TWM562779U - Hub with idle running ratchet surface release effect - Google Patents

Abstract

The present invention provides a flower hub with a ratchet surface disengaging effect during idling, which mainly comprises: a gear cylinder which is arranged on the mandrel and is located at a spacing of the driven end of the hub, and the gear cylinder is provided with first and second receiving portions. A ratchet disk is fixed on the driven end of the hub, and the first annular ratchet surface of the ratchet disk is opposite to the gear cylinder; a double-sided free tooth disk is disposed in the first receiving portion and is co-moving with the gear cylinder, and double-sided The free toothed disc includes a single steering engagement relationship between the second annular ratchet surface and the first annular ratchet surface; an elastic expansion member is disposed between the ratchet disk and the double-sided free toothed disc to Distracting the first and second annular ratchet surfaces in the idle mode; a repeller disk is circumferentially positioned to be mounted on the second receiving portion; and an axial repeller member includes the first and second repeller portions It is set on the double-sided free toothed disc and the repeller disc.

Description

Flower hub with detached ratchet surface

The present invention relates to a bicycle hub; in particular, an innovative flower hub structure type revealer having a ratcheting surface that is disengaged from each other in an idle mode.

In the bicycle flower hub structure design, in order to allow the user to drive the rear wheel forward when the pedal is being stepped on (ie, stepping forward), when the user does not step on the pedal, the rear wheel can still rotate forward without the pedal. The effect, which exhibits an idle mode, is typically achieved through the configuration of the ratchet assembly.

Looking at the structure of the ratchet assembly of the conventional bicycle hub, the inner ratchet disc and the outer ratchet disc are generally the main state switching members through the mutually elastic engagement state, wherein the inner ratchet disc and the flower hub move together, The ratchet disk is in the same motion as the gear-driven cylinder of the bicycle. When the outer ratchet disk is positively rotated due to the pedal being stepped on, the single oblique tooth surface is engaged by the single oblique tooth surface of the inner ratchet disk. State, conversely, when the user does not step on the pedal, the single oblique tooth surface between the inner ratchet disk and the outer ratchet disk will repel the mutual push to exhibit a relative misalignment, in which the bicycle rider can usually The tooth surface friction sound emitted by the single oblique tooth surface relative to the misalignment is clearly heard, and this also means that the inner ratchet disk and the outer ratchet in the ratchet assembly are in the idle mode when the bicycle rear wheel is in the idle mode. Although the discs can be retracted from each other between the slanted tooth faces, there is still considerable frictional resistance between the two, and this level of frictional resistance is a bicycle that requires speed and pedaling force output efficiency today. In terms of travel status, Will produce a relatively large traffic obstacles, especially for athletics car, the impact is more significant.

It can be seen that in the face of the current and future development trend of bicycles, the wheel hub ratchet assembly in the idle mode can achieve lower resistance or even close to zero resistance, which is obviously not negligible in the relevant industry. Important technical issues.

Therefore, in view of the problems existing in the above-mentioned bicycle bicycle hub technology, how to develop an innovative structure that can be more ideal and practical, and the relevant industry should further consider the goal and direction of breakthrough; in view of this, create People have been engaged in the manufacturing development and design experience of related products for many years. After the detailed design and careful evaluation of the above objectives, they will have a practical and practical creation.

The main purpose of this creation is to provide a flower hub with a ratchet surface disengagement effect during idling. The technical problem to be solved is to develop a new type of flower hub structure which is more ideal and practical. The goal is to think about innovative breakthroughs.

The technical feature of the present problem solving problem is mainly that the flower hub comprises: a mandrel which is fixed and cannot rotate; a hub is screwed on the mandrel, and the hub has an axial end; the gear cylinder is screwed on The mandrel is located at an axial interval of the driven end of the hub, and the outer circumference of the gear barrel has a gear sleeve portion, and the gear tube is concavely opposite to one end of the driven end of the hub, and the first receiving portion and the second receiving portion are sequentially formed. And the gear cylinder is operated in three modes including a forward rotation, a reverse rotation and a fixed rotation; the ratchet disk is fixed on the driven end of the hub and rotates synchronously with the hub, the ratchet disk has a first annular ratchet surface corresponding to the gear cylinder, the first annular ratchet surface includes a plurality of first single oblique tooth edges; and a double-sided free tooth disk disposed in the first housing portion of the gear cylinder The double-sided free toothed disc and the gear cylinder rotate in a synchronous relationship, and the double-sided free toothed disc is selectively pushed and displaced along the axial direction of the gear cylinder, and the double-sided free toothed disc includes the second annular ratchet surface and Pushing the surface, the second annular ratchet surface includes a plurality of second monoclinic a tooth edge, the second single oblique tooth edge and the first single oblique tooth edge of the first annular ratchet surface are in a single steering engagement relationship; an elastic expansion member is mounted on the ratchet disk and the double Between the free tooth plates, the double-sided free tooth disk is elastically pushed away from the ratchet disk, and the first annular ratchet surface and the second annular ratchet surface are oppositely formed when the gear cylinder is in the fixed and non-rotating mode. a detachment disc is disposed in a second receiving portion of the gear barrel, the repulsion disc is restricted in a circumferential direction with respect to the mandrel, and the repeller disc is pressed against the pushing surface; The repeller member includes a first repulsion portion and a second repulsion portion correspondingly disposed, wherein the first repeller portion is disposed on the pushed surface of the double-sided free sprocket wheel, and the second repulsion portion is disposed on the repeller The abutting surface of the disk, when the gear cylinder is in the forward rotation driving mode, and the double-sided free tooth disk is rotated with respect to the repulsion disk, the axis is generated between the first repeller and the second repeller Pushing force to push the double-sided free toothed disc toward the ratchet disk, so that the second annular ratchet surface and the first ring Ratchet engagement surface.

The main effect and advantage of the present invention is that when the gear cylinder of the flower hub is in the fixed non-rotation mode, the double-sided free toothed disc can be elastically pushed away from the ratchet disk through the elastic expansion member, and the two rings are formed. The ratchet surfaces are completely separated from each other, so that when the wheel hub is idling, the mutually engaging ratchet surfaces are completely disengaged, and the effect of zero resistance, no jamming friction and practical progress can be achieved.

Please refer to the first, second, and third figures, which are preferred embodiments of the flower hub with the ratchet surface disengaging effect when the idling is performed, but the embodiments are for illustrative purposes only, and are not used in patent applications. Limited by this structure.

The hub A includes a structure in which a mandrel 10 is fixed and cannot be rotated; a hub 20 is screwed to the spindle 10, and the hub 20 has a driven end 21 in the axial direction; a gear cylinder 30, Rotating on the mandrel 10 and axially spaced apart from the driven end 21 of the hub 20, the outer circumference of the gear barrel 30 has a gear sleeve 33, and the gear barrel 30 is inwardly facing one end of the driven end 21 of the hub 20 A first accommodating portion 31 and a second accommodating portion 32 are formed in a concave manner, and the gear cylinder 30 is operatively provided with three modes of positive rotation, reverse rotation, and non-rotation with respect to the hub 20; A ratchet disk 40 is fixed to the driven end 21 of the hub 20 in a synchronous rotational relationship with the hub 20, and the ratchet disk 40 has a first annular ratchet surface 41 corresponding to the gear cylinder 30. The first annular ratchet surface 41 includes a plurality of first single oblique tooth edges 415; a double-sided free toothed disc 50 is mounted on the first receiving portion 31 of the gear cylinder 30, and the double-sided free toothed disc 50 is The gear cylinder 30 is in a synchronous rotational relationship in the circumferential direction, and the double-sided free toothed disc 50 is selectively pushed along the axis of the gear cylinder 30. Displacement, the double-sided free toothed disc 50 includes a second annular ratchet surface 52 and a pushed surface 51, and the second annular ratchet surface 52 includes a plurality of second single oblique tooth edges 525, the second The single oblique tooth edge 525 and the first single oblique tooth edge 415 of the first annular ratchet surface 41 are in a single steering engagement relationship; an elastic expansion member 60 is mounted on the ratchet disk 40 Between the double-sided free sprocket 50, the double-sided free sprocket 50 is elastically pushed away from the ratchet disk 40, and the first ring is formed when the gear cylinder 30 is in the fixed and non-rotating mode. The ratchet surface 41 and the second annular ratchet surface 52 are separated from each other; a repeller disk 70 is mounted on the second housing portion 32 of the gear cylinder 30, and the repeller disk 70 is opposite to the The mandrel 10 is in a circumferentially restricted positioning state (ie, the repeller disk 70 cannot be rotated relative to the mandrel 10), and a gap is left between the outer circumference of the repeller disk 70 and the second accommodating portion 32 of the gear barrel 30. In an unconnected relationship, the repeller disk 70 has an abutting surface 71; an axial repulsion member 80 includes a first repeller 81 and a second repeller 8 correspondingly disposed. 2, wherein the first repeller portion 81 is disposed on the pushing surface 51 of the double-sided free sprocket 50, and the second repulsion portion 82 is disposed on the urging surface 71 of the repeller tray 70. When the double-sided free toothed disc 50 is rotated in the forward rotation driving mode with respect to the repulsion disk 70, an axial direction is generated between the first repeller 81 and the second repulsion portion 82. The force of the mutual pushing force pushes the double-sided free toothed disc 50 toward the ratchet disk 40 to engage the second annular ratchet surface 52 with the first annular ratchet surface 41.

As shown in FIG. 1 , in the present example, the outer circumference of the double-sided free toothed disc 50 and the first receiving portion 31 of the gear cylinder 30 are provided with oppositely engaging annular tooth edges 55 and 315 to The face free toothed disc 50 is in a synchronous rotational relationship with the gear barrel 30.

As shown in FIGS. 1 to 8, in this example, the first repulsion portion 81 and the second repulsion portion 82 of the axial repulsion member 80 are annular mountain-shaped tooth surface patterns that mesh with each other; An elastic supporting member 91 is disposed between the repeller 70 and a fixing surface of the second receiving portion 32 of the gear cylinder 30, and the elastic force of the elastic supporting member 91 is greater than the elastic force of the elastic expanding member 60. Further, the mandrel 10 is provided with a certain guiding position limiting member 92 for limiting the displacement of the repulsion disk 70 within a set axial stroke range; and as shown in FIG. 3a, the first single oblique toothing The maximum depth of engagement between the edge 415 and the second single oblique tooth edge 525 (as indicated by B1) must be greater than the annular flank surfaces of the first repeller 81 and the second repulsion portion 82. Depth (as indicated by B2); the ring of the first repeller 81 and the second repeller 82 when the first single oblique tooth edge 415 and the second single oblique tooth edge 525 are completely tightly engaged The ridge-shaped tooth faces can be completely disengaged from each other without affecting the driving of the hub 20 by the gear cylinder 30 (because the repeller disk 70 is in an unrotatable state with respect to the mandrel 10); in this example, The guide limiting member 92 is specifically sleeved on the mandrel 10 as shown in FIG. 1 , and is provided with an annular rib 921 and a plurality of axial protrusions of the spacer ring array. a rib 923, one end of each of the axial ribs 923 is connected to the annular rib 921, and the other end of each of the axial ribs 923 extends to one end of the fixed guiding member 92 to make the repulsion The disk 70 is provided with a plurality of axial guiding grooves 72 corresponding to the axial ribs 923.

As shown in FIG. 1 , in this example, the elastic expansion member 60 is a coil spring, and the elastic top support member 91 is a wave spring, a coil spring or a two-magnetic body with opposite poles. By.

With the above-mentioned structural composition and technical features, the use of the present application in the practical application is as shown in the above preferred embodiment, first as shown in the second and third figures, the gear cylinder 30 is in the forward rotation mode. The state is indicated, and the state is a state in which the rear wheel of the bicycle is forwardly driven by the positive step. In this state, since the repeller disk 70 is restricted from being positioned relative to the mandrel 10 and is not rotatable, the double-sided free sprocket 50 It has the characteristics of rotatable and axial displacement, so when the gear cylinder 30 is driven forward by the shifting gear (not shown) of the bicycle (as indicated by the arrow L1), the axial repulsion member 80 is annular. The first repulsion portion 81 and the second repeller portion 82 of the mountain-shaped flank meshing type are driven by the inclined surface repulsive action to drive the double-sided free toothed disc 50 to the left in the figure (as indicated by the arrow L2). The second annular ratchet surface 52 of the double-sided free toothed disc 50 is engaged with the first annular ratchet surface 41 of the ratchet disk 40 to drive the hub 20 to rotate forward (as indicated by arrow L3); Next, as shown in FIG. 3a, when the second annular ratchet surface 52 of the double-sided free toothed disc 50 and the ratchet disk 40 are When the first annular ratchet surfaces 41 are completely in close mesh with each other, the annular flank surfaces constituting the first repulsion portion 81 and the second repulsion portion 82 are separated from each other to form a gap (as shown by B3). And compressing the elastic expansion member 60 to accumulate the elastic force, and this portion has to be explained that since the first annular ratchet surface 41 and the second annular ratchet surface 52 are in mesh with each other, the tooth mask is slightly different. The barb fits the state design (see the shape depicted in Fig. 3a), so when the gear cylinder 30 is in the forward rotation mode, the first annular ratchet surface 41 and the second annular ratchet surface 52 can obtain the best friction. State, and ensure that the two can be displaced in a state in which they are in close mesh with each other (note: using the inclined surface guiding action), without any detachment due to the elastic struts of the elastic expansion member 60; then, as shown in Figures 4 and 5 As shown in the figure, the gear cylinder 30 is in a state of being in a non-rotation mode, and the state is a state in which the bicycle rear wheel is idling and undriven. In this state, the double-sided free toothed disc 50 is axially repulsed. 80 is pushed to the left of the figure to release the force, so the elastic expansion member 60 The elastic release action pushes the double-sided free toothed disc 50 back to the right in the figure (as indicated by the arrow L4 in FIG. 4), at this time, due to the ring shape of the first repeller 81 and the second repeller 82 The maximum depth of the kinematic tooth surface engagement is greater than the maximum depth of engagement between the first single oblique tooth edge 415 and the second single oblique tooth edge 525, so when the double-sided free toothed disc 50 is pushed back to the right in the figure When the repulsion portion 81 and the second repeller portion 82 are fully engaged, the ratchet disk 40 and the double-sided free sprocket 50 are completely separated from each other to form a gap W (as shown in FIG. 6), which constitutes the A zero-resistance state exists between an annular ratchet surface 41 and the second annular ratchet surface 52, so that the creation of the bicycle can achieve the ratchet-free friction and sound when the bicycle rear wheel is in the idle mode. The excellent driving quality state, which is not comparable to the conventional flower hub; and then, as shown in Figures 7 and 8, the gear cylinder 30 is reversely driven with respect to the hub 20, and the state is the corresponding bicycle pedal. a state of being stepped backwards, in this state, through the arrangement of the elastic top support member 91, the double-sided free toothed disc 50 is reversed When the tooth surface is displaced between the first repeller 81 and the second repulsion portion 82, the repulsion disk 70 is displaced toward the right in the figure (as indicated by the arrow L5 in FIG. 8). Therefore, the aforementioned tooth surface shifts can smoothly cross each other, thereby avoiding the tooth flanks between the respective toothed discs being closely bitten to each other, which is a structural protection measure in the preferred embodiment.

As shown in FIGS. 9 and 10, the elastic expansion member 60B disclosed in the present embodiment is a first magnetic body 61 which is disposed in a relationship between the ratchet disk 40 and the double-sided free tooth disk 50. a second magnetic body 62, and the first magnetic body 61 and the second magnetic body 62 are opposite to each other (such as N pole to N pole or S pole to S pole) and exhibit a normal repulsive relationship with each other ( As shown by the arrow L6 in Fig. 10, this type is also one of other specific embodiments.

As shown in FIGS. 11 and 12, in this example, the first repulsion portion 81B of the axial repulsion member 80B is an annular mountain-shaped tooth surface type provided on the pushed surface 51 of the double-sided free sprocket 50. The second repulsion portion 82B includes a plurality of elastic swinging claws 85 disposed on the abutting surface of the repulsion pad 70B, and each of the elastic oscillating claws 85 includes a pivoting end 851 and a urging end 852. The supporting end 852 abuts against the tooth bottom position of the annular mountain-shaped tooth surface of the pushing surface 51, and each of the elastic swinging claws 85 is combined with a torsion spring 86 to set the elastic end of the abutting end 852. In the state of the lower pressing angle, the repulsion pad 70B is in a state in which the steering and the axial position are both positioned and not displaceable with respect to the mandrel 10; the abutting surface of the repulsion pad 70B is provided with a corresponding one for each elastic swinging claw 85. Limiting edge 73 to limit the maximum lifting angle of each elastic swinging claw, and when the abutting end 852 of each of the elastic swinging claws 85 is in a set elastic lower pressing angle state, the elastic expanding member 60 is to The double-sided free toothed disc 50 is elastically pushed away from the ratchet disk 40 (as shown in Fig. 12) to constitute the first annular ratchet surface 41 and the second annular ratchet surface 52 are separated from each other. For the operation of this example, please refer to the figures 11 and 12, wherein the figure 11 shows the state in which the gear cylinder 30 is in the forward rotation driving mode. In this state, the abutting end 852 of each elastic swinging claw 85 will be The first repulsion portion 81B of the mountain-shaped tooth surface type is driven to be in a lifted state, thereby driving the double-sided free sprocket 50 to the left in the figure (as indicated by an arrow L8 in FIG. 11). The second annular ratchet surface 52 meshes with the first annular ratchet surface 41 of the ratchet disk 40, thereby driving the hub 20 to rotate forward, and compressing the elastic expansion member (not shown) to accumulate elastic force; 12 is a state in which the gear cylinder 30 is in a state of being fixed in an unrotated mode, that is, a state in which the bicycle rear wheel is idling and undriven, and in this state, the double-sided free toothed disc 50 is axially repulsion member 80B. The force pushed to the left in the figure is released, so the elastic release function of the elastic expansion member (not shown) pushes the double-sided free toothed disc 50 back to the right in the figure (such as the arrow of Fig. 12) L9), and the abutting end 852 of the elastic swinging claw 85 is returned to the set depression angle state by the elastic force of the torsion spring 86. Ratchet teeth 40 constituting the double-sided disc is completely free from the zero resistance state ratchet surface formed by a gap 50 of separation between the chainring.

In the embodiment disclosed in the above paragraph, when the first repulsive portion 81B of the annular mountain-shaped tooth surface pattern is reversed when the gear cylinder 30 is in the reverse rotation driving mode, as shown in FIG. 13, the elastic swinging claws 85 are abutted. The support end 852 is elastically depressed to the lowest angle state, so that the first repulsion portion 81B spans the abutment end 852 of the elastic swing claw 85 (as indicated by an arrow L10).

Efficacy Description: The "Human hub with the effect of the ratchet surface disengagement when idling" is mainly disclosed by the mandrel, the hub, the gear cylinder, the ratchet disc, the double-sided free toothed disc, the elastic expansion member, and the push The innovative and unique structure of the disc and the axial repulsion member constitutes the configuration type and technical features, so that the design of the prior art is based on the conventional structure, and the gear cylinder of the hub is in the unrotated mode. The elastic free-dissipating member can be elastically pushed away from the ratchet disk through the elastic distracting member, so that the annular ratchet surfaces of the two are completely separated from each other, so that the bicycle hub is idling when the wheel body is idling. The ratchet surface driven by the mutual engagement is completely disengaged, and the effect of zero resistance, no jamming friction and practical progress can be achieved.

A‧‧‧Flower hub 10‧‧‧ mandrel 20‧‧·wheel 21.‧‧Accepted end 30‧‧‧Gear cylinder 31‧‧‧First housing part 315‧‧‧ring tooth edge 32‧‧‧ Second accommodating part 33‧‧‧ Gear sleeve part 40‧‧‧ Ratchet disc 41‧‧‧First annular ratchet surface 415‧‧‧First single oblique tooth edge 50‧‧ ‧ double-sided free tooth Plate 51‧‧‧Pressed face 52‧‧‧Second annular ratchet surface 525‧‧‧Second single oblique tooth edge 55‧‧‧Ring tooth edge 60‧‧‧ elastic expansion member 61‧‧‧ The first magnetic body 62‧‧‧ the second magnetic body 70, 70B‧‧‧ the repeller disk 71‧‧‧ the pushing surface 72‧‧‧ the axis guiding groove 80, 80B‧‧‧ axial repulsion member 81, 81B‧‧‧First Repulse 82, 82B‧‧‧Second Repulsion 85‧‧‧Flexive Swinging Claw 851‧‧‧Pivot End 852‧‧‧Resistance End 86‧‧‧ Torsion Spring 91‧‧ ‧Elastic top support 92‧‧‧Guided limiter 921‧‧‧Ring rib 23‧‧‧ axial ribs

Figure 1 is an exploded perspective view of the preferred embodiment of the present invention. Fig. 2 is a cross-sectional view showing the state in which the gear cylinder of the preferred embodiment of the present invention is in a forward rotation mode. Fig. 3 is a side view of a partial member corresponding to Fig. 2. Fig. 3a is a schematic view showing the state in which the first and second annular ratchet surfaces of Fig. 3 are fully meshed. Fig. 4 is a cross-sectional view showing the state in which the gear cylinder of the preferred embodiment of the present invention is in a non-rotation mode. Figure 5 is a side view of a partial member corresponding to Figure 4. Fig. 6 is a partially enlarged schematic view of Fig. 5. Fig. 7 is a cross-sectional view showing the state in which the gear cylinder of the preferred embodiment of the present invention is reversely driven. Figure 8 is a side view of a partial member corresponding to Figure 7. Fig. 9 is an exploded perspective view showing an embodiment in which the elastic expansion member of the present invention is composed of a first magnetic body and a second magnetic body. Figure 10 is a combined cross-sectional view of the embodiment of Figure 9. Fig. 11 is a schematic view showing the state of the gear cylinder of the other embodiment of the axial repulsion member of the present invention in a forward rotation mode. Fig. 12 is a schematic view showing the state in which the gear cylinder disclosed in Fig. 11 is in a state of being fixed and not rotated. Fig. 13 is a schematic view showing the state in which the gear cylinder disclosed in Fig. 11 is reversely driven.

Claims (8)

A hub having a ratchet surface disengaging effect during idling, the hub comprising: a mandrel that is fixed and unrotatable; a hub that is screwed to the mandrel, the hub having a driven end in the axial direction; a gear cylinder is disposed on the mandrel and is axially spaced apart from the driven end of the hub. The outer circumference of the gear cylinder has a gear sleeve portion, and the gear cylinder is concavely formed at one end of the driven end of the hub and sequentially formed There is a first receiving portion and a second receiving portion, and the gear tube is operatively provided with three modes of positively rotating, reversing, and non-rotating relative to the hub; a ratchet disk is fixed on the a receiving end of the hub in synchronous rotation relationship with the hub, the ratchet disk having a first annular ratchet surface corresponding to the gear barrel, the first annular ratchet surface comprising a plurality of first single oblique teeth a double-sided free toothed disc is disposed in the first receiving portion of the gear cylinder, the double-sided free toothed disc and the gear cylinder are in a circumferential synchronous rotation relationship, and the double-sided free toothed disc is selectively subjected to Pushing along the axial displacement of the gear barrel, and the double-sided free The disk includes a second annular ratchet surface and a pushed surface, the second annular ratchet surface includes a plurality of second single oblique tooth edges, the second single oblique tooth edge and the first annular ratchet The first single oblique tooth edge is in a single steering engagement relationship; an elastic expansion member is disposed between the ratchet disk and the double-sided free toothed disk to elasticize the double-sided free toothed disk Pushing away from the ratchet disk, when the gear cylinder is in the fixed and non-rotating mode, the first annular ratchet surface and the second annular ratchet surface are separated from each other; The second accommodating portion of the gear cylinder is disposed in a circumferential direction with respect to the spindle, and the outer circumference of the repeller disc and the second housing portion of the gear cylinder are left between The first repeller and the second repeller are disposed in a corresponding manner, wherein the first repeller and the second repulsion are correspondingly disposed. The repeller is disposed on the pushing surface of the double-sided free sprocket, and the second repulsion portion is disposed on the urging surface of the repulsion disc, when the gear cylinder When the double-sided free toothed disc is rotated relative to the repulsion disc in the forward rotation driving mode, an axial mutual pushing force is generated between the first repeller and the second repeller. Thereby, the double-sided free toothed disc is pushed against the ratchet disk to engage the second annular ratchet surface with the first annular ratchet surface. The flower hub with the detachment ratchet surface disengaging effect according to the first aspect of the invention, wherein the outer circumference of the double-sided free toothed disc and the first receiving portion of the gear cylinder are provided with a relatively engaged ring shape. The tooth edge is such that the double-sided free toothed disc and the gear cylinder rotate in a synchronous relationship. The flower hub having the ratchet surface disengaging effect when idling as described in claim 2, wherein the first repulsion portion and the second repulsion portion of the axial repulsion member are ring-shaped meshes with each other a mountain-shaped tooth surface type; an elastic top support member is disposed between the repeller disk and a fixing surface of the second receiving portion of the gear tube, and the elastic force of the elastic top support member is greater than the elastic force expanding member The elastic force, and the spindle shaft setting position has a certain guiding limit member for limiting the displacement of the repeller disk within a set axial stroke range; and wherein the first single oblique tooth edge and the second single oblique direction The maximum depth of engagement between the tooth edges must be greater than the maximum depth at which the annular flank surfaces of the first repeller and the second repulsion engage each other. A flower hub having a ratchet surface disengaging effect when idling as described in claim 3, wherein the elastic expansion member is a coil spring. The flower hub with the detachment ratchet surface disengaging effect as described in claim 3, wherein the elastic expansion member is disposed on the ratchet disk and the double-sided free tooth disk are spaced apart from each other. And a first magnetic body and a second magnetic body, and the first magnetic body and the second magnetic body are in a normal repulsion relationship with the same poles. The flower hub having the ratchet surface disengaging effect when idling, as described in claim 4 or 5, wherein the elastic top support member is a coil spring, a wave spring or a two-magnetic body in which the same pole is oppositely disposed. One of them. The flower hub having the ratchet surface disengaging effect when idling as described in claim 2, wherein the first repeller of the axial repulsion member is provided on the pushed surface of the double-sided free sprocket The second repulsion portion includes a plurality of elastic swinging claws disposed on the abutting surface of the repeller disk, each of the elastic swinging claws including a pivoting end and a urging end, The abutting end abuts against the bottom of the annular mountain-shaped tooth surface of the pushed surface, and each of the elastic swinging claws is assembled with a torsion spring, so that the abutting end is in a set elastic lower pressing angle state. The repeller disc is in a state in which the steering and the axial position are both positioned and not displaceable relative to the mandrel, and the urging surface of the repeller disc is provided with a limiting edge corresponding to each elastic swinging claw to limit each The elastic swinging claw is lifted to a maximum angle, and when the abutting end of each of the elastic swinging claws is in a set elastic lower pressing angle state, the elastic expanding member elastically pushes the double-sided free toothed disc away from the ratcheting disc. Thereby, the first annular ratchet surface and the second annular ratchet surface are separated from each other. The flower hub having the ratchet surface disengaging effect when idling, as described in claim 7, wherein the first repulsor of the annular mountain-shaped tooth surface type is reversed when the gear cylinder is in the reverse rotation driving mode The abutting end of each of the elastic swinging pawls is elastically depressed to a minimum angle state, and the first repeller is required to span the abutting end of the elastic swinging pawl.