When the fulcrum of the "open power path" state is activated, the ring gear control cam is driven to rotate forward to slide the fulcrum pawl from the first end of the control chute to the other side of the control chute One of the second ends causes the fulcrum pawl to form a unidirectional consolidation with the ring gear, causing the ring gear of the planetary gear train to become the fulcrum of the planetary gear train operation in its own reverse direction; When the clutch enters the "close power path" state, the ring gear control cam is driven to perform a reverse rotation to slide the fulcrum pawl from the second end toward the first end to make the fulcrum pawl The driving gear is separated from the ring gear, so that the ring gear of the planetary gear train cannot be used as a fulcrum of the planetary gear train operation in its forward or reverse direction. A power transmission system having a rear clutch device according to claim 14, wherein the clutch further includes a fulcrum mount fixedly coupled to the shaft center, the carrier control cam mechanism further comprising a fulcrum disposed at the fulcrum a planet carrier control cam of the carrier near the planet carrier, a plurality of planet carrier telescopic bumps disposed on the planet carrier and elastically protruding to the planet carrier control cam, and a plurality of corresponding planets disposed on the fulcrum mount a bumping hole of the telescopic bump, and a position of the telescopic bump of the carrier, and a peripheral edge of the carrier control cam is further protruded and provided with a plurality of fulcrum guiding arms, the guiding arm is outwardly and outwardly One side of the fulcrum mount is extended by a predetermined length; when the clutch is moved to the fulcrum of the "open power path" state, the bump guiding arm of the carrier control cam is driven to rotate forward by the bump card hole The front edge of the planetary telescopic bump exits, and the removal of the bump guiding arm re-projects the planetary telescopic bump into the bump hole of the fulcrum mount And unidirectionally consolidating the planet carrier and the fulcrum mount in the reverse direction of the planet carrier itself, so that the planet carrier becomes the fulcrum of the planetary gear train operation in its reverse direction; and when the clutch When the operation of the "closed power path" state is performed, the bump guiding arm of the carrier control cam is reversely extended into the corresponding convex hole of the bump, and the front edge of the planetary telescopic bump is borrowed. The planet telescopic bump is "shoveled out" from the anchor hole of the anchor by the pushing and pulling action of the bump guiding arm, so that the planet carrier is separated from the fulcrum fixing seat, thereby the planet carrier Released by the clutch, thereby causing the planet carrier of the planetary gear train to be unable to function as a fulcrum for operation of the planetary gear train, either in its forward or reverse direction. The power transmission system with a rear clutch device according to claim 12, wherein the external force is transmitted to the clutch by a clutch transmission group, and the clutch transmission group further includes a first input for the external force. a transmission member, a transmission pawl seat driven by the first transmission member, and a second transmission member for directly transmitting power to the clutch, wherein the transmission pawl seat and the second transmission member are further disposed as a second A C-shaped torsion spring that is buffered between the two. The power transmission system with a rear clutch device according to claim 11, wherein the power source is a motor in which the outer casing is fixed and the inner rotor is rotatable in the forward and reverse directions; the inner rotor of the power source Rotating in a relatively rotatable manner on the axis and rotating in a forward or reverse direction with respect to the fixed axis; the transmission includes a front planetary gear train and a terminal planet a gear train; the front planetary gear train includes a front end sun gear, a front end planet carrier, a plurality of front end planetary gears, and a front end ring gear; a one-way clutch having a one-way engagement between the front end sun gear and the inner rotor The front end planet carrier is a stationary component: the front end ring gear is coupled to and rotates with a terminal sun gear of one of the terminal planetary gear trains; the terminal planetary gear train is adjacent to the clutch and is controlled by the same Whether the rotary power can be output; the terminal planetary gear train includes the terminal sun gear, a terminal planet carrier, a plurality of terminal planetary gears, and a terminal ring gear; the terminal sun gear can be driven by the front ring gear to rotate And another one-way clutch provided with a one-way engagement between the inner rotor; the terminal carrier is coupled to the clutch, and whether the external carrier can drive the clutch to determine whether the terminal carrier will It is consolidated by the clutch to become the fulcrum of the transmission. The power transmission system with a rear clutch device according to claim 11, wherein one of the following is disposed between the clutch and the shaft: at least one one-way clutch, and a keyway design a sliding button; wherein the sliding button is slidable relative to each other in an axial direction between a snapping position and a disengaged position; when no external force is applied to the clutch to actuate, the sliding button is held in a disengaged position, that is, the "closed" The power path state; when an external force is applied to the clutch, the sliding button is switched to a meshing position, that is, the "open power path" state.