Silent hub

Abstract

The invention discloses a silent flower hub, comprising main components such as a gear barrel, a fixed ratchet disc, a free toothed disc, a propulsion disc, a rotation linkage component, a guide seat, an axial pushing component, a reset torsion spring and a magnetic attraction component; when the free toothed disc is in a released position, the gear barrel is in a stationary non-rotating mode, at this time, because the axial pushing component has not yet performed an axial pushing action, and the magnetic attraction force of the magnetic attraction component will cause the free toothed disc to reset to the released position, so that the driving convex part and the driven convex part of the rotation linkage component are engaged, and the free toothed disc and the fixed ratchet disc are completely disengaged; when the pedal is not stepped on during the movement of the bicycle, the silent flower hub will not have the sound of ratchets getting stuck to each other and the existence of resistance, and can indeed achieve the ideal state of silence and zero resistance.

Description

Technical Field

[0001] The invention relates to a bicycle hub, and in particular to an innovative silent hub structure in which the ratchet surfaces of a free toothed disc and a fixed ratchet disc can be completely disengaged from each other in an idling mode. Background Art

[0002] The bicycle wheel hub structure is designed to allow the rear wheel to rotate forward when the user is pedaling (i.e., stepping forward), and when the user is not pedaling, the rear wheel can still rotate forward without being affected by the pedals, presenting the so-called "idling mode". This function is usually achieved through the configuration of a ratchet assembly.

[0003] The ratchet assembly structure of the conventional bicycle wheel hub is generally composed of an inner fixed ratchet disc and an outer fixed ratchet disc in an elastic meshing state with each other as the main state switching component, wherein the inner fixed ratchet disc moves together with the wheel hub, and the outer fixed ratchet disc moves together with the gear drive cylinder of the bicycle. When the outer fixed ratchet disc is indirectly driven to rotate forward due to the positive pedaling, its single oblique tooth surface bites into the single oblique tooth surface of the inner fixed ratchet disc to present an engaged driving state; when the user does not pedal, the single oblique tooth surfaces between the inner fixed ratchet disc and the outer fixed ratchet disc will repel and push each other to present a relative dislocation jumping state. In this process, the bicycle rider Usually, the tooth surface friction sound caused by the relative misalignment and jumping of the single oblique tooth surface can be clearly heard, and this state also shows that when the rear wheel of the conventional bicycle is in the idling mode, although the single oblique tooth surfaces of the inner fixed ratchet plate and the outer fixed ratchet plate in the ratchet assembly can be retracted from each other, there is still a considerable friction resistance between the two in fact, and this degree of friction resistance is bound to produce a relatively large driving obstacle. The speed that the cyclist has finally brought up by pedaling hard will quickly weaken due to the influence of the aforementioned friction resistance and must be accelerated again. For competitive bicycles, the impact is more significant.

[0004] On the other hand, when people are riding bicycles, whether they are facing various road conditions or experiencing the beautiful scenery and tranquil atmosphere along the way, they are often disturbed by the friction sound of the teeth, which more or less affects the quality of riding bicycles. This is also a problem that the bicycle-related industry currently wants to further improve.

[0005] It can be seen that in the face of the current and future development trend of higher quality design of bicycles, how to achieve lower or even zero resistance requirements for the hub ratchet assembly of the wheel body in the idling mode is an important technical issue that cannot be ignored by the relevant industry. Summary of the invention

[0006] The main purpose of the present invention is to provide a silent hub.

[0007] In order to achieve the above object, the present invention adopts the following technical solutions:

[0008] A silent hub comprises: a spindle, which is arranged along an axial direction in a fixed and non-rotatable state; a wheel hub, which is coaxially rotated on the outer periphery of the spindle, and the axial direction of the wheel hub has a driven end; a gear cylinder, which is rotated at an interval on the outer periphery of the spindle and adjacent to the driven end of the wheel hub, and the outer periphery of the gear cylinder has a gear sleeve portion, and the gear cylinder is concave inwardly corresponding to the driven end to form a receiving cavity, and an inner ring tooth is provided at a place on the inner wall of the receiving cavity, and the gear cylinder operation includes three modes relative to the wheel hub, namely, forward rotation drive, reverse rotation drive and fixed non-rotation; a fixed ratchet plate, which is arranged at the driven end of the wheel hub in a positioning state and is in a synchronous rotation relationship with the wheel hub, and the fixed ratchet plate is located at the interval on the outer periphery of the spindle, and the fixed ratchet plate has a first annular ratchet surface facing the position of the gear cylinder direction; a free toothed disc, installed in the gear cylinder accommodating cavity and located at the outer periphery of the spindle, an outer ring tooth is provided on the outer periphery of the free toothed disc, and the outer ring tooth is relatively meshed with the inner ring tooth provided on the inner wall of the accommodating cavity of the gear cylinder, so that the free toothed disc and the gear cylinder are in a synchronous rotation relationship, and the free toothed disc can be pushed and displaced along the axial direction of the gear cylinder, so that the free toothed disc has a meshing position and a releasing position change in actuation, and the free toothed disc is provided with a second annular ratchet surface and a driving surface, when the free toothed disc is in the meshing position, a single steering meshing driving relationship is formed between the second annular ratchet surface and the first annular ratchet surface, and when the free toothed disc is in the releasing position, the second annular ratchet surface and the first annular ratchet surface are completely disengaged from each other; a A propulsion disc is installed in the gear barrel accommodating cavity and is located on the outer periphery of the spindle. The propulsion disc is in a state of being able to rotate and axially displace under force. The propulsion disc has a driven side and a pushing side, and the driven side corresponds to the driving surface of the free toothed disc; a rotation linkage component includes a plurality of driving protrusions arranged in an interval ring array on the driving surface of the free toothed disc, and a plurality of driven protrusions arranged in an interval ring array on the driven side of the propulsion disc; when the free toothed disc is in a released position, the driven protrusions and the driving protrusions are relatively meshed, thereby forming a state in which the propulsion disc is driven to rotate by the free toothed disc, and when the free toothed disc is in an engaged position, the driven protrusions and the driving protrusions are mutually disengaged; a guide seat is installed in the gear barrel accommodating cavity in a positioning state and is located on the outer periphery of the spindle. The guide seat has a guide surface, which corresponds to the pushing side of the propulsion disc; a plurality of axial pushing members are arranged between the guide surface of the guide seat and the driven side of the propulsion disc in an annular and spaced distribution form. When the propulsion disc rotates relative to the guide seat, an axial thrust is generated by the equiaxial pushing members to push the propulsion disc together with the free toothed disc toward the fixed ratchet disc, so as to drive the free toothed disc to move to the meshing position; a reset torsion spring is arranged at the corresponding position of the propulsion disc and the guide seat, so that the rotation of the propulsion disc has a reset elastic force; a magnetic attraction member is installed in the gear barrel accommodating cavity and positioned at a place on the outer circumference of the spindle, and the magnetic field formed by the installation position of the magnetic attraction member is used to generate a reset magnetic attraction force to move the free toothed disc from the meshing position to the release position.

[0009] The main effect and advantage of the present invention is that the silent hub can achieve a state in which the second annular ratchet surface of the free sprocket and the first annular ratchet surface of the fixed ratchet disc are completely disengaged when the rider does not step on the pedal during the bicycle's movement. Therefore, there will be no sound or resistance caused by the ratchets getting stuck to each other. Therefore, the ideal silent and zero-resistance actuation state and practical progress can be achieved, thereby greatly improving the riding quality of the bicycle.

[0010] Another purpose of the present invention is to provide a standby stroke section in the form of a straight surface on the adjacent side of each guide surface, and the circumferential path stroke of the standby stroke section is in the angle range of 5 degrees to 150 degrees, so that each push block must pass through the standby stroke section before it aligns with the corresponding inclined guide surface to produce an inclined surface push motion. Another technical feature can achieve the function and practical improvement of not driving the axial push too sensitively when the user's foot has a slight forward or backward stepping action when the user stops pedaling.

[0011] Another purpose of the present invention is to further reduce the axial volume of the overall structure of the hub by providing a driving surface of the free sprocket in the form of an axially concave surface, relative to the free sprocket, to define an axially concave space for the propulsion disk to be embedded therein, thereby facilitating the design development trend of further miniaturization of the hub and achieving practical advancement. BRIEF DESCRIPTION OF THE DRAWINGS

[0012] Figure 1 This is a three-dimensional diagram of the detailed components of a preferred embodiment of the present invention.

[0013] Figure 2 It is a three-dimensional diagram of partial components of a preferred embodiment of the present invention.

[0014] Figure 3 This is a corresponding diagram of the three-dimensional assembly relationship between the free toothed disc and the propulsion disc of the present invention.

[0015] Figure 4 This is a corresponding diagram of the three-dimensional assembly relationship between the propulsion disc and the guide seat of the present invention.

[0016] Figure 5 It is a combined cross-sectional view of the related structures of the free toothed disc of the present invention in the released position.

[0017] Figure 6 For the corresponding Figure 5 Side view of the appearance of local components in the state shown.

[0018] Figure 7 for Figure 5 Partial enlarged image.

[0019] Figure 8 This is a combined sectional view of the related structures of the free toothed disc moving toward the meshing position of the present invention.

[0020] Fig. 9 For the corresponding Figure 8 Side view of the appearance of local components in the state shown.

[0021] Fig.10 for Figure 8 Partial enlarged image.

[0022] Fig.11 It is a cross-sectional view of the structure combination of the free toothed disc of the present invention in the meshing position.

[0023] Fig.12 For the corresponding Fig.11 Side view of the appearance of local components in the state shown.

[0024] Fig.13 for Fig.11 Partial enlarged image.

[0025] Fig.14 Schematic diagram of the axial push member of the present invention performing axial push action Figure 1 .

[0026] Fig.15 Schematic diagram of the axial push member of the present invention performing axial push action Figure 2 .

[0027] Fig.16 Schematic diagram of the axial push member of the present invention performing axial push action Figure 3 .

[0028] Fig.17 This is another preferred embodiment of the axial pushing component structure of the present invention.

[0029] Fig.18 This is a diagram showing an embodiment of the present invention in which the driving convex portion and the driven convex portion have an inclination angle. DETAILED DESCRIPTION

[0030] See also Figures 1 to 7 As shown, preferred embodiments of the silent hub of the present invention are shown, but these embodiments are for illustration only and are not limited to this structure in the patent application.

[0031] The silent hub comprises the following components: a spindle 10, which is arranged along an axial direction L1 and is fixed and cannot rotate; a wheel hub 20, which is coaxially rotated on the outer periphery of the spindle 10, and the wheel hub 20 has a driven end 21 in the axial direction; a gear cylinder 30, which is rotated at an interval on the outer periphery of the spindle 10 and adjacent to the driven end 21 of the wheel hub 20, and the outer periphery of the gear cylinder 30 has a gear sleeve portion 31, and one end of the gear cylinder 30 is concave inwardly corresponding to the driven end 21 to form an accommodating cavity 32, and an inner ring tooth 33 is provided at a place on the inner wall of the accommodating cavity 32, and the gear cylinder 30 is relatively stable during operation. The wheel hub 20 includes three modes: forward rotation drive, reverse rotation drive and stationary non-rotation (i.e., stop pedaling state, also known as idling mode); a fixed ratchet plate 40 is arranged at the driven end 21 of the wheel hub 20 in a positioning state and is in a synchronous rotation relationship with the wheel hub 20, and the fixed ratchet plate 40 is located at the outer periphery of the spindle 10, and the fixed ratchet plate 40 has a first annular ratchet surface 41 facing the direction of the gear cylinder 30; a free toothed plate 50 is installed in the accommodating cavity 32 of the gear cylinder 30 and is located on the outer periphery of the spindle 10, and the free toothed plate 50 An outer ring tooth 51 is provided on the outer periphery, and the outer ring tooth 51 is meshed with the inner ring tooth 33 provided on the inner wall of the accommodating cavity 32 of the gear cylinder 30, so that the free toothed disc 50 and the gear cylinder 30 are in a synchronous rotation relationship, and the free toothed disc 50 can be pushed and displaced along the axial direction of the gear cylinder 30, so that the free toothed disc 50 has a meshing position and a release position change in actuation, and the free toothed disc 50 is provided with a second annular ratchet surface 52 and a driving surface 53. When the free toothed disc 50 is in the meshing position, the second annular ratchet surface 52 and the first annular ratchet surface 53 are formed. The ratchet surfaces 41 are in a single steering meshing driving relationship, and when the free toothed disc 50 is in the release position, the second annular ratchet surface 52 and the first annular ratchet surface 41 are completely disengaged from each other; a propulsion disc 60 is installed in the accommodating cavity 32 of the gear cylinder 30 and is located on the outer periphery of the spindle 10. The propulsion disc 60 is in a state of being able to rotate and axially displace under force, and the propulsion disc 60 has a driven side 61 and a pushing side 62, wherein the driven side 61 corresponds to the driving surface 53 of the free toothed disc 50; a rotating linkage member 70 (as shown in detail Figure 3 As shown in FIG. 1 ), it includes a plurality of driving protrusions 71 arranged in an interval ring array on the driving surface 53 of the free toothed disc 50, and a plurality of driven protrusions 72 arranged in an interval ring array on the driven side 61 of the propulsion disc 60; when the free toothed disc 50 is in the release position (as shown in FIG. Figure 5 , Figure 7 As shown in FIG. 1 , the driven protrusion 72 is relatively engaged with the driving protrusion 71, thereby forming a state in which the propulsion disk 60 is driven to rotate by the free toothed disk 50. When the free toothed disk 50 is in the engaged position (as shown in FIG. 1 ), the driven protrusion 72 is relatively engaged with the driving protrusion 71, thereby forming a state in which the propulsion disk 60 is driven to rotate by the free toothed disk Figures 11 to 13As shown in FIG. 1 , the driven protrusion 72 and the driving protrusion 71 are in a mutually disengaged state; a guide seat 80 is installed in the accommodating cavity 32 of the gear cylinder 30 in a positioning state (note: the guide seat 80 does not move with the gear cylinder 30) and is located on the outer periphery of the spindle 10. The guide seat 80 has a guide surface 81, and the guide surface 81 corresponds to the push side 62 of the propulsion disk 60; a plurality of axial propulsion members 90 are arranged between the guide surface 81 of the guide seat 80 and the push side 62 of the propulsion disk 60 in an annular spaced distribution form. When the propulsion disk 60 rotates relative to the guide seat 80, an axial thrust is generated by the axial propulsion members 90 to The propulsion disc 60 and the free toothed disc 50 are pushed toward the fixed ratchet disc 40 (note: this action is referred to as axial pushing in the following text) to drive the free toothed disc 50 to move to the meshing position; a reset torsion spring 101 is arranged at the corresponding position of the propulsion disc 60 and the guide seat 80 to make the propulsion disc 60 rotate with a reset elastic force; a magnetic attraction component 102 (which can be but is not limited to a strong magnet ring) is installed in the accommodating cavity 32 of the gear cylinder 30 and positioned at the outer periphery of the spindle 10, and the magnetic field formed by the installation position of the magnetic attraction component 102 is used to generate a reset magnetic attraction force to move the free toothed disc 50 from the meshing position to the release position.

[0032] like Figure 4 As shown, in this example, each axial pushing member 90 includes a pushing block 91 provided on the pushing side 62 of the pushing disk 60, and an inclined guide surface 92 provided on the guide surface 81 of the guide seat 80; this example mainly provides a preferred specific embodiment of the axial pushing member 90, which is simply a method of matching the protrusion with the inclined surface.

[0033] Based on the above structural components and technical features, the actuation changes of the preferred embodiment of the silent hub structure of the present invention in practical application are described as follows:

[0034] First, Figure 5 , Figure 6 , Figure 7 As shown in FIG. 1 , the free sprocket 50 is in the released position. This state corresponds to the state that the cyclist does not step on the bicycle pedal, so the gear cylinder 30 is in a stationary non-rotating mode. In this state, the push block 91 of the axial pushing member 90 and the inclined guide surface 92 are in a state where no axial pushing action is performed (such as Fig.14As shown in the figure), the magnetic attraction force formed by the magnetic attraction member 102 will cause the free sprocket 50 to move back to the release position, so at this time, the driving protrusion 71 and the driven protrusion 72 will be in a state of mutual engagement, and the second annular ratchet surface 52 and the first annular ratchet surface 41 will be completely disengaged from each other; it can be seen that when the rider does not step on the pedal during the movement of the bicycle, the silent hub of the present invention will not have any sound or resistance of the ratchets getting stuck to each other, so it can indeed achieve the ideal state of silence (or mute) and zero resistance; then, when the bicycle pedal is stepped on, the gear barrel 30 is in a forward driving mode, and the free sprocket 50 will also be driven to rotate forward (as shown in the figure). Figure 2 , Figure 8 As shown by arrow L2); Figures 8 to 10 As shown, the driving protrusion 71 and the driven protrusion 72 are engaged with each other, which drives the propulsion plate 60 to rotate relative to the guide seat 80, and at the same time pulls the return torsion spring 101 to accumulate a circumferential return elastic force. As the propulsion plate 60 continues to rotate, the push block 91 and the inclined guide surface 92 are guided by an inclined surface, thereby achieving the axial push action (such as Figures 14 to 16 When the propulsion disc 60 is axially moved, the free toothed disc 50 is pushed toward the fixed ratchet disc 40. Figures 8 to 10 The figure shows the initial meshing state between the second annular ratchet surface 52 and the first annular ratchet surface 41. Because it is a ratchet bevel meshing relationship, once the tooth surfaces are partially meshed, the first annular ratchet surface 41 will produce an axial hooking and guiding effect on the second annular ratchet surface 52, so that the two quickly bite each other, thereby achieving the following Figures 11 to 13 The free toothed disc 50 is shown in a state of being fully meshed with the fixed ratchet disc 40, and at this time, the driving protrusion 71 of the free toothed disc 50 and the driven protrusion 72 of the propulsion disc 60 are disengaged from each other and have a gap (such as Fig.13 The purpose of forming the gap is that after the second annular ratchet surface 52 and the first annular ratchet surface 41 are fully meshed, the free toothed disc 50 will drive the fixed ratchet disc 40 to rotate together with the wheel hub 20. Therefore, at this time, the original axial push of the propulsion disc 60 against the free toothed disc 50 has been completed. In order to prevent the propulsion disc 60 from interfering with the rotation of the free toothed disc 50, the driving protrusion 71 and the driven protrusion 72 are disengaged to solve this problem. When the driving protrusion 71 and the driven protrusion 72 are disengaged, the propulsion disc 60 is immediately disengaged from the linkage relationship with the free toothed disc 50. At this time, the reset elastic force previously accumulated by the reset torsion spring 101 will pull the propulsion disc 60 back to the state before the axial push action (such as Fig.14 When the cyclist returns to the state of not stepping on the bicycle pedal again, the second annular ratchet surface 52 and the first annular ratchet surface 41 will be retracted due to relative reversal, returning to Figures 5 to 7In the state shown, the magnetic attraction force of the magnetic attraction member 102 will drive the free toothed disc 50 to move back to the release position. This state is the same as described above and will not be described again.

[0035] like Figure 1 , Figure 7 As shown, in this example, a cylinder 11 is tightly positioned on the outer periphery of the mandrel 10, and an annular groove 12 is provided on the outer periphery of the cylinder 11 for the magnetic attraction member 102 to be embedded and positioned therein; this example mainly provides a preferred specific positioning method for the magnetic attraction member 102. Figure 5 As shown, further, the back side of the annular groove 12 is relatively defined to form an annular shoulder 13, and the propulsion plate 60 is correspondingly provided with a bearing surface 63 (Note: it can be provided on a side surface of each push block 91, as shown in detail Figure 3 As shown in the figure, a corrugated spring 103 or a conical spring (not shown) is disposed between the annular shoulder 13 and the bearing surface 63 to elastically press against the propulsion disk 60; the effect of the embodiment shown in this example is mainly that when the free toothed disk 50 is fully engaged with the fixed ratchet disk 40, the corrugated spring 103 can push the propulsion disk 60 in the opposite direction to disengage from the free toothed disk 50, which helps to drive the rapid jump between the protrusion 71 and the driven protrusion 72, thereby more effectively avoiding the jamming phenomenon between the two. The conical spring can reach a single wire diameter thickness when flattened, and has a softer elastic force than the aforementioned corrugated spring, and the production industry can select it according to the elastic force requirements.

[0036] like Figure 1 , Figure 7 As shown, in this example, the outer end of the cylinder 11 is further screwed with an outer baffle 14 in an enlarged outer diameter shape, and the outer baffle 14 is used for the guide seat 80 to axially abut and limit, so that the outer baffle 14 and the guide seat 80 are both made of magnetic conductive materials, and a positioning magnetic member 15 (specifically, it can be a ring magnet) is provided between the outer baffle 14 and the guide seat 80 to magnetically position the guide seat 80 on the outer baffle 14; the implementation form shown in this example is mainly to provide a specific positioning method for the guide seat 80, and the magnetic property of the positioning magnetic member 15 set in this example also has a certain degree of axial reset auxiliary function and effect for the propulsion disk 60.

[0037] Cheng Figure 4 In the embodiment shown, the adjacent sides of each guide surface 81 are as follows Fig.14As shown, there is also a standby stroke section 82 in the form of a flat surface, and the circumferential path stroke of the standby stroke section 82 is in the angle range of 5 degrees to 150 degrees, so that each push block 91 must pass through the standby stroke section 82 when it moves, and then it will align with the corresponding inclined guide surface 92 to produce an inclined surface push movement; the effect of the implementation form shown in this example is mainly to allow the user to stop stepping (that is, the gear cylinder 30 is in a fixed and non-rotating mode), if the user's foot has a small angle of less than 35 degrees to step backward (that is, the gear cylinder 30 is in a reverse driving mode), so that the axial push function will not be driven too sensitively.

[0038] like Fig.17 As shown, in this example, each axial pushing member 90B includes a first arcuate groove 93 provided on the pushing side 62 of the pushing disk 60, a second arcuate groove 94 provided on the guide surface 81 of the guide seat 80, and a rigid ball 95 placed between the first arcuate groove 93 and the second arcuate groove 94; this example mainly provides another preferred specific embodiment of the axial pushing member 90B, in short, the ball cooperates with the concave arc surface.

[0039] like Figure 7 As shown, in this example, the driving surface 53 of the free toothed disc 50 is in the form of an axially concave surface, defining an axially concave space 54 relative to the free toothed disc 50 for the propulsion disc 60 to be embedded therein; the effect of the implementation form shown in this example is mainly that it can further reduce the axial volume of the overall structure of the hub 20, thereby being conducive to the development trend of further miniaturization of the hub 20 design.

[0040] like Fig.18 As shown, in this example, the driving protrusion 71B and the driven protrusion 72B are rigid protrusion bodies with a protruding angle (X) between 0 and 20 degrees, so that both can take into account reasonable driving force and smooth tooth withdrawal. Through the inclination shape of the driving protrusion 71B and the driven protrusion 72B, the noise when the two collide can be relatively reduced.

[0041] Continuing with the embodiment shown in the previous paragraph, one of the driving protrusion and the driven protrusion can be in the form of a vertical rigid protrusion without an inclination angle, and the other can be in the form of a rigid protrusion with an inclination angle of 10 to 20 degrees; this variation of the implementation can also achieve the effect described in the previous paragraph (Note: the drawings of this example are omitted).

[0042] The above is only a specific embodiment of the present invention, but the protection scope of the present invention is not limited thereto. Any person skilled in the art who is familiar with the technical field can easily think of changes or substitutions within the technical scope disclosed in the present invention, which should be included in the protection scope of the present invention. Therefore, the protection scope of the present invention should be based on the protection scope of the claims.

Claims

1. A silent hub, characterized in that include: A spindle, arranged along an axial direction in a fixed and non-rotatable state; A hub is coaxially rotatably disposed on the outer periphery of the spindle, and the hub has a driven end in the axial direction; A gear cylinder is rotatably mounted on the outer circumference of the spindle and adjacent to the driven end of the wheel hub. The outer circumference of the gear cylinder has a gear sleeve portion. One end of the gear cylinder corresponding to the driven end is concave inward to form a receiving cavity. An inner ring tooth is provided at a point on the inner wall of the receiving cavity. The gear cylinder has three operation modes relative to the wheel hub, namely, forward rotation driving, reverse rotation driving, and stationary non-rotating; A fixed ratchet plate is arranged at the driven end of the wheel hub in a positioning state and is in a synchronous rotation relationship with the wheel hub, and the fixed ratchet plate is located at the outer circumference of the spindle, and the fixed ratchet plate has a first annular ratchet surface facing the direction of the gear cylinder; A free toothed disc is installed in the gear barrel accommodating cavity and is located at the outer periphery of the spindle. An outer ring tooth is provided on the outer periphery of the free toothed disc. The outer ring tooth is relatively meshed with the inner ring tooth provided on the inner wall of the accommodating cavity of the gear barrel, so that the free toothed disc and the gear barrel are in a synchronous rotation relationship, and the free toothed disc can be pushed and displaced along the axial direction of the gear barrel, so that the free toothed disc has a meshing position and a release position change in actuation. The free toothed disc is provided with a second annular ratchet surface and a driving surface. When the free toothed disc is in the meshing position, a single steering meshing driving relationship is formed between the second annular ratchet surface and the first annular ratchet surface, and when the free toothed disc is in the release position, the second annular ratchet surface and the first annular ratchet surface are in a state of complete mutual disengagement; A propulsion disc is installed in the gear cylinder accommodating cavity and is located on the outer periphery of the spindle. The propulsion disc is capable of rotating and axially displacing under force. The propulsion disc has a driven side and a pushing side, wherein the driven side corresponds to the driving surface of the free toothed disc; A rotation linkage component, comprising a plurality of driving protrusions arranged in an interval ring array on the driving surface of the free toothed disc, and a plurality of driven protrusions arranged in an interval ring array on the driven side of the propulsion disc; when the free toothed disc is in a released position, the driven protrusions are relatively meshed with the driving protrusions, thereby forming a state in which the propulsion disc is driven to rotate by the free toothed disc, and when the free toothed disc is in an engaged position, the driven protrusions and the driving protrusions are mutually disengaged; A guide seat is installed in the gear cylinder accommodating cavity in a positioning state and is located at the outer periphery of the spindle. The guide seat has a guide surface, and the guide surface corresponds to the pushing side of the propulsion disc; A plurality of axial pushing members are arranged between the guide surface of the guide seat and the pushing side of the pushing disc in an annular spaced distribution form. When the pushing disc rotates relative to the guide seat, an axial thrust is generated by the equiaxial pushing members to push the pushing disc together with the free toothed disc toward the fixed ratchet disc, so as to drive the free toothed disc to move to the meshing position; A return torsion spring is arranged at the position corresponding to the propulsion disk and the guide seat, so that the propulsion disk has a return elastic force when rotating; and A magnetic attraction component is installed in the gear cylinder accommodating cavity and positioned at the outer circumference of the spindle. The magnetic field formed by the installation position of the magnetic attraction component is used to generate a magnetic attraction force to reset the free toothed disc from the meshing position to the release position.

2. The silent hub according to claim 1, characterized in that Each axial pushing component comprises a pushing block arranged on the pushing side of the pushing disk, and an inclined guide surface arranged on the guide surface of the guide seat.

3. The silent hub according to claim 2, characterized in that A standby travel section in the form of a straight surface is further provided on the adjacent side of each guide surface. The circumferential path of the standby travel section is in the angle range of 5 degrees to 150 degrees. When each push block moves, it must pass through the standby travel section before it aligns with the corresponding inclined guide surface to generate inclined surface push motion.

4. The silent hub according to claim 1, characterized in that Each axial pushing component comprises a first arc groove arranged on the pushing side of the pushing disk, a second arc groove arranged on the guiding surface of the guiding seat and a rigid ball disposed between the first arc groove and the second arc groove.

5. The silent hub according to claim 1, characterized in that The driving surface of the free toothed disc is in the form of an axially concave surface, and defines an axially concave space relative to the free toothed disc for the propulsion disc to be embedded therein.

6. The silent hub according to claim 1, characterized in that The driving convex part and the driven convex part are in the form of rigid convex pieces with a convex setting angle between 0 and 20 degrees.

7. The silent hub according to claim 1, characterized in that One of the driving convex part and the driven convex part is in the form of a vertical rigid convex piece without an inclination angle, and the other is in the form of a rigid convex piece with an inclination angle of 10 to 20 degrees.

8. The silent hub according to claim 1, characterized in that A cylinder is tightly sleeved and positioned on the outer periphery of the spindle, and an annular groove is arranged on the outer periphery of the cylinder for the magnetic attraction component to be embedded and positioned therein.

9. The silent hub according to claim 8, characterized in that The back side of the annular groove is relatively defined to form an annular shoulder, and the propulsion disc is correspondingly provided with a bearing surface, and a corrugated spring or a conical spring is arranged between the annular shoulder and the bearing surface to elastically press against the propulsion disc.

10. The silent hub according to claim 7, characterized in that The outer end of the cylinder is further screwed with an outer stopper with an enlarged outer diameter for the guide seat to abut axially against and limit, so that the outer stopper and the guide seat are both made of magnetic conductive materials, and a positioning magnetic member is provided between the outer stopper and the guide seat to magnetically position the guide seat on the outer stopper.

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