Patent Description:
In a conventional internal engagement transmission mechanism, a rotating shaft is disposed in an eccentric shaft, and thus the rotating shaft directly drives the eccentric shaft to rotate by means of the engagement of the external teeth of the rotating shaft and the internal teeth of the eccentric shaft. Although such driving method is simple in structure, it is inconvenient to machining due to the arrangement of the internal teeth in the eccentric shaft. Especially for a transmission mechanism with a small size, since the space of the hollow cavity in the eccentric shaft is small, it is difficult to process the internal teeth of the eccentric shaft.

Document <CIT> discloses a conventional internal engagement transmission mechanism comprising a planetary gear device.

Document <CIT> discloses a transmission mechanism having an outer case with internal pin teeth, an internal wheel engaging with the internal pin teeth, and three eccentric shafts having eccentric portions and capable of rotating about their central axis and about a central axis of the outer wheel.

The exemplary embodiment of this invention can solve at least some problems mentioned above. For example, the invention provides a transmission mechanism according to claim <NUM>.

According to the transmission mechanism described above, the periphery of the eccentric shaft is provided with a second supporting portion. The inner wheel is provided with at least two inner wheel through-holes. The transmission mechanism further comprises a second flange and at least two connection and transfer components. The first flange and the second flange are respectively arranged on opposite sides of the inner wheel, and the second flange is disposed around the second supporting portion. The each of the at least two connection and transfer components penetrates a corresponding one of the at least two inner wheel through-holes in the inner wheel, and the first flange and the second flange on opposite sides of the inner wheel are connected together. The eccentric portions of the eccentric shaft are arranged between the first flange and the second flange.

According to the transmission mechanism described above, each of the at least one planetary gearing device further comprises a planetary gear supporting portion, a first planetary gear and a second planetary gear. The first planetary gear is connected to the second planetary gear via the planetary gear supporting portion. The first row of planetary teeth and the second row of planetary teeth are respectively disposed on the first planetary gear and the second planetary gear.

According to the transmission mechanism described above, the first row of planetary teeth and the second row of planetary teeth are arranged on two sides of the supporting hole.

According to the transmission mechanism described above, the first flange comprises at least one planetary gearing accommodation portion. The at least one planetary gearing accommodation portion is disposed around a corresponding one of the at least one supporting hole to accommodate the second planetary gear.

According to the transmission mechanism described above, the first planetary gear and the second planetary gear are disposed at two ends of the planetary gear supporting portion.

According to the transmission mechanism described above, the first row of planetary teeth and the second row of planetary teeth are disposed on the same side of the first flange, and the second row of planetary teeth are closer to the first flange than the first row of planetary teeth. The first flange comprises an eccentric shaft accommodation portion penetrating the first flange. The eccentric shaft passes through the eccentric shaft accommodation portion such that the eccentric shaft external teeth are disposed on the same side of the first flange as the first row of planetary teeth and the second row of planetary teeth.

The transmission mechanism of this invention transmit power between the rotating shaft and the eccentric shaft via at least one planetary gearing device, and the at least one planetary gearing device, the rotating shaft and the eccentric shaft are provided with external teeth, so as to provide a large range of speed ratio while reduce the producing cost.

Other features, advantages and embodiments of the present invention may be elaborated or become apparent by considering the following specific embodiments, accompanying drawings and claims. Furthermore, it should be appreciated that the summary and the following specific embodiments are all exemplary, and are intended to provide a further explanation, but not to limit the scope of protection of the present invention. However, the specific embodiments and specific examples merely indicate preferred embodiments of the present invention. For those skilled in the art, various variations and modifications within the spirit and scope of the present invention will become apparent by the way of the specific embodiments.

These and other features and advantages of the present invention may be better understood by reading the following detailed description with reference to the accompanying drawings. In all the accompanying drawings, the same reference numerals represent the same parts, in the figures:.

Particular embodiments of the present invention are described below with reference to the accompanying drawings which constitute part of this description. It should be appreciated that although the terms, such as "left" and "right", and "outer" and "inner", indicating orientations are used in the present invention to describe various exemplary structural parts and elements in the present invention, these terms used herein are, in order to facilitate illustration, only determined based on the exemplary orientations as shown in the accompanying drawings. Since the embodiments disclosed in the present invention can be arranged in different directions, these terms indicating directions are only illustrative and should not be considered as limitations. In the following accompanying drawings, the same reference numerals are used for the same components.

In a transmission mechanism <NUM> in the present invention, a rotating shaft <NUM>, an outer wheel <NUM>, and a first flange <NUM> and a second flange <NUM> connected together can move in a relative motion, such that power is output via the transmission mechanism <NUM>, and the transmission mechanism <NUM> can achieve the purpose of speed reduction or speed increase. When the rotating shaft <NUM> serves as a power input component (i.e., connected to a driving component) and the transmission mechanism <NUM> needs to realize speed reduction, the outer wheel <NUM> may be fixed, and the first flange <NUM> and/or the second flange <NUM> serves as a power output component (i.e., connected to a driven component), or the first flange <NUM> and the second flange <NUM> are fixed, and the outer wheel <NUM> serves as a power output component. When the outer wheel <NUM> serves as a power input component and the transmission mechanism <NUM> needs to realize speed increase, the first flange <NUM> and the second flange <NUM> may be fixed, and the rotating shaft <NUM> serves as a power output component. When the first flange <NUM> and/or the second flange <NUM> serves as a power input component and the transmission mechanism <NUM> needs to realize speed increase, the outer wheel <NUM> may be fixed, and the rotating shaft <NUM> serves as a power output component. In order to facilitate description, an example in which the rotating shaft <NUM> serves as a power input component, the outer wheel <NUM> is fixed, and the second flange <NUM> serves as a power output component so as to realize speed reduction will be described below.

<FIG> is a perspective view of an embodiment of the transmission mechanism <NUM> according to the present invention as seen from right to left. <FIG> is a perspective view of the transmission mechanism <NUM> shown in <FIG> as seen from left to right. <FIG> is a cross-sectional view of the transmission mechanism shown in <FIG> to show more components in the transmission mechanism <NUM>. As shown in <FIG>, the transmission mechanism <NUM> comprises an outer wheel <NUM>, a first flange <NUM>, a second flange <NUM>, a first inner wheel <NUM>, a second inner wheel <NUM>, a connection and transfer component <NUM>, an auxiliary transfer component <NUM>, an eccentric shaft <NUM>, planetary gearing device <NUM>, <NUM>, <NUM>, and a rotating shaft <NUM>. The first inner wheel <NUM>, the second inner wheel <NUM>, the first flange <NUM> and the second flange <NUM> are disposed side by side, and are carried or supported by the outer wheel <NUM>. The first flange <NUM> and the second flange <NUM> are respectively arranged on two sides of the first inner wheel <NUM> and the second inner wheel <NUM>, and are rigidly connected together via the connection and transfer component <NUM>. The connection and transfer component <NUM> passes through the first flange <NUM>, the first inner wheel <NUM>, the second inner wheel <NUM> and the second flange <NUM> so as to hold the first inner wheel <NUM> and the second inner wheel <NUM> between the first flange <NUM> and the second flange <NUM>. The auxiliary transfer component <NUM> passes through the first inner wheel <NUM>, the second inner wheel <NUM> and the second flange <NUM>. The planetary gearing device <NUM>, <NUM>, <NUM> are disposed on the first flange <NUM>. The eccentric shaft <NUM> penetrates the first flange <NUM>, the second flange <NUM>, the first inner wheel <NUM> and the second inner wheel <NUM>, and can engage with the planetary gearing device <NUM>, <NUM>, <NUM>. The rotating shaft <NUM> is disposed on the right side of the eccentric shaft <NUM>, and also engages with the planetary gearing device <NUM>, <NUM>, <NUM>.

When the transmission mechanism <NUM> is in operation, the power transfer relationship thereof is substantially described as follows.

The rotating shaft <NUM> engages with the planetary gearing device <NUM>, <NUM>, <NUM> so as to drive the planetary gearing device <NUM>, <NUM>, <NUM> to rotate. The planetary gearing device <NUM>, <NUM>, <NUM> engage with the eccentric shaft <NUM> so as to drive the eccentric shaft <NUM> to rotate. The eccentric shaft <NUM> can drive the first inner wheel <NUM> and the second inner wheel <NUM> to rotate. The connection and transfer component <NUM> and the auxiliary transfer component <NUM> transfer the motion of the first inner wheel <NUM> and the second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM> to drive the first flange <NUM> and the second flange <NUM> to rotate. The first flange <NUM> and the second flange <NUM> are connected to a driven component (not shown) so as to achieve speed change and torque output.

The specific structure of each component in the transmission mechanism <NUM> will be described in detail below with reference to <FIG>.

<FIG> is a perspective view of the rotating shaft <NUM> of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is an axial cross-sectional view of the rotating shaft <NUM> shown in <FIG> to show the specific structure of the rotating shaft <NUM>. As shown in <FIG>, the rotating shaft <NUM> is substantially cylindrical and has a central axis X. The circumferential face of the left end of the rotating shaft <NUM> is provided with rotating shaft external teeth <NUM> for engaging with a first row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM> (see <FIG>). The rotating shaft <NUM> is internally provided with an internal accommodation portion <NUM> and a fastener receiving portion <NUM>. The internal accommodation portion <NUM> is formed by extending inward from the right side of the rotating shaft <NUM> and is used for receiving an output component of a driving component (e.g., a rotating shaft of a motor). The internal accommodation portion <NUM> also has a central axis X. The internal accommodation portion <NUM> is provided with a key slot <NUM> on one side to prevent the output end of the driving component from rotating around the central axis X relative to the rotating shaft <NUM>. The rotating shaft <NUM> is further internally provided with a fastener receiving portion <NUM> for receiving a fastener. The fastener receiving portion <NUM> is disposed perpendicular to the central axis X. After the output end of the driving component is inserted into the internal accommodation portion <NUM>, the fastener can be inserted into the fastener receiving portion <NUM> to abut against the output end of the driving component to prevent the output end of the driving component to move along the central axis X relative to the rotating shaft <NUM>.

<FIG> is a perspective view of the eccentric shaft <NUM> of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is an axial cross-sectional view of the eccentric shaft <NUM> shown in <FIG> to show the specific structure of the eccentric shaft <NUM>. As shown in <FIG>, the eccentric shaft <NUM> comprises an eccentric shaft body <NUM>, which is substantially cylindrical and has a central axis Y. The eccentric shaft <NUM> is provided with an eccentric shaft engaging portion <NUM> that is formed by extending outward along the radial direction of the eccentric shaft body <NUM>. The external circumferential surface of the eccentric shaft engaging portion <NUM> is provided with eccentric shaft external teeth <NUM> for engaging with the second row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM> (see <FIG>). The eccentric shaft <NUM> is further provided with a first eccentric portion <NUM> and a second eccentric portion <NUM> which are disposed on the left side of the eccentric shaft engaging portion <NUM>. The first eccentric portion <NUM> and the second eccentric portion <NUM> are symmetrically and eccentrically arranged with respect to the central axis Y and have the same eccentricity. Both the first eccentric portion <NUM> and the second eccentric portion <NUM> are a circular ring eccentrically disposed with respect to the central axis Y of the eccentric shaft <NUM>. The external circumferential face of the first eccentric portion <NUM> and the external circumferential face of the second eccentric portion <NUM> have the same diameter. More specifically, the first eccentric portion <NUM> and the second eccentric portion <NUM> respectively have a first inner wheel central axis N1 and a second inner wheel central axis N2. The first inner wheel central axis N1 and the second inner wheel central axis N2 have a distance e from the central axis Y of the eccentric shaft <NUM>. The distance e is greater than <NUM>. The first inner wheel central axis N1 and the second inner wheel central axis N2 are symmetrically arranged with respect to the central axis Y. That is, the first eccentric portion <NUM> and the second eccentric portion <NUM> have an axial phase difference of <NUM>°. When the eccentric shaft <NUM> rotates around the central axis Y thereof, the first inner wheel central axis N1 of the first eccentric portion <NUM> and the second inner wheel central axis N2 of the second eccentric portion <NUM> both rotate around the central axis Y.

The right end of the eccentric shaft body <NUM> extends beyond the first eccentric portion <NUM> along the central axis Y to form a first supporting portion <NUM> for abutting against the inner wall of the first flange bearing <NUM> (see <FIG>). Since the eccentric shaft engaging portion <NUM> extends radially beyond the first supporting portion <NUM>, it can restrict the first flange bearing <NUM> from axially moving to the left. The left end of the eccentric shaft body <NUM> extends beyond the second eccentric portion <NUM> along the central axis Y to form a second supporting portion <NUM> for abutting against the inner wall of the second flange bearing <NUM> (see <FIG>). Since the second eccentric portion <NUM> extends radially beyond the second supporting portion <NUM>, it can restrict the second flange bearing <NUM> from axially moving to the right.

Referring to <FIG>, the planetary gearing device <NUM>, the planetary gearing device <NUM> and the planetary gearing device <NUM> have the same structure, and are evenly disposed on the first flange <NUM>. For more brief description, the planetary gearing device <NUM> is taken as an example for structural description below with reference to <FIG>.

<FIG> is an exploded view of the planetary gearing device <NUM> of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is a cross-sectional view of the planetary gearing device <NUM> of the transmission mechanism shown in <FIG> to show the specific structure of the planetary gearing <NUM>. As shown in <FIG>, the planetary gearing device <NUM> comprises a first planetary gear <NUM>, a planetary gear supporting portion <NUM>, and a second planetary gear <NUM>. The first planetary gear <NUM>, the planetary gear supporting portion <NUM>, and the second planetary gear <NUM> have a central axis Z. The first planetary gear <NUM> is provided with a first row of planetary teeth <NUM> for engaging with the rotating shaft external teeth <NUM>. The second planetary gear <NUM> is provided with a second planetary gear <NUM> for engaging with the eccentric shaft external teeth <NUM>. The planetary gear supporting portion <NUM> is used for arrangement of the planetary gearing bearing <NUM> (see <FIG>). In the embodiment of the present invention, the second planetary gear <NUM> and the planetary gear supporting portion <NUM> are integrally formed. The right end of the planetary gear supporting portion <NUM> has a substantially rectangular connecting portion <NUM> for connecting with the first planetary gear <NUM>. The first planetary gear <NUM> is provided with a connecting and receiving portion <NUM>, which penetrates the second planetary gear <NUM> and is used to accommodate the connecting portion <NUM> to enable the first planetary gear <NUM> and the second planetary gear <NUM> to be connected together, such that the first planetary gear <NUM> and the second planetary gear <NUM> rotate together around the central axis Z.

It could be understood by those skilled in the art that, although the first planetary gear <NUM> is integrally formed with the planetary gear supporting portion <NUM> and is connected to the second planetary gear <NUM> in this embodiment, the first planetary gear <NUM> and the second planetary gear <NUM> can be connected together in any way, which fall within the scope of protection of the present invention.

<FIG> is a perspective view of the first flange <NUM> of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is a perspective view of the first flange <NUM> shown in <FIG> as seen from left to right. <FIG> is an axial cross-sectional view of the first flange <NUM> shown in <FIG>. Specifically, the first flange <NUM> comprises a first flange body <NUM> and a first flange projecting portion <NUM>. The first flange body <NUM> is substantially ring-shaped and has a central axis E. The first flange projecting portion <NUM> is disposed at the right portion of the first flange body <NUM>, and is formed by radially extending from the first flange body <NUM>. The first flange body <NUM> and the first flange projecting portion <NUM> form a step portion <NUM> used to receive balls in the first outer wheel bearing assembly <NUM> (see <FIG>) and restrict the first outer wheel bearing assembly <NUM> from axially moving to the right.

The first flange <NUM> is provided with an eccentric shaft accommodation portion <NUM> that transversely penetrates the first flange <NUM> to accommodate the eccentric shaft <NUM>. Specifically, the size of the left portion of the eccentric shaft accommodation portion <NUM> is greater than the size of the right portion of the eccentric shaft accommodation portion <NUM>, such that the left portion of the eccentric shaft accommodation portion <NUM> can accommodate the eccentric shaft external teeth <NUM> on the eccentric shaft <NUM>, and the right portion of the eccentric shaft accommodation portion <NUM> can accommodate the first supporting portion <NUM> of the eccentric shaft <NUM> and the first flange bearing <NUM> that is sheathed over the first supporting portion <NUM> (see <FIG>). More specifically, the right portion of the eccentric shaft accommodation portion <NUM> has an inner wall <NUM> for contacting with the outer wall of the first flange bearing <NUM>.

The first flange <NUM> is further provided with three supporting holes <NUM> that transversely penetrate the first flange <NUM>. The three supporting holes <NUM> are evenly disposed in the circumferential direction of the first flange <NUM>. The first flange <NUM> is further provided with three planetary gearing accommodation portions <NUM>. Each of the three planetary gearing accommodation portions <NUM> is disposed around a corresponding one of the three supporting holes <NUM>. The right portion of the planetary gearing accommodation portion <NUM> can accommodate the planetary gear supporting portion <NUM> and the planetary gearing bearing <NUM> that is sheathed over the planetary gear supporting portion <NUM>, and the planetary gearing accommodation portion <NUM> is used for accommodating the second planetary gear <NUM> when the planetary gearing device <NUM>, <NUM>, <NUM> and the eccentric shaft <NUM> are disposed in place, the second row of planetary teeth <NUM> on the second planetary gear <NUM> can engage with the eccentric shaft external teeth <NUM> on the eccentric shaft <NUM>.

The first flange <NUM> is further provided with nine connection and transfer component mounting portions <NUM> that transversely penetrate the first flange <NUM>. Each group of three connection and transfer component mounting portions <NUM> are evenly disposed between two planetary gearing accommodation portions <NUM>. The nine connection and transfer component mounting holes <NUM> are all counterbored holes used to receive the connection and transfer components <NUM> (see <FIG>).

<FIG> is a perspective view of the second flange <NUM> of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is a perspective view of the second flange <NUM> shown in <FIG> as seen from left to right. <FIG> is an axial cross-sectional view of the second flange <NUM> shown in <FIG>. Specifically, the second flange <NUM> comprises a second flange body <NUM> and a second flange projecting portion <NUM>. The second flange body <NUM> is substantially ring-shaped and has a central axis F. The second flange projecting portion <NUM> is disposed at the left portion of the second flange body <NUM>, and is formed by radially extending from the second flange body <NUM>. The second flange body <NUM> and second flange projecting portion <NUM> form a step portion <NUM> used to receive balls in the second outer wheel bearing assembly <NUM> (see <FIG>) and restrict the second outer wheel bearing assembly <NUM> from axially moving to the left.

The second flange <NUM> is provided with an internal accommodation cavity <NUM> that transversely penetrates the second flange body <NUM> to accommodate the second supporting portion <NUM>. The inner wall of the internal accommodation cavity <NUM> is provided with a radially extending groove <NUM>. The inner wall <NUM> of the right side of the groove <NUM> is used for receiving the second flange bearing <NUM> (see <FIG>), and the groove <NUM> is used for mounting a stop sheet <NUM> (see <FIG>) to restrict the second flange bearing <NUM> from axially moving to the left.

The second flange <NUM> is further provided with nine connection and transfer component mounting portions <NUM> and three auxiliary transfer component mounting portions <NUM>, which are evenly arranged in the circumferential direction of the second flange <NUM> and are respectively used for receiving nine connection and transfer components <NUM> and three auxiliary transfer components <NUM> (see <FIG>). Each of the nine connection and transfer component mounting portions <NUM> is provided with a screw thread to fit with the screw thread on one end of the connection and transfer component <NUM> such that the second flange <NUM> can be connected to the connection and transfer component <NUM>. As shown in <FIG> and <FIG>, the transmission mechanism <NUM> in this embodiment is provided with nine connection and transfer components <NUM>. Each of the connection and transfer components <NUM> has the same structure, and is used to connect the first flange <NUM> and the second flange <NUM> together and transfer the power from the first inner wheel <NUM> and the second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM>.

<FIG> is a perspective view of the connection and transfer component <NUM> of the transmission mechanism <NUM> shown in <FIG>. <FIG> is an axial cross-sectional view of the connection and transfer component <NUM> shown in <FIG>. As shown in <FIG>, the connection and transfer component <NUM> comprises a pin <NUM>, a sleeve <NUM>, and a fastener <NUM>. In this embodiment, the fastener <NUM> is a nut. The pin <NUM> is substantially cylindrical, with the diameter thereof being larger at the middle portion and smaller at two ends. The sleeve <NUM> is sheathed over the middle portion of the pin <NUM> with the larger diameter. The middle portion of the pin <NUM> and the sleeve <NUM> are accommodated in the inner wheel through-holes <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM> (see <FIG>) to transfer the power from the first inner wheel <NUM> and the second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM>. The sleeve <NUM> is used for protecting the pin <NUM> from wear. The two ends of the pin <NUM> with the smaller diameter are provided with screw threads. The screw thread at the left end of the pin <NUM> can fit with the screw thread in the connection and transfer component mounting portion <NUM> such that the pin <NUM> is connected to the second flange <NUM>. The screw thread at the right end of the pin <NUM> can fit with the screw thread in the fastener <NUM> to enable the pin <NUM> to be connected to the first flange <NUM>.

As shown in <FIG> and <FIG>, three auxiliary transfer components <NUM> are provided in the transmission mechanism <NUM> according to this embodiment. Each of the auxiliary transfer components <NUM> has the same structure, and is used for transferring the power from the first inner wheel <NUM> and the second inner wheel <NUM> to the second flange <NUM>. Since the first flange <NUM> and the second flange <NUM> are connected together, the auxiliary transfer component <NUM> can transfer the power from the first inner wheel <NUM> and second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM>.

<FIG> is a perspective view of the auxiliary transfer component <NUM> of the transmission mechanism <NUM> shown in <FIG>. <FIG> is an axial cross-sectional view of the auxiliary transfer component <NUM> shown in <FIG>. As shown in <FIG>, the auxiliary transfer component <NUM> comprises a pin <NUM> and a sleeve <NUM>. The pin <NUM> is substantially cylindrical, with the diameter thereof being larger at the right portion and smaller at the left portion. The left portion of the pin <NUM> is accommodated in the auxiliary transfer component mounting portion <NUM> on the second flange <NUM> so as to fit with the second flange <NUM>. The sleeve <NUM> is sheathed over the right portion of the pin <NUM> with the larger diameter. The right portion of the pin <NUM> and the sleeve <NUM> are accommodated in the inner wheel through-holes <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM> (see <FIG>) to transfer the power from the first inner wheel <NUM> and the second inner wheel <NUM> to the second flange <NUM>. The sleeve <NUM> is used to protect the pin <NUM> from wear.

As shown in <FIG> and <FIG>, a first inner wheel <NUM> and a second inner wheel <NUM> are provided in the transmission mechanism <NUM> according to this embodiment. In this embodiment, the first inner wheel <NUM> and the second inner wheel <NUM> have the same structure, and are used for transferring the power from the eccentric shaft <NUM> to the connection and transfer component <NUM> and the auxiliary transfer component <NUM>.

<FIG> is a perspective view of the first inner wheel <NUM> and the second inner wheel <NUM> of the transmission mechanism <NUM> shown in <FIG>. As shown in <FIG>, the first inner wheel <NUM> and the second inner wheel <NUM> are substantially ring-shaped and have a certain thickness. The first inner wheel <NUM> and the second inner wheel <NUM> respectively have central axes N1 and N2. The first inner wheel <NUM> and the second inner wheel <NUM> are further provided therein with an accommodation portion <NUM> that radially penetrates the first inner wheel <NUM> and the second inner wheel <NUM>. The diameter of the wall <NUM> of the accommodation portion <NUM> is substantially the same as the outer diameters of inner wheel bearings <NUM>, <NUM> (see <FIG>), such that the first inner wheel <NUM> and the second inner wheel <NUM> can be sheathed over the inner wheel bearings <NUM>, <NUM> arranged around the eccentric portions <NUM>, <NUM>. When the eccentric shaft <NUM> rotates, the eccentric portions <NUM>, <NUM> of the eccentric shaft <NUM> can drive the eccentric rotation of the first inner wheel <NUM> and the second inner wheel <NUM> via the inner wheel bearings <NUM>, <NUM>. In other words, when the eccentric shaft <NUM> rotates, the eccentric shaft <NUM> enables the central axes N1, N2 of the first inner wheel <NUM> and the second inner wheel <NUM> to rotate around the central axis Y of the eccentric shaft <NUM> (i.e., the first inner wheel <NUM> and the second inner wheel <NUM> can rotate along a circular path around the central axis Y of the eccentric shaft <NUM>). The periphery of the first inner wheel <NUM> and the second inner wheel <NUM> is provided with inner wheel external teeth <NUM>. The inner wheel external teeth <NUM> is configured to engage with the outer wheel internal teeth <NUM> of the outer wheel <NUM> (see <FIG> and <FIG>). More specifically, when the first inner wheel <NUM> and the second inner wheel <NUM> move, at least some of the inner wheel external teeth <NUM> can engage with the outer wheel internal teeth <NUM> of the outer wheel <NUM>. There is a difference in the number of teeth between the inner wheel external teeth <NUM> and the outer wheel internal teeth <NUM>. The number of the outer wheel internal teeth <NUM> is greater than the number of the inner wheel external teeth <NUM> (i.e., the difference in the number of teeth is an integer greater than zero). When the first inner wheel <NUM> and the second inner wheel <NUM> are driven by the eccentric shaft <NUM> to eccentrically rotates in the outer wheel <NUM>, the engagement of the inner wheel external teeth <NUM> and the outer wheel internal teeth <NUM> enables the first inner wheel <NUM> and the second inner wheel <NUM> to rotate (i.e., rotating on their own axes). In this way, the eccentric shaft <NUM> enables the first inner wheel <NUM> and the second inner wheel <NUM> to rotate in the outer wheel <NUM> along a circular path and rotate on their own axes.

The first inner wheel <NUM> and the second inner wheel <NUM> further comprise twelve inner wheel through-holes <NUM>, which are evenly arranged around the central axes N1, N2 in the circumferential direction and are used to accommodate the connection and transfer components <NUM> and the auxiliary transfer components <NUM>. Since the outer diameter of the sleeve <NUM> of the connection and transfer component <NUM> is the same size as the outer diameter of the sleeve <NUM> of the auxiliary transfer component <NUM>, the twelve inner wheel through-holes <NUM> have the same size. A gap is provided between the wall of the inner wheel through-hole <NUM> and the periphery of the sleeve <NUM> and of the sleeve <NUM>, and is configured such that when the first inner wheel <NUM> and the second inner wheel <NUM> eccentrically rotate, the first flange <NUM> and the second flange <NUM> can be driven to rotate together via the connection and transfer component <NUM> and the auxiliary transfer component <NUM>.

<FIG> is a perspective view of the outer wheel <NUM> of the transmission mechanism <NUM> shown in <FIG>. <FIG> is an axial cross-sectional view of the outer wheel <NUM> shown in <FIG>. As shown in <FIG> and <FIG>, the outer wheel <NUM> is substantially ring-shaped and has an outer wheel central axis O. The outer wheel <NUM> has an accommodation portion <NUM>, and the accommodation portion <NUM> penetrates the outer wheel <NUM>. The middle portion of the wall of the accommodation portion <NUM> is provided with outer wheel internal teeth <NUM> that can engage with the inner wheel external teeth <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM>.

The outer wheel <NUM> is further provided with a first supporting portion <NUM> and a second supporting portion <NUM>, which are respectively disposed on the left and right sides of the outer wheel internal teeth <NUM>. The first supporting portion <NUM> is used to support the first outer wheel bearing assembly <NUM>, and the second supporting portion <NUM> is used to support the second outer wheel bearing assembly <NUM> (see <FIG>).

<FIG> is a side view of the transmission mechanism <NUM> shown in <FIG> as seen from right to left. <FIG> is a cross-sectional view of the transmission mechanism shown in <FIG> along line A-A in <FIG> to show the relationship of relative position and the fitting relationship of the components in the transmission mechanism <NUM>. The rotating shaft <NUM>, the eccentric shaft <NUM>, the first flange <NUM> and the second flange <NUM> are disposed coaxially with the outer wheel <NUM>. The first eccentric portion <NUM> of the eccentric shaft <NUM> is provided with a first inner wheel bearing <NUM>. The second eccentric portion <NUM> of the eccentric shaft <NUM> is provided with a second inner wheel bearing <NUM>. Specifically, the inner wall of the first inner wheel bearing <NUM> is in contact with the external circumferential face of the first eccentric portion <NUM>, and the outer wall of the first inner wheel bearing <NUM> is in contact with the wall <NUM> of the accommodation portion <NUM> of the first inner wheel <NUM>, such that the first inner wheel <NUM> is sheathed over the first eccentric portion <NUM>. When the eccentric shaft <NUM> rotates around the central axis O, the first inner wheel <NUM> can rotate along a circular path around the central axis O, that is, the first inner wheel central axis N1 of the first inner wheel <NUM> rotates (i.e., translates) around the central axis O. The inner wall of the second inner wheel bearing <NUM> is in contact with the external circumferential face of the second eccentric portion <NUM>, and the outer wall of the second inner wheel bearing <NUM> is in contact with the wall <NUM> of the accommodation portion <NUM> of the second inner wheel <NUM>, such that the second inner wheel <NUM> is sheathed over the second eccentric portion <NUM>. When the eccentric shaft <NUM> rotates around the central axis O, the second inner wheel <NUM> rotates along a circular path around the central axis O, that is, the second inner wheel central axis N2 of the second inner wheel <NUM> rotates (i.e., translates) around the central axis O.

Since the first inner wheel <NUM> and the second inner wheel <NUM> have the same structure, and the first inner wheel <NUM> and the second inner wheel <NUM> are symmetrically and eccentrically arranged relative to the central axis O, when the eccentric shaft <NUM> drives the first inner wheel <NUM> and the second inner wheel <NUM> to rotate, the first inner wheel <NUM> and the second inner wheel <NUM> always have a phase difference of <NUM>°, thereby ensuring the first inner wheel <NUM> and the second inner wheel <NUM> to maintain a dynamic balance as a whole during movement.

Furthermore, the first inner wheel <NUM> and the second inner wheel <NUM> both engage with the outer wheel <NUM>. Specifically, when the eccentric shaft <NUM> drives the first inner wheel <NUM> and the second inner wheel <NUM> to rotate along a circular path, since there is a difference in the number of teeth between the inner wheel external teeth <NUM> and the outer wheel internal teeth <NUM>, and the outer wheel <NUM> is fixed, the first inner wheel <NUM> and the second inner wheel <NUM> can rotate around their respective central axes (i.e., the first inner wheel central axis N1 and the second inner wheel central axis N2). That is, the first inner wheel <NUM> and the second inner wheel <NUM> rotate on their own axes while rotating along a circular path (i.e., eccentric rotation).

The first flange <NUM> and the second flange <NUM> are respectively disposed on two sides of the first inner wheel <NUM> and the second inner wheel <NUM>, and the first flange <NUM> and the second flange <NUM> are connected together via the connection and transfer component <NUM>. The first inner wheel <NUM> and the second inner wheel <NUM> drive the first flange <NUM> and the second flange <NUM> to rotate via the connection and transfer component <NUM>. The first flange <NUM> is disposed on the right side of the inner wheel <NUM>, and the second flange <NUM> is disposed on the left side of the inner wheel <NUM>.

Specifically, the first flange <NUM> is sheathed over the eccentric shaft <NUM> via the first flange bearing <NUM>, and is disposed in the outer wheel <NUM> via the first outer wheel bearing assembly <NUM>. The inner wall of the first flange bearing <NUM> is in contact with the first supporting portion <NUM>, and the outer wall of the first flange bearing <NUM> is in contact with the inner wall <NUM> of the eccentric shaft accommodation portion <NUM> of the first flange <NUM>. The balls in the first outer wheel bearing assembly <NUM> abut against the step portion <NUM> of the first flange <NUM>, and the outer wall of the first outer wheel bearing assembly <NUM> is contact with the first supporting portion <NUM> of the outer wheel <NUM>.

Similarly, the second flange <NUM> is sheathed over the eccentric shaft <NUM> via the second flange bearing <NUM>, and is disposed in the outer wheel <NUM> via the second outer wheel bearing assembly <NUM>. The inner wall of the second flange bearing <NUM> is in contact with the second supporting portion <NUM>, and the outer wall of the second flange bearing <NUM> is in contact with the inner wall <NUM> of the second flange body <NUM>. The balls in the second outer wheel bearing assembly <NUM> abut against the step portion <NUM> of the second flange <NUM>, and the outer wall of the second outer wheel bearing assembly <NUM> is in contact with the second supporting portion <NUM> of the outer wheel <NUM>, such that the second flange <NUM> is mounted on the outer wheel <NUM> via the second outer wheel bearing assembly <NUM>.

Thus, both the first flange <NUM> and the second flange <NUM> can rotate around the central axis O relative to the outer wheel <NUM>.

The first flange <NUM> and the second flange <NUM> are connected to each other via the pin <NUM> and the fastener <NUM> in the connection and transfer component <NUM>, and the first inner wheel <NUM> and the second inner wheel <NUM> drive, via the connection and transfer component <NUM>, the first flange <NUM> and the second flange <NUM> to rotate around the central axis O. Specifically, the screw thread at the left end of the pin <NUM> is fit with the screw thread in the connection and transfer component mounting portion <NUM> on the second flange <NUM>, such that the pin <NUM> is connected to the second flange <NUM>. The right end of the pin <NUM> passes through the connection and transfer component mounting hole <NUM> in the first flange <NUM> from the left side of the first flange <NUM>, and then the fastener <NUM> is sheathed over the right end of the pin <NUM> from the right side of the first flange <NUM>. The screw thread on the fastener <NUM> fits with the screw thread at the right end of the pin <NUM>, such that the first flange <NUM> and the second flange <NUM> are connected together.

Each of the planetary gearing device <NUM>, <NUM>, <NUM> is supported on the first flange <NUM>. Specifically, a planetary gearing bearing <NUM> is sheathed over the planetary gear supporting portion <NUM> of each of the planetary gearing device <NUM>, <NUM>, <NUM>, and passes through the supporting hole <NUM> in the first flange <NUM> from the left side and then extends out of the right side of the first flange <NUM>. The left end of the planetary gear supporting portion <NUM> is connected to the second planetary gear <NUM>, and the right end of the planetary gear supporting portion <NUM> is connected to the first planetary gear <NUM>, such that the three planetary gearing device <NUM>, <NUM>, <NUM> are rotatably supported on the first flange <NUM>. The second row of planetary teeth <NUM> on the second planetary gears <NUM> of the three planetary gearing device <NUM>, <NUM>, <NUM> engage with the eccentric shaft external teeth <NUM> of the eccentric shaft <NUM>, such that the three planetary gearing device <NUM>, <NUM>, <NUM> can drive the eccentric shaft <NUM> to rotate.

The rotating shaft <NUM> is disposed on the right side of the first flange <NUM>, and is disposed among the three planetary gearing device <NUM>, <NUM>, <NUM>. The right end of the rotating shaft <NUM> is configured to be connected to the driving component (not shown) to enable the rotating shaft <NUM> to rotate. The rotating shaft external teeth <NUM> at the left end of the rotating shaft <NUM> engage with the first row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM>, such that the rotating shaft <NUM> can drive the three planetary gearing device <NUM>, <NUM>, <NUM> to rotate.

Furthermore, the first inner wheel <NUM> and the second inner wheel <NUM> can also drive, via the auxiliary transfer component <NUM>, the second flange <NUM> to rotate around the central axis O. Specifically, the left portion of the pin <NUM> of the auxiliary transfer component <NUM> is accommodated in the auxiliary transfer component mounting portion <NUM> on the second flange <NUM>, and the right portion of the pin <NUM> and the sleeve <NUM> are accommodated in the inner wheel through-holes <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM>, such that when the first inner wheel <NUM> and the second inner wheel <NUM> rotate, the second flange <NUM> can be driven to rotate via the auxiliary transfer component <NUM>.

The process of transfer of torque/power during operation of the transmission mechanism <NUM> will be described below in detail, taking an example in which the outer wheel <NUM> is fixed (i.e., the outer wheel <NUM> does not translate or rotate), the first flange <NUM> and/or the second flange <NUM> serves as an output component, and the rotating shaft <NUM> serves as an input component.

A driving component (e.g., a motor, not shown) drives the rotating shaft <NUM> to rotate around the central axis O. The rotating shaft external teeth <NUM> of the rotating shaft <NUM> engage with the first row of planetary teeth <NUM> of the three planetary gearing device <NUM>, <NUM>, <NUM>, such that the three planetary gearing device <NUM>, <NUM>, <NUM> can rotate around the respective central axes (i.e., rotate on their own axes). Since the second row of planetary teeth <NUM> of the three planetary gearing device <NUM>, <NUM>, <NUM> engage with the eccentric shaft external teeth <NUM> of the eccentric shaft <NUM>, the rotation of the three planetary gearing device <NUM>, <NUM>, <NUM> will drive the eccentric shaft <NUM> to rotate around the central axis O. The eccentric shaft <NUM> drives, via the first eccentric portion <NUM> and the second eccentric portion <NUM>, the first inner wheel <NUM> and the second inner wheel <NUM> to rotate along a circular path (i.e., the first inner wheel central axis N1 and the second inner wheel central axis N2 rotate around the central axis O). The inner wheel external teeth <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM> engage with the outer wheel internal teeth <NUM> of the outer wheel <NUM>, such that the first inner wheel <NUM> and the second inner wheel <NUM> rotate on their own axes (i.e., the first inner wheel <NUM> and the second inner wheel <NUM> can rotate around their respective central axes N1, N2). In this way, the first inner wheel <NUM> and the second inner wheel <NUM> can rotate on their own axes while rotating along a circular path.

When the first inner wheel <NUM> and the second inner wheel <NUM> rotate along a circular path and rotate on their own axes, by means of the connection and transfer component <NUM> (including the pin <NUM> and the sleeve <NUM>) and the auxiliary transfer component <NUM> fitting with the inner wheel through-holes <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM>, the connection and transfer component <NUM> and the auxiliary transfer component <NUM> transfers the rotating of the first inner wheel <NUM> and the second inner wheel <NUM> on their own axes to the first flange <NUM> and the second flange <NUM>, such that the first flange <NUM> and the second flange <NUM> rotate around the central axis O. The first flange <NUM> and/or the second flange <NUM> may be connected to a driven device (not shown). Thus, the torque of the driving mechanism can be output to the driven device via the transmission mechanism <NUM>.

It should be noted that when the outer wheel <NUM> is fixed (i.e., the outer wheel <NUM> does not translate and rotate), when the first flange <NUM> and/or the second flange <NUM> serves as an output component while the rotating shaft <NUM> serves as an input component, since the three planetary gearing device <NUM>, <NUM>, <NUM> are rotatably supported on the first flange <NUM> via the supporting holes <NUM>, the rotation of the first flange <NUM> also drives the three planetary gearing device <NUM>, <NUM>, <NUM> to rotate along a circular path (i.e., the three planetary gearing device <NUM>, <NUM>, <NUM> can rotate around the central axis O). However, the rotation of the three planetary gearing device <NUM>, <NUM>, <NUM> along a circular path will not prevent the second row of planetary teeth <NUM> of the three planetary gearing device <NUM>, <NUM>, <NUM> from driving the eccentric shaft <NUM> to rotate.

It should be noted that, since the first flange <NUM> and the second flange <NUM> are mounted on the outer wheel <NUM> via the first outer wheel bearing assembly <NUM> and the second outer wheel bearing assembly <NUM>, the first flange <NUM> and the second flange <NUM> can only rotate around the central axis O. Thus, when power is transferred from the first inner wheel <NUM> and the second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM>, only the rotation of the first inner wheel <NUM> and the second inner wheel <NUM> on their own axes is transferred to the first flange <NUM> and the second flange <NUM>, and the rotation of the first inner wheel <NUM> and the second inner wheel <NUM> along a circular path cannot be transferred to the first flange <NUM> and the second flange <NUM>.

In this embodiment, when the first row of planetary teeth <NUM> and the rotating shaft external teeth <NUM> have a first difference in the number of teeth, the second row of planetary teeth <NUM> and the eccentric shaft external teeth <NUM> have a second difference in the number of teeth, and the inner wheel external teeth <NUM> and the outer wheel internal teeth <NUM> have a third difference in the number of teeth, the transmission mechanism <NUM> can achieve three-stage speed change. Specifically, the three-stage speed change includes a first-stage speed change, a second-stage speed change, and a third-stage speed change. The first-stage speed change is achieved by the rotating shaft external teeth <NUM> of the rotating shaft <NUM> and the first row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM>, with a speed ratio of i<NUM>. The second-stage speed change is achieved by the second row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM> and the eccentric shaft external teeth <NUM> of the eccentric shaft <NUM>, with a speed ratio of i<NUM>. The third-stage speed change is achieved by transfer from the first inner wheel <NUM> and the second inner wheel <NUM> to the first flange <NUM> and the second flange <NUM>, with a speed ratio of i<NUM>. Specifically, the number of teeth of the rotating shaft external teeth <NUM> of the rotating shaft <NUM> is Za, the number of teeth of the first row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM> is Zb1, the number of teeth of the second row of planetary teeth <NUM> of the planetary gearing device <NUM>, <NUM>, <NUM> is Zb2, the number of teeth of the eccentric shaft external teeth <NUM> of the eccentric shaft <NUM> is Zc, the number of teeth of the inner wheel external teeth <NUM> of the first inner wheel <NUM> and the second inner wheel <NUM> is Zd, and the number of teeth of the outer wheel internal teeth <NUM> of the outer wheel <NUM> is Ze. The first-stage speed ratio i<NUM> satisfied: <MAT>.

The second-stage speed ratio i<NUM> satisfies: <MAT>.

The third-stage speed ratio i<NUM> satisfies: <MAT>.

Thus, the total speed ratio I satisfies: <MAT>.

As described in the present invention, the transmission mechanism <NUM> of the present invention has four transmission modes as follows: (<NUM>) when the transmission mechanism <NUM> needs to achieve speed reduction, the outer wheel <NUM> is fixed, the rotating shaft <NUM> serves as a power input component, and the first flange <NUM> and/or the second flange <NUM> serves as a power output component; (<NUM>) when the transmission mechanism <NUM> needs to achieve speed reduction, the first flange <NUM> and the second flange <NUM> are fixed, the rotating shaft <NUM> serves as a power input component, and the outer wheel <NUM> serves as a power output component; (<NUM>) when the transmission mechanism <NUM> needs to achieve speed increase, the outer wheel <NUM> is fixed, the first flange <NUM> and/or the second flange <NUM> serve as a power input component, and the rotating shaft <NUM> serves as a power output component; and (<NUM>) when the transmission mechanism <NUM> needs to achieve speed increase, the first flange <NUM> and the second flange <NUM> are fixed, the outer wheel <NUM> serves as a power input component, and the rotating shaft <NUM> serves as a power output component. The stages of speed ratio and the total speed ratio in the first transmission mode are expressed above. Similarly, the stages of speed ratio and the total speed ratio in the other three transmission modes may also be calculated.

in the above second transmission mode (i.e., when the transmission mechanism <NUM> needs to achieve speed reduction, the first flange <NUM> and the second flange <NUM> are fixed, the rotating shaft <NUM> serves as a power input component, and the outer wheel <NUM> serves as a power output component), the first-stage speed ratio k<NUM> and the second-stage speed ratio k<NUM> are the same as the first-stage speed ratio i<NUM> and the second-stage speed ratio i<NUM> in the first transmission mode. However, in the second transmission mode, since the first flange <NUM> and the second flange <NUM> are fixed, the planetary gearing device <NUM>, <NUM>, <NUM> in the second transmission mode will not rotate along a circular path, and therefore the third-stage speed ratio k<NUM> in the second transmission mode satisfies: <MAT>.

Thus, the total speed ratio K of the transmission mechanism <NUM> satisfies: <MAT>.

In the above third transmission mode (i.e., when the transmission mechanism <NUM> needs to achieve speed increase, the outer wheel <NUM> is fixed, the first flange <NUM> and/or the second flange <NUM> serve as a power input component, and the rotating shaft <NUM> serves as a power output component), based on the order of transmission in the first transmission mode, it would have been readily appreciated by those skilled in the art that the order of transmission in the third transmission mode is in the reverse order of transmission in the first mode, so the order of transmission will not be described in detail. The three-stage transmission may also be achieved, and the total transmission ratio m satisfies: <MAT>.

Similarly, in the above fourth transmission mode (i.e., when the transmission mechanism <NUM> needs to achieve speed increase, the first flange <NUM> and the second flange <NUM> are fixed, the outer wheel <NUM> serves as a power input component, and the rotating shaft <NUM> serves as a power output component), based on the order of transmission in the second transmission mode, it would have been readily appreciated by those skilled in the art that the order of transmission in the fourth transmission mode is in the reverse order of transmission in the second mode, so the order of transmission will not be described in detail. The three-stage transmission may also be achieved, and the total transmission ratio n satisfies: <MAT>.

It should be noted that, when the total speed ratio is calculated as a positive number, it is indicated that the direction of rotation of the output component is the same as the direction of rotation of the input component. When the total speed ratio is calculated as a negative number, it is indicated that the direction of rotation of the output component is in opposite direction of rotation of the input component.

In a conventional transmission mechanism, one end of the rotating shaft needs to be disposed in the eccentric shaft. Rotating shaft external teeth are provided on the rotating shaft, and eccentric shaft internal teeth are provided in the eccentric shaft, such that the rotating shaft can engage with the eccentric shaft so as to drive the eccentric shaft to rotate. In such an arrangement, it is necessary to provide an accommodation cavity in the eccentric shaft for accommodating the rotating shaft and to provide eccentric shaft internal teeth, which requires a larger space, resulting in a larger overall size of the transmission mechanism. Furthermore, since it is more difficult for the machine to machining the internal teeth than the external teeth, the machining efficiency is low. For example, for a component with a diameter of <NUM>, if the external teeth are machined, it only needs to take <NUM>-<NUM> minutes, but if the internal teeth are machined, it needs to take at least <NUM> hour.

Compared with the conventional transmission mechanism, the transmission mechanism <NUM> of the present invention at least has the following beneficial effects:
Firstly, the transmission mechanism <NUM> of the present invention requires short machining time, and has a low manufacturing cost. Specifically, the transmission mechanism <NUM> of the present invention achieves the transmission between the rotating shaft <NUM> and the eccentric shaft <NUM> by means of providing the planetary gearing device <NUM>, <NUM>, <NUM> on the first flange <NUM>. More specifically, in the transmission mechanism <NUM> of the present invention, the rotating shaft <NUM>, the planetary gearing device <NUM>, <NUM>, <NUM> and the eccentric shaft <NUM> are all provided with external teeth, and the transmission is achieved by means of the engaging of the external teeth. Since the external teeth have good machinability and require short machining time, the transmission mechanism <NUM> of the present invention has short machining time and a low manufacturing cost.

Secondly, the transmission mechanism <NUM> of the present invention can achieve a larger transmission ratio. Specifically, in the transmission mechanism <NUM> of the present invention, the planetary gearing device <NUM>, <NUM>, <NUM> are provided with a first row of planetary teeth <NUM> and a second row of planetary teeth <NUM>, such that the transmission mechanism <NUM> achieves three-stage speed change. Taking the first transmission mode as an example, when Za = <NUM>, Zb1 = <NUM>, Zb2 = <NUM>, Zc = <NUM>, Zd = <NUM> and Ze = <NUM>, the transmission mechanism <NUM> of the present invention can achieve the total transmission ratio I = -<NUM>. However, the conventional transmission mechanism can generally achieve a transmission ratio less than <NUM>.

It could be understood by those skilled in the art that, although the above embodiment comprises three planetary gearing device <NUM>, <NUM>, <NUM>, the number of planetary gearing device is not limited to three, and even at least one planetary gearing device falls within the scope of protection of the present invention.

It could also be understood by those skilled in the art that the number of inner wheels is not limited to two as shown in the embodiment of the present invention, and a plurality of inner wheels are configured to be able to maintain a dynamic balance as a whole during the high-speed eccentric rotation.

Although in this embodiment nine connection and transfer components <NUM> are provided and accordingly the first flange <NUM> and the second flange <NUM> are respectively provided with nine connection and transfer components mounting holes <NUM> and nine connection and transfer components mounting holes <NUM>, it could be understood by those skilled in the art that the transmission mechanism <NUM> is provided with at least two connection and transfer components <NUM>, and the first flange <NUM> and the second flange <NUM> are respectively provided with a corresponding number of connection and transfer component mounting holes <NUM> and connection and transfer component mounting holes <NUM>.

Although in this embodiment the connection and transfer component mounting holes <NUM> are counterbored holes and the connection and transfer component mounting holes <NUM> are blind holes, it could be understood by those skilled in the art that they may be through-holes or in other forms, as long as they can fit with the connection and transfer components <NUM>.

Although in this embodiment the connection and transfer component <NUM> comprises a pin <NUM>, a sleeve <NUM> and a fastener <NUM>, it could be understood by those skilled in the art that it only needs that they can fit with the first inner wheel <NUM>, the second inner wheel <NUM> and the second flange <NUM>.

It could also be understood by those skilled in the art that although the auxiliary transfer component <NUM> is provided in this embodiment, the auxiliary transfer component <NUM> may not be provided in other embodiments.

It could also be understood by those skilled in the art that although in this embodiment the rotating shaft <NUM> is disposed on the right side of the first flange <NUM> and engages with the planetary gearing device <NUM>, <NUM>, <NUM>, in other embodiments, when the power input component is disposed on the left side of the transmission mechanism <NUM>, the rotating shaft <NUM> may also penetrate the internal accommodation cavity of the eccentric shaft <NUM>, enable the left portion of the rotating shaft <NUM> to be connected to the power input component, and enable the rotating shaft external teeth <NUM> of the right portion to engage with the planetary gearing device <NUM>, <NUM>, <NUM>.

<FIG> shows an axial cross-sectional view of another embodiment of the transmission mechanism according to the present invention. The transmission mechanism <NUM> shown in <FIG> is substantially the same as the transmission mechanism <NUM> shown in <FIG>. For the brief expression, the same part will not be described in detail. The difference is that in the transmission mechanism <NUM>, the first planetary gear <NUM> and the second planetary gear <NUM> in the planetary gearing device <NUM>, <NUM>, <NUM> are disposed at two ends of the planetary gear supporting portion <NUM> (i.e., the first planetary gear <NUM> and the second planetary gear <NUM> are disposed on two sides of the first flange <NUM>), and accordingly, the eccentric shaft engaging portion <NUM> and the first supporting portion <NUM> on the eccentric shaft <NUM> are sequentially disposed on the right side of the first eccentric portion <NUM>. However, in the transmission mechanism <NUM> shown in <FIG>, the first planetary gear <NUM> and the second planetary gear <NUM> in the planetary gearing device <NUM>,<NUM>,<NUM> are disposed on the right side of the planetary gear supporting portion <NUM> (i.e., the first planetary gear <NUM> and the second planetary gear <NUM> are disposed on the same side of the first flange <NUM>). The first planetary gear <NUM> and the second planetary gear <NUM> can rotate together, and are supported on the first flange <NUM> via the planetary gear supporting portion <NUM>. The second planetary gear <NUM> is disposed closer to the first flange <NUM> than the first planetary gear <NUM>. The first row of planetary teeth <NUM> on the first planetary gear <NUM> can engage with the rotating shaft external teeth <NUM>. Also, accordingly, the first supporting portion <NUM> and the eccentric shaft engaging portion <NUM> on the eccentric shaft <NUM> are sequentially disposed on the right side of the first eccentric portion <NUM>. The first supporting portion <NUM> is sheathed with a first flange bearing assembly <NUM>, such that the eccentric shaft <NUM> is disposed in the first flange <NUM>. The eccentric shaft external teeth <NUM> on the eccentric shaft engaging portion <NUM> can engage with the second row of planetary teeth <NUM> on the second planetary gear <NUM>.

It should also be noted that although in the transmission mechanism <NUM> the first flange <NUM> is provided with an eccentric shaft accommodation portion <NUM> that transversely penetrates the first flange <NUM>, the eccentric shaft accommodation portion <NUM> may not penetrate the first flange <NUM>, but being provided with a recess to accommodate the first supporting portion <NUM> and the first flange bearing <NUM> that is sheathed over the first supporting portion <NUM>. However, in the configuration of the transmission mechanism <NUM>, the first flange <NUM> is necessarily provided with an eccentric shaft accommodation portion that transversely penetrates the first flange <NUM>, as such the eccentric shaft engaging portion <NUM> of the eccentric shaft <NUM> can be disposed on the right side (i.e., the outer side) of the first flange <NUM> such that the eccentric shaft external teeth <NUM> on the eccentric shaft engaging portion <NUM> engage with the second row of planetary teeth <NUM>.

The embodiment shown in <FIG> can achieve the similar technical effects as those of the transmission mechanism <NUM>, which will not be described in detail here.

Claim 1:
A transmission mechanism (<NUM>,<NUM>), comprising:
an outer wheel (<NUM>) which is ring-shaped and has a central axis (O);
an inner wheel (<NUM>, <NUM>), the inner wheel (<NUM>, <NUM>) being disposed in the outer wheel (<NUM>), and the inner wheel (<NUM>, <NUM>) engaging with the outer wheel (<NUM>);
an eccentric shaft (<NUM>), the eccentric shaft (<NUM>) rotating about said central axis (O) of the outer wheel (<NUM>), the periphery of the eccentric shaft (<NUM>) being provided with eccentric portions (<NUM>, <NUM>), eccentric shaft external teeth (<NUM>) and a first supporting portion (<NUM>), and the inner wheel (<NUM>, <NUM>) being disposed around the eccentric portions (<NUM>, <NUM>) such that, when the transmission mechanism (<NUM>) is in operation, the rotation of the eccentric shaft (<NUM>) drives the inner wheel (<NUM>, <NUM>) to rotate eccentrically or such that an eccentric rotation of the inner wheel (<NUM>, <NUM>) drives the eccentric shaft (<NUM>) to rotate;
a first flange (<NUM>), the first flange (<NUM>) and the inner wheel (<NUM>, <NUM>) being arranged side by side, and the first flange (<NUM>) being disposed around the first supporting portion (<NUM>);
a rotating shaft (<NUM>), the rotating shaft (<NUM>) having rotating shaft external teeth (<NUM>); and
at least one planetary gearing device (<NUM>,<NUM>), the at least one planetary gearing device (<NUM>,<NUM>) being supported by the first flange (<NUM>), the periphery of each of the at least one planetary gearing device (<NUM>) being provided with a first row of planetary teeth (<NUM>) and a second row of planetary teeth (<NUM>), the first row of planetary teeth (<NUM>,<NUM>) engaging with the rotating shaft external teeth (<NUM>), and the second row of planetary teeth (<NUM>,<NUM>) engaging with the eccentric shaft external teeth (<NUM>).