CN102865340B - Power transmission system with rear clutch device - Google Patents

Abstract

The invention discloses a power transmission system with a rear clutch device, which comprises a power source, a speed changer, a clutch and a clutch transmission set controlled by external force. The transmission is used for directly converting the rotating speed of the power output by the power source and can also comprise a terminal planetary gear train. The clutch is used for determining whether the output of the planetary gear train is available or not. When no external force is introduced, the planetary gear train is in an idle running state without outputting power because of no fulcrum; when external force is input, the clutch and the planetary gear train form a proper fulcrum state, so that the power output by the power source can be output through the planetary gear train of the transmission.

Description

Power transmission system with rear clutch device

technical field

The invention relates to a power transmission system with a clutch device, in particular to a power transmission or supply system that utilizes a rear clutch device to judge whether an external force intervenes or not to control a power output mode.

Background technique

Generally, the device configuration of the power supply system, power output system and power transmission system with a transmission (or gearbox) and a clutch is usually shown in Figure 1; wherein, the power (output by the original power source or other power conversion devices) is obtained by One end of the clutch 1 is input, and the clutch 1 controls whether the power is output or transmitted to the subsequent transmission 2. The power is directly output from the end of the transmission 2 after the speed and torque are converted by the transmission 2.

In the prior art, the power transfer operation of the clutch 1 is usually the input and output of a single speed, and is not used as a speed change function. The transmission 2, after receiving the power input controlled by the clutch 1, selects the appropriate shift gear (manual or automatic), and then transmits the power (speed, direction and torque) that suits the needs to the subsequent power application system. with the device (not shown). Basically, the operation of the clutch 1 does not intervene in the function of changing the nature of the output power.

As mentioned above, the power transmission system is a system in which the clutch 1 is set before the transmission 2; and in the prior art, there is also a system as shown in Figure 2. In this system, the clutch 1 is set at the transmission 2 After 2, that is, after the power input is directly shifted by the transmission 2, 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 Figure 2, but its power output path does not go through the clutch 1 at all, and its application range is preferably used in light-load power systems ( Such as electric bicycles, lawn mowers, and even robotic bicycles, etc.), especially the power transmission system hidden in the hub shell.

Contents of the invention

The main purpose of the present invention is to provide a power transmission system with a rear clutch device, which is integrated in the hub and can be controlled by external force input to achieve power output (open or stop power transmission) clutch power transmission.

Another object of the present invention is to provide a power transmission system with a rear clutch device, the clutch only provides the fulcrum of the power transmission system, so the power transmission path of the power transmission system does not pass through the clutch. The load on the clutch can be reduced to meet the needs of the light-loaded power system.

In the present invention, the power transmission system with the rear clutch device is arranged according to a fixed axis, including a power source, a speed changer, a clutch, and a clutch transmission group controlled by an external force.

The transmission is connected with the power source for direct speed conversion of the power output by the power source, and may include a terminal planetary gear train as the power output terminal. This planetary gear system can also include a sun gear pivoted on the shaft center and driven by a power source, a planet carrier, a ring gear, and multiple gears pivoted on the planet carrier and engaged to rotate between the sun gear and the ring gear. planetary gears.

The clutch is controlled by 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 does not provide Any force fulcrum of the planetary gear system causes the planetary gear (driven by the sun gear) of the planetary gear system to be in an idling state; and when an external force actuates the clutch through the clutch transmission group, the clutch is in a state of structural engagement with the planetary gear system , so that the planetary gear train has an appropriate force fulcrum, and then opens the output path of the power source, and the planetary gear train can output power to the hub shell through one of the planet carrier or the ring gear.

When there is no external force, the clutch does not form a fulcrum relationship with the planetary 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, resulting in no power output to the hub shell. When the external force intervenes, the clutch will form a proper fulcrum relationship with the planetary carrier and the ring gear. Therefore, the power transmitted from the power source to the sun gear will be determined to be driven by the planetary gear according to the direction of the sun gear. Either the ring gear or the output via the planet carrier.

In an embodiment of the present invention, the power transmission system with the rear clutch device can further include a hub shell, and most of the power source, speed changer, clutch and clutch transmission group are arranged in the hub shell, while the ring gear and the planet carrier and a hub shell ratchet ring in the hub shell to form individual one-way clutches respectively.

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

In an embodiment of the present invention, in the clutch of the power transmission system with the rear clutch device, the ring gear control cam mechanism and the planetary carrier control cam mechanism are two interlocking but separate pairs of cams and followers. In the ring gear control cam mechanism, the cam profile is a control chute that acts with external force, and the follower is a fixed fulcrum pawl. And in the planetary carrier control cam mechanism, the matching cam profile system is a bump guide arm actuated with external force, and the follower is a planetary carrier telescopic bump arranged on the planetary carrier.

In an embodiment of the present invention, the ring gear control cam mechanism and the planetary carrier control cam mechanism of the power transmission system with 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 a control chute that moves with the external force, and the follower is a fixed fulcrum pawl; while in the planet carrier control cam mechanism, the matching cam profile is the follower A protruding point actuated by external force guides the arm, and the follower is a telescopic protruding point of the planetary carrier arranged on the planetary carrier.

In one embodiment of the present invention, the clutch of the power transmission system with the rear clutch device may further include a fulcrum fixed seat fixedly combined with the shaft center, and the ring gear control cam mechanism may further include a fulcrum fixed seat The ring gear control cam on one side, a plurality of ratchet through holes on the inner edge of the rib ring of the fulcrum fixing seat, and individual fulcrum ratchets pivotally arranged in the ratchet through holes and exposed on both sides of the rib ring, the ring The gear control cam can also include a plurality of control chute corresponding to the pawl through hole on the fulcrum fixing seat and the fulcrum pawl; At this time, the fulcrum pawl slides from a first end of the control chute to a second end on the other side, so as to promote the fulcrum pawl to lift up and form a one-way solidification with the ring gear. state, so that the ring gear will be supported by the fulcrum pawl in a single rotation (reverse) direction and become the fulcrum of the planetary gear train operation, so that the sun gear can transmit power through the planetary gear in a single rotation (forward rotation) direction rack output. And when the external force on the clutch is removed, the return torsion spring drives the ring gear control cam to return to the original one end position, so that the fulcrum pawl is closed downward and no longer engages with the ring gear. When the gear is driven, whether it is forward rotation or reverse rotation, it will be in an idling state and the power cannot be output from the planet carrier.

In an embodiment of the present invention, the clutch of the power transmission system with the rear clutch device may further include a fulcrum fixed seat fixedly combined with the shaft center, and the planet carrier control cam mechanism may further include a fulcrum fixed seat near the The planetary carrier control cam of the planetary carrier, a plurality of telescopic protrusions of the planetary carrier arranged on the planetary carrier and elastically protruding toward the planetary carrier control cam, and a plurality of protrusions arranged on the fulcrum fixing seat and corresponding to the telescopic protrusions of the planetary carrier Point clamping holes, matching the position of the telescopic bumps of the planet carrier, and the outer edge of the planet carrier control cam are protrudingly provided with multi-pivot guide arms. The configuration of the bump guide arms is outward and toward the side of the fulcrum holder. , and extend a predetermined length along one direction. When the clutch is not subjected to external force, the return torsion spring provides a restoring force to drive the lug guide arm of the planet carrier control cam to rotate to the front edge of the corresponding planetary telescopic lug, by the pushing action of the lug guide arm , shovel out the telescopic convex point of the planet from the hole of the anchored convex point, so that the planet carrier is separated from the fulcrum fixing seat, so that there is no force-bearing fulcrum on the planet carrier; at this time, the power input by the sun gear, that is Because the planetary carrier does not have a force fulcrum, it is idling and cannot output power from the ring gear. When the external force drives the clutch to rotate forward, the convex point guide arm of the planetary carrier control cam will rotate forward to a position away from the corresponding convex point clamping hole, so that the telescopic convex point of the planetary carrier is seated (engaged) on the corresponding In the bump hole, the fixed relationship between the clutch and the planet carrier is stabilized in one direction, so that the planet carrier will be engaged by the bump hole in a single rotation (reverse) direction and become the fulcrum of the planetary gear train operation ; At this time, the power input by the sun gear in a single (reverse) steering can be output through the planetary gear to drive the ring gear in forward rotation.

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

The beneficial effect of the present invention is that the present invention achieves the clutch type power transmission of power output or not (opening or interrupting power transmission) through external force input control; at the same time, the clutch only provides the force fulcrum of the power transmission system, so the power of the power transmission system The transmission path does not pass through the clutch, which can reduce the load on the clutch to meet the needs of the light-load power system.

Description of drawings

Fig. 1 is a schematic diagram of system configuration of a traditional power transmission system;

2 is a schematic diagram of another system configuration of a power transmission system with a rear clutch device;

3 is a schematic diagram of the system configuration of the power transmission system with the rear clutch device of the present invention;

Fig. 4 is a schematic structural configuration diagram of a preferred embodiment of the power transmission system with the rear clutch device of the present invention;

Fig. 5 is an exploded view of the detailed implementation of parts of the embodiment shown in Fig. 4;

Figure 6 is a schematic cross-sectional view of the combination of Figure 5;

Fig. 7 is a three-dimensional enlarged schematic diagram of the planet carrier, the ring gear and the ratchet ring of the hub shell;

Fig. 8 is a three-dimensional exploded view of the main components of the clutch of the power transmission system with the rear clutch device of the present invention;

Figure 9 is a schematic diagram of the operation of the planet carrier control cam of the present invention; and

Fig. 10 is a three-dimensional exploded view of the clutch transmission group of the power transmission system with the rear clutch device of the present invention.

Fig. 11 is a schematic diagram of the structural configuration of the second preferred embodiment of the power transmission system with the rear clutch device of the present invention.

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

Fig. 12B is a schematic diagram of the structural configuration of the third preferred embodiment of the power transmission system with the rear clutch device of the present invention (the power path is turned on).

Explanation of reference signs: 1-clutch; 2-transmission; 3-planetary gear train; 4-clutch transmission group; 5-hub shell; 7-terminal planetary gear train; Ring gear control cam; 15-planetary carrier control cam; 17-planetary carrier telescopic bump; 19-return torsion spring; 31-sun gear; 32-planetary carrier; 33-planetary gear; 34-ring gear; 41-transmission parts ;43-transmission pawl seat; 45-transmission parts; 47-C-shaped torsion spring; 51-right ratchet ring; 53-hub shell ratchet ring; 55-left bead bowl; 57-hub shell left cover; 61 -front-end sun gear; 62-front-end planetary carrier; 63-front-end planetary gear; 64-front-end ring gear; 71-terminal sun gear; 72-terminal planetary carrier; 73-terminal planetary gear; 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; chute; 151-bump guide arm; 200-one-way clutch; 201-fulcrum pawl; 202-sliding key; 341-ring gear tooth profile; 343-ring gear ratchet part; 431-central cavity; 433 - the positioning point of the torsion spring; 451 - the driving cylinder; 1331 - the first end of the chute; 1333 - the second end of the chute; 1511 - the sealing end.

detailed description

Please refer to Figure 3, which is a schematic diagram of the system configuration of the power transmission system with the rear clutch device of the present invention; compared with the system shown in Figure 2, the clutch 1 of the power transmission system of the present invention is located behind the transmission 2, also That is to say, the power input is also directly changed by the transmission 2, and then the clutch 1 determines whether to output. The difference is that the transmission 2 of the present invention is a transmission structure with the output of the final planetary gear train 3, so it can be produced in three different ways. Output on the position: the idling of state N does not output the state, the output when the sun gear rotates forward (state+), and the output when the sun gear reverses (state-), and the clutch 1 of the present invention is to determine or control "Whether the power of the power source will be output through the planetary gear train?" Obviously, the key point of the present invention is: because the planetary gear train 3 is set at the terminal of the transmission 2, the clutch 1 device, compared to the overall power transmission system, is It has the connotation of "determining the opening and closing of the power path by controlling whether the fulcrum of the planetary gear train 3 is provided or not".

Please refer to FIG. 4 , which is a schematic structural configuration diagram of a preferred embodiment of a power transmission system with a rear clutch device according to the present invention. This embodiment implements the power transmission system of the present invention in the hub of a rotatable wheel. Those skilled in the art should know that the application of the present invention can be implemented in other transmission systems in the same way after some changes. .

As shown in the figure, in this embodiment, the power transmission system of the present invention is constructed in a hub shell 5, used to drive the hub shell 5 to rotate, and is set according to a fixed axis 10, which may include a power Source 100 , a transmission 2 with a final planetary gear train 3 , a clutch 1 .

The power source 100 is used to provide the power to rotate the hub shell, which can be implemented by an electric motor or other similar power supply structures.

The transmission 2 is used to change the speed of the power output by the power source 100 (usually decelerate), and includes several rotatable transmission parts. In this embodiment, the transmission parts described in the transmission 2 further include a terminal planetary gear train 3 as a power output. The planetary gear train 3 includes a sun gear 31, a planetary carrier 32, a ring gear 34, And a plurality of planetary gears 33 pivoted on the planet carrier 32 and meshed and rotated between the sun gear 31 and the ring gear 34 . As shown in the figure, this planetary gear train 3 can output power to the hub shell 5 that is covered with rotation by the ring gear 34 (when the sun gear 31 is rotating in reverse) or the planet carrier 32 (when the sun gear 31 is rotating forward), and thus drives The hub shell 5 rotates forward.

Clutch 1, through a pedal, manual, electric or other ways to control the input of external force to actuate the internal parts, to determine whether the power of the planetary gear train 3 can be output to the hub shell 5 or can only idle, in other words, Clutch 1 is to act as a power output "switch" (Switch) role without the function of power transmission. In the present invention, in order to successfully perform its function of "closing the power path", the clutch 1 must simultaneously make the ring gear 34 of the planetary gear train 3 and the planetary carrier 32 all present the state of no force fulcrum, so that the sun gear 31 Regardless of the different power paths transmitted by the forward rotation and the reverse rotation, the ring gear 34 and the planetary carrier 32 can only cause the idling motion of the ring gear 34 and the planetary carrier 32 but cannot drive the hub shell 5 to rotate (that is, the rotation power cannot be output to the hub shell 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". 10 Consolidated free-rotating (ie idling) state. Therefore, no matter the sun gear 31 is driven by the power source 100 to rotate forward or reverse, the rotational power of the sun gear 31 can only make the ring gear 34 and the planetary carrier 32 idle, without any rotational power being transmitted to the hub shell 5 . That is to say, 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 shell 5 .

And when the external force acts through the clutch 1 to "open the power path", the ring gear 34 and the planet carrier 32 of the planetary gear train 3 are all in a one-way (reverse direction) solidification with the shaft center 10, and the other One-way locked state where the direction (forward rotation direction) is slipping. In this embodiment, when the external force acts through the clutch 1 to "open the power path", the ring gear 34 will be one-way locked by the clutch 1 in its own reverse direction, and will be locked in the forward direction. It slips away from the clutch 1 and can rotate forward; at the same time, the planet carrier 32 is also subject to the one-way locking of the clutch 1 in its own reverse direction, and can slip off from the clutch 1 in the forward direction to rotate forward.

Thus, 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 rotate reversely, but at this time the planet carrier 32 is not locked by the clutch 1 because it is rotating forward. Therefore, the clutch 1 can provide a fulcrum for the ring gear 34 , so that the positive rotation power of the sun gear 31 can be output to the outer rotating hub shell 5 through the positive rotation planetary carrier 32 . And 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 rotates in the forward direction, but at this time the planet carrier 32 will be locked by the clutch 1 and cannot rotate reversely. Therefore, the clutch 1 can provide a force fulcrum for the planetary carrier 32 , so that the reverse rotation power of the sun gear 31 can be output to the externally rotating hub shell 5 through the forward rotation ring gear 34 .

In the present invention, the one-way clutch connection type between the ring gear 34 and the planetary carrier 32 and the hub shell 5 can use a hub shell ratchet ring with a one-way pawl mechanism as an intermediary combination of the one-way clutch 200, the one-way clutch 200 is a skilled art for those who are familiar with this type of technology, so its implementation details will not be repeated here.

The technology of the present invention is not strictly limited to a speed change mechanism that must be completely composed of a planetary gear train for the implementation requirements of the speed changer 2, but only defines that it should be a planetary gear train in its terminal transmission stage, and the planetary gear of this terminal speed change The input to the train is the sun gear, and the output is either the planet carrier or the ring gear. In the following part embodiments of the present invention, a planetary gear train is adopted as a single structure of the transmission 2, and any transmission mechanism that may exist between the terminal planetary gear train and the power source 100 is omitted, thereby simplifying the understanding of the present invention by those skilled in the art understanding. Only, those who are familiar with this type of art also need to know: a terminal planetary gear train is not a necessary condition for the implementation of the speed changer 2 in the technology of the present invention, and the speed changer 2 that only exists in the form of a single planetary gear train is not the only implementation of the technology speed changer 2 of the present invention . Under the situation that implements with non-terminal planetary gear train, the present invention "clutch closes/opens the mode of power path downstream of transmission" also can be applied on it easily, for example in the transmission state of a single output mode, the present invention The clutch only needs to "lock" this single power path, instead of simultaneously "locking" the ring gear 34 and the planet carrier 32 of the planetary gear train 3 in the reverse direction as in the disclosed embodiment.

Please refer to FIG. 5 and FIG. 6 (and please refer to FIG. 4 ), which are respectively an exploded view and a combined cross-sectional schematic diagram of the detailed implementation of the parts of the embodiment shown in FIG. 4 . The implementation of this embodiment is applied in a hub shell 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 hub shell 5, to cooperate with the implementation of the power transmission system of the present invention , the arrangement between the hub shell 5 as the rotation output and the system includes a right side ratchet ring 51, a hub shell ratchet ring 53 fixed in the hub shell 5 as a system output intermediary, and a left side on the other side. Bead bowl 55 and a hub shell left side cover 57 of this other side sealing.

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

The transmission 2 connected to the power source 100 is implemented with a single planetary gear train 3, but also includes a sun gear 31 pivotally arranged on the shaft center 10 and directly driven by the power source 100, a planet carrier 32, a ring gear 34, and A plurality of planetary gears 33 (three in the figure) are pivoted on the planet carrier 32 and meshed and rotated between the sun gear 31 and the ring gear 34 .

Please refer to FIG. 6 and FIG. 7 , wherein FIG. 7 is used to simply show the corresponding relationship between the planet carrier 32 , the ring gear 34 and the hub shell ratchet ring 53 . As shown in the figure, the output system of the planetary gear train 3 can be output by one of the ring gear 34 or the planet carrier 32 when it is rotating forward, through the hub shell ratchet ring 53 to the externally rotating Hub shell 5. In terms of design, in order to use a single member, that is, the hub shell ratchet ring 53, as the common output member of the ring gear 34 and the planet carrier 32, in terms of construction, the outer diameter of the ring gear 34 or the planet carrier 32 (as The size of the power output end) is about equal, so that the selective output between the two and the hub shell ratchet ring 53 can be implemented conveniently. In this embodiment, the connection between the ring gear 34 and the ratchet ring 53 of the hub shell, and the connection between the planetary carrier 32 and the ratchet ring 53 of the hub shell are in the form of ratchet rings with pawls and one-way engaging ratchet rings. One-way clutch 200 for it.

As shown in FIG. 7 , the ring gear 34 of the present invention may further include a ring gear tooth portion 341 meshing with the planetary gear 33 , and an adjacent ring gear ratchet portion 343 serving as a control input from the clutch 1 .

Please refer to Fig. 8, which is a three-dimensional exploded view of the main components of the clutch 1 of the power transmission system with the rear clutch device of the present invention; as mentioned above, the clutch 1 of the present invention is controlled by external force to determine the planetary gear 3 output methods. In addition, the force is input by the clutch transmission group 4, and its implementation direction is directed from the second direction shown in the figure to the first direction. This feed action also stores the potential energy in the return torsion spring 19, After the external force is removed, the state of the clutch 1 is automatically restored (feeding from the first direction to the second direction) to the position of "closing the power path" of "making the planetary carrier 32 and the ring gear 34 idle at the same time".

As shown in the figure, the clutch 1 in this embodiment mainly includes a fulcrum fixed seat 11 fixedly combined with the shaft center 10 and unable to rotate, a ring gear control cam 13 arranged on the fulcrum fixed seat 11 close to the clutch transmission group 4, a The planetary carrier control cam 15 that is located on the other end surface of the fulcrum fixed seat 11, and a plurality of planetary carrier telescopic bumps 17 that are arranged on the planetary carrier 32 and can elastically protrude or retract toward the planetary carrier control cam 15 (three are shown in the figure) ), and a set of return torsion springs 19 (see Fig. 6) set on the center flange of the fulcrum holder 11.

The fulcrum fixing seat 11 is a fixed ring body, on which a central peripheral rib ring 111, a plurality of pawl through holes 113 (three shown in the figure) located on the inner edge of the rib ring 111, and a plurality of corresponding planetary rings are arranged. The protrusion clamping holes 115 (three shown in the figure) of the telescopic protrusions 17 of the frame, and the fulcrum pawls 201 pivotally arranged in the pawl through holes 113 and exposed on both sides of the rib ring 111 .

The ring gear control cam 13 is arranged on the side surface of the transmission member 45 of the fulcrum fixed seat 11 near the clutch transmission group 4, and is linked with the transmission member 45, and includes a plurality of driving cylinders 451 on the corresponding transmission member 45. The input member 131 (three in the figure) and a plurality of control sliding slots 133 (three in the figure) corresponding to the pawl through hole 113 on the fulcrum fixing seat 11 and the fulcrum pawl 201 . Wherein, the driving column 451 and the driving input member 131 , and the fulcrum pawl 201 (or the pawl through hole 113 ) and the control sliding groove 133 adopt corresponding configurations, and its implementation is based on the principle of being arranged in pairs. In the present invention, the composition of the control chute 133 is configured 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. (jack up) or closed (down) state, and then determine whether the ring gear 34 is in a locked fulcrum state in its own reverse direction. As shown in the figure, the control chute 133 can further include a chute first end 1331 and a chute second end 1333 .

The planet carrier control cam 15 is located on the other end surface of the fulcrum holder 11 close to the planetary gear train 3, and is in the shape of a circular plate. Cooperate with the position of the telescopic convex point 17 of the planetary frame, a multi-pivot guide arm 151 is protruded from the outer edge of the planetary frame control cam 15, and the convex point guide arm 151 is directed outward from the disc body towards the fulcrum fixing seat 11 and extend obliquely for 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 protrusion guiding arm 151 is defined as a closed end 1511 .

The telescoping bumps 17 of the planet carrier are arranged in the bump receiving holes on the planet carrier 32 , and elastically protrude toward the control cam 15 of the planet carrier, and their relative positions correspond to the bump locking holes 115 on the fulcrum fixing seat 11 .

In the clutch 1 of the foregoing embodiment, the ring gear control cam 13 and the planetary carrier control cam 15 are limitedly linked with the transmission member 45 of the clutch transmission group 4, and the fulcrum fixing seat 11 is fixed on the shaft center 10; in other words Yes, the combination of the gear control cam 13 and the planetary carrier control cam 15 and the fulcrum holder 11 are relatively rotatable at a limited angle, and the range of rotation is the same as the length of the control chute 133 .

As shown in the figure, the direction extending 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 called the reverse direction), and the direction extending from the second end 1333 of the chute to the chute The direction of the first end 1331 is defined as the first direction (this direction can also be called the forward rotation direction).

Please refer to FIG. 10 , which is an exploded perspective view of the main components of the clutch transmission set 4 of the power transmission system with the rear clutch device of the present invention. Wherein, the clutch transmission group 4 includes a transmission part 41 for external force input, a transmission pawl seat 43 driven by the transmission part 41, and a transmission part 45. At least one one-way clutch 200 is provided on the periphery of the transmission pawl seat 43. , the one-way clutch 200 is engaged with the one-way ratchet on the inner ring surface of the right ratchet ring 51 . When the power transmission system of the present invention is arranged on an electric rollator, the transmission member 41 may be combined with the pedal crank of the electric rollator, whereby when the rider begins to step on the pedals forward, That is to provide an external force input to the transmission member 41 to make it 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 system 3 has no power output), the one-way clutch 200 of the transmission pawl seat 43 will engage and drive the right ratchet The ring 51 rotates forward together with the hub shell 5 which is closely fitted and fixed with the ratchet ring 51 on the right side. In other words, the external force input by the transmission member 41 will be directly used to drive the hub shell 5 to rotate. And when the transmission member 41 drives the transmission pawl seat 43 to reverse, no matter whether the power source 100 provides power, the one-way clutch 200 of the transmission pawl seat 43 will slip with the right ratchet ring 51 mutually. As for, when the power source 100 provides power and the transmission member 41 drives the transmission pawl seat 43 to rotate forward, the power output by the power source 100 through the planetary gear train 3 will help drive the hub shell 5 to rotate forward; The forward rotation speed of the hub shell 5 driven by the gear train 3 is greater than the forward rotation speed of the transmission pawl seat 43, and the one-way clutch 200 of the transmission pawl seat 43 will slip; 43 forward rotation speed, the power output by the power source 100 can provide a torque, so that the external force input from the transmission member 41 has a labor-saving effect.

The transmission member 45 is disposed in a central cavity 451 of the transmission pawl seat 43 , and communicates with the drive input member 131 on the ring gear control cam 13 through the drive cylinder 451 thereon. And between the transmission ratchet seat 43 and the transmission member 45, a C-shaped torsion spring 47 as a linkage buffer between the two is set again. The C-shaped torsion spring 47 is sleeved in the annular groove provided on the outermost ring surface of the transmission member 45, and a protruding end of the C-shaped torsion spring 47 is engaged with a torsion spring positioning point on the side of the central cavity 431 433 and combined with the transmission pawl seat 43. This C-shaped torsion spring 47 can provide a function similar to a one-way clutch. When the transmission member 41 drives the transmission pawl seat 43 to rotate forward, because the C-shaped torsion spring 47 will have a tendency to reduce the inner diameter, it can be used for the transmission member 45. Provide a tightening force and drive it to rotate forward. Relatively, when the transmission member 41 drives the transmission pawl seat 43 to reverse, because the C-shaped torsion spring 47 will have a tendency to expand the inner diameter, so its tightening force on the transmission member 45 will be reduced and cause slippage, that is, the transmission member. 45 does not follow the tendency to reverse. However, whether it is forward rotation or reverse rotation, once the transmission member 45 cannot continue to rotate due to some reasons (such as but not limited to the lock between the clutch transmission group 4 and the planetary gear train 3), no matter whether the transmission member 41 drives the transmission ratchet When the claw seat 43 rotates forward or reversely, 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 make it rotate in the first direction (forward rotation direction) (that is, the action of opening the power path with the intervention of an external force), its parts are actuated by The transmission member 41 rotates at a certain angle pointing to the first direction, and the pawl seat 43 is linked to drive the transmission member 45 to buffer and drive the transmission member 45 to input the forward rotation action to the clutch 1; at the same time, the external force also stores the potential energy to Back in the torsion spring 19. In the clutch 1, the action of the transmission member 45 makes the ring gear control cam 13 also rotate in the first direction. At this time, the fulcrum pawl 201 is relatively slid from the first end 1331 of the chute to the chute. The second end 1333 . At this time, the fulcrum pawl 201 is located at the other end of the rib ring 111, that is, it forms a one-way solidified state with the ring gear ratchet part 343 on the ring gear 34 to open upwards, so that the ring gear 34 of the planetary gear train 3 is reversed in itself. In the direction, it will be locked by the fulcrum pawl 201 to form a force fulcrum during the operation of the planetary gear train, and then turn on the actuation output of the planetary carrier 32 when it is rotating forward, that is, turn on the planetary carrier 32 to rotate forward. direction of the power output path. And at the same time, the bump guide arm 151 of the interlocking planetary carrier control cam 15 promptly rotates due to forward rotation and is stretched into the corresponding bump clamping hole 115, under the front edge of the planet telescopic bump 17. (bottom side of Figure 9) to exit. By means of the push-pull action of the bump guide arm 151 and the elastic recovery force inside the planetary telescopic bump 17 , the planetary telescopic bump 17 re-protrudes into the bump hole 115 of the fulcrum fixing seat 11 to be anchored. That is, the planetary carrier 32 and the fulcrum fixing seat 11 are unidirectionally consolidated in the reverse direction of the planetary carrier 32 itself, so that the planetary carrier 32 of the planetary gear train 3 will be anchored by the planetary telescopic bump 17 in its own reverse direction. The locking effect of the fixed point locking hole 115 forms the fulcrum of force during the operation of the planetary gear train, and then opens the actuation output of the ring gear 34 in the forward rotation, that is, opens the ring gear 34 in its own forward rotation direction power output path. To put it simply, when an external force intervenes to make the transmission member 45 of the clutch transmission set 4 rotate forward, both the ring gear 34 and the planetary carrier 32 will be unidirectionally consolidated by the clutch 1 in their own reverse direction and can It provides the function of a fulcrum, and can output power in both the forward rotation direction of the ring gear 34 and the planet carrier 32 .

At this time, the rotation direction of the sun gear 31 driven by the power source 100 will determine whether the power will be output by the ring gear 34 or the planet carrier 32 . When the input of the sun gear 31 is forward rotation force, the planetary carrier 32 will have a forward rotation tendency, while the ring gear 34 will have a reverse rotation tendency; therefore, the ring gear 34 will be pushed against by the fulcrum pawl 201 of the clutch 1 It is locked to become a fulcrum, and the power is output to the hub shell 5 to rotate forwardly by the planetary carrier 32 rotating forwardly. At this time, the planetary telescopic bump 17 and the bump clamping hole 115 will be in a slipping state. In contrast, when the input of the sun gear 31 is reverse power, the planetary carrier 32 will have a tendency to reverse, while the ring gear 34 will have a tendency to rotate forward; therefore, the planetary carrier 32 will be anchored by the planetary telescopic bump 17 The locking effect of the protrusion locking hole 115 forms a fulcrum for bearing force during the operation of the planetary gear train, and the power is output from the forward rotating ring gear 34 to the hub shell 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 action of closing the power path without external force intervention), the potential energy in the return torsion spring 19 is released, and the clutch transmission group 4 is directed to the second direction ( reversing) on the return rotation. At this time, its parts are actuated: the transmission member 41 performs a return rotation pointing to the second direction at a certain angle, and the pawl seat 43 is linked to drive the transmission member 45, and then the ring gear control cam 13 is directed to the second direction. reverse rotation on.

In the clutch 1, the ring gear control cam 13 is also reversely rotated in the second direction by the reverse movement of the transmission member 45. At this time, the fulcrum pawl 201 slides from the second end 1333 of the chute to the opposite direction. The first end 1331 of the chute. At this time, the fulcrum pawl 201 is located at the other end of the rib ring 111, that is, forms a downwardly closed slippage state with the ring gear ratchet part 343 on the ring gear 34, so that the ring gear 34 of the planetary gear train 3 is rotated forward regardless of its own normal rotation. Or in the reverse direction, it will slip off from the fulcrum pawl 201 and cannot form a force fulcrum. Simultaneously, the bump guide arm 151 of the interlocking planetary carrier control cam 15 promptly stretches into the corresponding bump clamping hole 115 due to reverse rotation, under the leading edge of the planet telescopic bump 17 (as shown in the 9th figure). dotted line position), through the pushing and pulling action of the bump guide arm 151, the telescopic bump 17 of the planet is "shoveled out" from the bump hole 115 where the anchor is anchored, that is, the planet carrier 32 is separated from the fulcrum fixing seat 11 Therefore, the planetary carrier 32 of the planetary gear train 3 will present a slipping state with the planetary carrier control cam 15 no matter in its forward rotation or reverse direction, and cannot form a force fulcrum. Thereby, since the entire planetary gear train 3 does not have any element that can be a force fulcrum; therefore, even if the power source 100 still provides power input at this time, no matter whether the power input by the sun gear 31 is forward rotation or reverse rotation, it can only The entire planetary gear train 3 is idling, and the ring gear 34 or the planet carrier 32 cannot be driven to output power to the hub shell 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 The planet carriers 32 are in a free-rotating state not fixed to the shaft 10 , therefore, the planetary gear train 3 cannot transmit any power that can be output to the hub shell 5 .

In the foregoing embodiments of the present invention, two interlocking but separate pairs of cams and followers are included, one of which is used to control the fulcrum operation of the ring gear 34 (the ring gear controls the cam mechanism), and the other is used to Operate with the fulcrum of the control planetary carrier 32 (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; while in the planetary carrier control cam mechanism, the cam profile is the configuration of the bump guide arm 151. configuration, the follower is the telescopic protrusion 17 of the planet carrier. In the prior art, there are many types of combined cams, which can be easily implemented by those who are familiar with this type of art according to the foregoing disclosure of the present invention; for example, in another non-illustrated embodiment That is, the ring gear control cam 13 and the planetary carrier control cam 15 can be combined into a plate body, and set on the same side of the rib ring 111, and then cooperate with the space of other parts and the interference elimination treatment of the action, the aforementioned implementation can be achieved The function of the example, and the variation similar to this kind of equivalent is familiar to those skilled in this kind of art, and does not go beyond the scope of the disclosure of the present invention, so it will not be repeated here.

In each of the embodiments described below, since the structures and functions of most components are the same as those of the above-mentioned embodiments, the same or similar components will be directly given the same component names and numbers, and the details will not be repeated.

Please refer to FIG. 11 , which is a schematic diagram of the structural configuration of the second preferred embodiment of the power transmission system with the rear clutch device of the present invention. The power transmission system of this embodiment is generally similar to the previous embodiments, and is also built in a hub shell 5 for driving the hub shell 5 to rotate. Moreover, it is also arranged according to a fixed shaft center 10 , which also includes a power source 100 , a transmission 2 , a clutch 1 , and a clutch transmission group 4 . The transmission 2 includes several rotatable transmission parts, and these transmission parts further include a terminal planetary gear train 7 connected to the hub shell 5 by a one-way clutch 200 as a power output. Similarly, at least a part of the clutch 1 is fixed to the shaft 10 and acts as a power output "switch" (Switch) without the function of power transmission. 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 the transmission parts in the transmission 2 In the non-consolidated release state, all the transmission parts in the transmission 2 do not have any fulcrum, so that the power cannot be output through the terminal planetary gear train 7 of the transmission 2 . That is to say, 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 shell 5 . When the external force drives the clutch 1 through the clutch transmission group 4 to "open the power path", the terminal planet carrier 72 of the terminal planetary gear train 7 and the shaft center 10 are consolidated in one direction (forward rotation direction). A one-way locked state that slips in the other direction (reverse direction). That is to say, when the clutch 1 enters the state of "opening the power path", the clutch 1 forms a solid form with at least one of the transmission parts in the transmission 2 (that is, the terminal planet carrier 72 of the terminal planetary gear train 7). knot, so that the consolidated transmission part (terminal planet carrier 72) becomes the force fulcrum of the transmission 2, and then its power can pass through other unconsolidated transmission parts in the transmission 2 (that is, set at the terminal The one-way clutch 200) between the final ring gear 74 of the planetary gear train 7 and the hub shell 5 is output.

The differences between the second preferred embodiment of the present invention shown in FIG. 11 and the foregoing embodiments are explained as follows.

In the embodiment shown in FIG. 11, the power source 100 is a motor whose outer casing is fixed and the inner rotor 104 can rotate in forward and reverse directions. The inner rotor 104 of the power source 100 (motor) is sheathed on the shaft 10 in a relatively rotatable manner and can rotate forward or reverse relative to the fixed shaft 10 . The transmission 2 series includes two sets of planetary gear trains (one of which is the aforementioned terminal planetary gear train 7 ). Among them, the group of planetary gear trains adjacent to the power source 100 can be called the front-end planetary gear train, which includes a front-end sun gear 61, a front-end planetary carrier 62, several (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 (engages when the inner rotor 104 rotates forward, and slips when the inner rotor 104 rotates reversely). The front-end planet carrier 62 is fixed to the casing of the power source 100 and is a fixed component. The front end ring gear 64 is connected to the terminal sun gear 71 of the terminal planetary gear train 7 and rotates in conjunction with it.

The terminal planetary gear train 7 is adjacent to the clutch 1 and is controlled by it to determine whether the rotational power can be output to the hub shell 5 . The terminal planetary gear train 7 also includes: a terminal sun gear 71 , a terminal planetary carrier 72 , several (usually three) terminal planetary gears 73 , and a terminal ring gear 74 . In addition to the terminal sun gear 71 being driven to rotate by the front ring gear 64, there is also another one-way clutch 106 between the inner rotor 104 and one-way engagement (the inner rotor 104 engages when it reverses, and slips when it rotates forward). . The terminal planetary carrier 72 is connected to the clutch 1, and whether the terminal planetary carrier 72 will be consolidated by the clutch 1 can be determined by whether there is an external force through the clutch transmission group 4 to drive the clutch 1 to actuate and then become the transmission 2. Force fulcrum. A one-way clutch 200 is provided between the terminal ring gear 74 and the hub shell 5 for one-way engagement (the terminal ring gear 74 engages when it rotates forward, and slips when it rotates reversely). With the aforementioned structure, the second preferred embodiment can also provide two different speed ratios through the forward and reverse rotation of the inner rotor 104 of the power source 100, and whether there is an external force applied from the clutch transmission group 4 The function of actuating the clutch 1 to determine whether the terminal planetary gear train 7 can output power to the hub shell 5 .

As for the clutch 1 in the second preferred embodiment, its specific structure and actuation mode are generally similar to the embodiment shown in Fig. 8, the difference is that the clutch in the second preferred embodiment 1. Only the terminal planetary carrier 72 needs to be consolidated, and only one set of one-way clutches 201 need to be set between the clutch 1 and the shaft center 10 (engagement in forward rotation and slipping in reverse rotation).

Please refer to FIG. 12A and FIG. 12B , which are respectively schematic diagrams of the structure and configuration of the third preferred embodiment of the power transmission system with the rear clutch device of the present invention (the state of closing the power path and the state of opening the power path). Most of the components of the third preferred embodiment are the same as those of the second preferred embodiment shown in FIG. 11 , so details will not be repeated here. 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, the design between the clutch 1 and the shaft 10 can be relatively slid in the axial direction between a bite position and a Slide key 202 between disengagement positions. When no external force is applied to the clutch 1 from the clutch transmission group 4, the sliding key 202 is maintained at the disengaged position (that is, the "closed power path" state as shown in Figure 12A), resulting in the terminal planetary gear train 7 can only idle at most and cannot produce any power that can be output to the hub shell 5. And when an external force is applied to the clutch 1 from the clutch transmission group 4, the sliding key 202 will be switched to the engaged position (that is, the state of "opening the power path" as shown in Figure 12B), and the clutch 1 is in contact with the clutch 1. The terminal planetary carrier 72 of the terminal planetary gear train 7 is formed and consolidated as a fulcrum, so that its power can be output through the transmission of the one-way clutch 200 between the terminal ring gear 74 and the hub shell 5 .

However, the above-mentioned embodiments should not be used to limit the applicable scope of the present invention, and the protection scope of the present invention should be based on the technical spirit defined in the claims of the present invention and the range covered by equivalent changes. That is, all equivalent changes and modifications made according to the claims of the present invention will still not lose the gist of the present invention, nor depart from the spirit and scope of the present invention, so all should be regarded as further implementation status of the present invention.

Claims (8)

1. a kind of dynamic transfer system with back segment clutch apparatus, is arranged according to an axle center fixed, it is characterised in that bag Include：

One power source；

One variator, is connected with the power source, carries out transformation of speed, the variator to the power exported to the power source Also include a terminal epicyclic train as the output of power；The epicyclic train is hubbed on the axle center and by this including one again The central gear of power source drive, a planet carrier, a rim gear wheel and be hubbed on the planet carrier and engagement rotation in the sun Multiple planetary gears between gear and the rim gear wheel；

One clutch, controls start by an external force, and to determine the way of output of the epicyclic train, its selection has free pass Close power path state and there are the path status that turn on the power of the external force intervention；The clutch is made when there is the external force to intervene When turning on the power path status into this, the clutch is by both the rim gear wheel of the epicyclic train and the planet carrier At least one forms consolidation with the axle center in the reverse direction of itself, in making both the rim gear wheel and the planet carrier At least one can become fulcrum force when the epicyclic train is operated in the reverse direction of itself so that by this too The power of positive gear input, it is defeated through carrying out for rotating forward person in both in the planet gear drives planet carrier and the rim gear wheel Go out；And work as after the external force removes, the clutch is elastic recovery to the cut out power path state, and now, the clutch will The planet carrier of the epicyclic train and rim gear wheel release, so that both the planet carrier and the rim gear wheel cannot become this Fulcrum force when epicyclic train is operated, now, the power being input into by the central gear cannot pass through the planetary gear System's output；And,

One clutch transmission group, the external force are transmitted to the clutch through the clutch transmission group；When have the external force put on this from When closing transmission group, the clutch transmission group can order about the clutch entrance path status that turn on the power；And work as after the external force removes, The clutch transmission group can allow the clutch to return back to the closing power path state；

The described clutch again including one to control the rim gear wheel fulcrum operate rim gear wheel control cam mechanism and The one planet carrier control cam mechanism operated to the fulcrum for controlling the planet carrier；

The clutch control cam mechanism and the planet carrier to control cam mechanism system to be two gearings but discrete including rim gear wheel again Cam and driven member pair；In the rim gear wheel control cam mechanism, the cam contour system is to slide with a control of the external force start Groove, and the driven member is then the fulcrum ratchet of a fixation；And in planet carrier control cam mechanism, the cam contour system be with One salient point guid arm of the external force start, and the driven member is then provided at the flexible salient point of the planet carrier on the planet carrier.

2. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 1, it is characterised in that again including a flower Drum shell, the power source, the variator and the clutch system be arranged in the flower drum shell, wherein the rim gear wheel and the planet carrier system and A flower drum shell ratchet ring in the flower drum shell forms an other one-way clutch respectively and combines.

3. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 1, it is characterised in that the clutch transmission Group includes that a driving member being input into for the external force, a driving click seat driven by the driving member and one are direct by power again Transmit to the driving member of the clutch, the driving click seat and this power is directly transferred between the driving member of the clutch and is set One is put as the C-shaped torsion spring that buffering is interlocked between the two.

4. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 1, it is characterised in that in the clutch It is further provided between the axle center one of following：An at least one-way clutch and the slide key of key slot type design；Its In, the slide key axially opposed can be slided between an occlusal position and a disengaging configuration；When being applied to this without any external force During clutch start, the slide key is to maintain in a disengaging configuration namely closing power path state；And working as has external force to apply When adding to the clutch start, the slide key can be switched to an occlusal position namely path status that turn on the power.

5. a kind of dynamic transfer system with back segment clutch apparatus, is arranged according to an axle center fixed, it is characterised in that bag Include：

One power source；

One variator, is connected with the power source, is exported to the power that receives to export the power source and after being driven again； Also, some driving sections are at least included in the variator；

One clutch, is to control start by an external force, and to determine the way of output of the variator, its selection has a closing power Path status and one turn on the power path status；At least part of system of the clutch is consolidated with axle center；And,

One clutch transmission group, the external force are transmitted to the clutch through the clutch transmission group；When have the external force put on this from When closing transmission group, the clutch transmission group can order about the clutch entrance path status that turn on the power；And work as after the external force removes, The clutch transmission group can allow the clutch to return back to the closing power path state；

Wherein, when the clutch entrance this turn on the power path status when, the clutch be with the variator at least within One of driving section formed consolidation, make the driving section being consolidated become the fulcrum force of the variator, and then make the power saturating Cross the transmission of other driving sections not being consolidated in the variator and export；

Wherein, when the clutch enters the cut out power path state, the clutch is and all biographies in the variator Dynamic portion all forms the release conditions not consolidated, and makes all no any fulcrum force in all of driving section in the variator, enters And the power is exported through the variator；

Some driving sections described in the variator include a terminal epicyclic train as the output of power again；The planetary gear System is again hubbed on the axle center including one and by the central gear of the power source drive, a planet carrier, a rim gear wheel and is pivoted On the planet carrier and multiple planetary gears of the engagement rotation between the central gear and the rim gear wheel；

When there is the external force to intervene the clutch, the clutch entrance path status that turn on the power, now, the clutch be by At least one in both the rim gear wheel and the planet carrier of the epicyclic train is in the reverse direction of itself and is somebody's turn to do Axle center forms consolidation, make in both the rim gear wheel and the planet carrier at least one can in the reverse direction of itself into Fulcrum force when operating for the epicyclic train so that the power being input into by the central gear, through the planet gear drives Exported for rotating forward person in both in the planet carrier and the rim gear wheel；And work as after the external force removes, the clutch is that elasticity is returned It is multiple to the closing power path state, now, the clutch will the epicyclic train the planet carrier and the rim gear wheel release Put, so that both the planet carrier and the rim gear wheel cannot become the fulcrum force when epicyclic train is operated, now, by this The power of central gear input, i.e., cannot export through the epicyclic train；

The described clutch again including one to control the rim gear wheel fulcrum operate rim gear wheel control cam mechanism and The one planet carrier control cam mechanism operated to the fulcrum for controlling the planet carrier；

The clutch control cam mechanism and the planet carrier to control cam mechanism system to be two gearings but discrete including rim gear wheel again Cam and driven member pair；In the rim gear wheel control cam mechanism, the cam contour system is to slide with a control of the external force start Groove, and the driven member is then the fulcrum ratchet of a fixation；And in planet carrier control cam mechanism, the cam contour system be with One salient point guid arm of the external force start, and the driven member is then provided at the flexible salient point of the planet carrier on the planet carrier.

6. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 5, it is characterised in that again including a flower Drum shell, the power source, the variator and the clutch be arranged in the flower drum shell, wherein the rim gear wheel and the planet carrier system and this A flower drum shell ratchet ring in flower drum shell forms an other one-way clutch respectively and combines.

7. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 5, it is characterised in that the clutch transmission Group includes that a driving member being input into for the external force, a driving click seat driven by the driving member and one are direct by power again Transmit to the driving member of the clutch, the driving click seat and this power is directly transferred between the driving member of the clutch and is set One is put as the C-shaped torsion spring that buffering is interlocked between the two.

8. there is the dynamic transfer system of back segment clutch apparatus as claimed in claim 5, it is characterised in that in the clutch It is further provided between the axle center one of following：An at least one-way clutch and the slide key of key slot type design；Its In, the slide key axially opposed can be slided between an occlusal position and a disengaging configuration；When being applied to this without any external force During clutch start, the slide key is to maintain in a disengaging configuration namely closing power path state；And working as has external force to apply When adding to the clutch start, the slide key can be switched to an occlusal position namely path status that turn on the power.