CN114810950A

CN114810950A - Internal gearing transmission mechanism

Info

Publication number: CN114810950A
Application number: CN202110110123.0A
Authority: CN
Inventors: 不公告发明人
Original assignee: Ningbo Hansheng Transmission Technology Co ltd
Current assignee: Ningbo Hansheng Transmission Technology Co ltd
Priority date: 2021-01-27
Filing date: 2021-01-27
Publication date: 2022-07-29

Abstract

The application discloses inner gearing drive mechanism, it includes interior wheel, first foreign steamer, first flange body, second foreign steamer and at least one roller group. The inner wheel has external teeth. A first outer wheel is disposed about the inner wheel, the first outer wheel having internal teeth that mesh with the external teeth. The first and second flange bodies are disposed on opposite sides of the inner wheel and are connected to each other for common rotation. At least one annular space is formed between the first flange body and the second outer wheel. Each of the at least one roller set is disposed in a respective one of the at least one annulus. The internal gearing mechanism is configured to: the second outer wheel carries the first flange body by at least one roller set. The first outer wheel is made of a material having a first hardness and the second outer wheel is made of a material having a second hardness, the first hardness being different from the second hardness. The inner gearing transmission mechanism has the advantages of long service life, good processing performance, low manufacturing cost and the like.

Description

Internal gearing transmission mechanism

Technical Field

The present application relates to a transmission mechanism, and more particularly, to an internal engagement transmission mechanism.

Background

The inner gearing transmission mechanism comprises a plurality of components such as an outer wheel, an inner wheel, a flange body and the like. Wherein, the outer wheel is provided with outer wheel inner teeth which are meshed with inner wheel outer teeth arranged on the inner wheel. The outer wheel is also provided with a bearing part for bearing the flange body. Because the bearing part and the inner tooth part of the outer wheel are worn to different degrees, the service life of the outer wheel is determined by the part of the bearing part and the inner tooth part of the outer wheel, which has lower service life, so that the service life of the outer wheel is reduced.

Disclosure of Invention

Exemplary embodiments of the present application may address at least some of the above-mentioned issues. For example, the present application provides an internal gearing mechanism that includes at least one inner wheel, a first outer wheel, a first flange body, a second outer wheel, and at least one roller set. The at least one inner wheel has external teeth. The first outer wheel is disposed around the at least one inner wheel, the first outer wheel having internal teeth engageable with the external teeth. The first and second flange bodies are disposed on opposite sides of the inner wheel and are connected to each other for rotation together. The second outer wheel is disposed about the first flange body, with at least one annular space formed between the first flange body and the second outer wheel. Each of the at least one roller set is disposed in a respective one of the at least one annulus. The first flange body is rotatably supported by the second outer wheel via the at least one roller set.

The transmission according to the present application, wherein the first outer wheel is made of a material having a first hardness and the second outer wheel is made of a material having a second hardness, and wherein the first hardness is equal to the second hardness.

The transmission according to the present application, wherein the first outer wheel is made of a material having a first hardness and the second outer wheel is made of a material having a second hardness, and wherein the first hardness is lower than the second hardness.

According to the transmission mechanism of the present application, the first outer wheel and the second outer wheel are arranged side by side and connected to each other.

According to the transmission of the present application, the at least one roller set is spaced from the first outer wheel and the first flange body is spaced from the first outer wheel.

According to the transmission of the present application, each of the at least one roller set comprises a plurality of rollers arranged in a ring in an annular space.

According to the transmission mechanism of the application, the first flange body comprises a first flange body and a radial protruding ring, and the radial protruding ring is formed by extending outwards from the first flange body in the radial direction. Wherein the at least one annular space includes a first annular space and a second annular space formed on both sides of the radially protruding ring. Wherein the at least one roller set includes a first roller set and a second roller set disposed in the first annular space and the second annular space, respectively. Wherein an axis of each roller in the first and second roller sets is arranged parallel or perpendicular to an axis of the first flange body.

According to the transmission mechanism of the application, the internal engagement transmission mechanism further comprises an isolating piece, and the isolating piece is arranged between the second roller group and the first outer wheel.

According to the transmission of the present application, the second outer wheel comprises a second outer wheel first portion and a second outer wheel second portion arranged side by side, the second outer wheel second portion being arranged between the first outer wheel and the second outer wheel first portion. Wherein the second outer wheel second portion is disposed around the first and second roller sets, and the second outer wheel first portion is disposed at one side of the first roller set to enclose the first annular space.

According to the transmission mechanism of the application, the first flange body comprises a first flange body and a first flange body radial recessed ring, and the first flange body radial recessed ring is formed by inwards recessed from the first flange body in the radial direction. The second outer wheel comprises a second outer wheel radial recessed ring, the second outer wheel is provided with a second outer wheel inner cavity used for containing the first flange body, and the second outer wheel radial recessed ring is arranged on the inner wall of the second outer wheel inner cavity. The at least one annular space comprises an annular space that is defined by the first flange body radially recessed ring and the second outer wheel radially recessed ring. The at least one roller group is a group of roller groups, and the axis of each roller in the group of roller groups is inclined to the axis of the first flange body.

According to the transmission mechanism of the present application, the second outer wheel includes a second outer wheel first portion and a second outer wheel second portion arranged side by side, the second outer wheel first portion being arranged between the first outer wheel and the second outer wheel second portion. Wherein the second outer wheel first portion, the second outer wheel second portion, and the first flange body enclose the annular space.

The transmission mechanism further comprises a driving shaft, wherein the periphery of the driving shaft is provided with at least one eccentric part, the inner wheel is arranged around the at least one eccentric part, so that the driving shaft can drive the at least one inner wheel to eccentrically rotate in the outer wheel.

The internal gearing transmission mechanism has the advantages of long service life, good processing performance, low manufacturing cost and the like because the first outer wheels which are connected together are made of a material with a first hardness, the second outer wheels are made of a material with a second hardness, and the first hardness is not equal to the second hardness.

Other features, advantages, and embodiments of the application may be set forth or apparent from consideration of the following detailed description, drawings, and claims. Furthermore, it is to be understood that both the foregoing summary of the invention and the following detailed description are exemplary and intended to provide further explanation without limiting the scope of the invention as claimed. However, the detailed description and the specific examples merely indicate preferred embodiments of the application. Various changes and modifications within the spirit and scope of the application will become apparent to those skilled in the art from this detailed description.

Drawings

These and other features and advantages of the present application may be better understood by reading the following detailed description with reference to the drawings, in which like characters represent like parts throughout the drawings, wherein:

FIG. 1A is a perspective view of an internal gearing transmission mechanism according to an embodiment of the present application, viewed from the front to the rear;

FIG. 1B is a perspective view of the internal gearing transmission mechanism illustrated in FIG. 1A as viewed from the rear to the front;

FIG. 1C is a cross-sectional view of the internal gearing mechanism shown in FIG. 1A;

FIG. 2A is a perspective view of a drive shaft of the internal gearing transmission mechanism shown in FIG. 1C;

FIG. 2B is an axial cross-sectional view of the drive shaft shown in FIG. 2A;

FIG. 3A is a perspective view of the first flange body of the internal gearing transmission mechanism illustrated in FIG. 1C, as viewed from the front to the rear;

FIG. 3B is a perspective view of the first flange body shown in FIG. 3A as viewed from the rear to the front;

FIG. 3C is an axial cross-sectional view of the first flange body shown in FIG. 3B;

FIG. 4A is a perspective view of the second flange body of the internal gearing transmission mechanism illustrated in FIG. 1C, as viewed from the front to the rear;

FIG. 4B is a perspective view of the second flange body shown in FIG. 4A as viewed from the rear to the front;

FIG. 4C is an axial cross-sectional view of the second flange body shown in FIG. 4B;

FIG. 5 is a perspective view of an inner wheel of the internal gearing transmission mechanism illustrated in FIG. 1C;

fig. 6A is a perspective view of a first outer wheel of the internal gear transmission shown in fig. 1C;

FIG. 6B is an axial cross-sectional view of the first outer wheel shown in FIG. 6A;

FIG. 7A is a perspective view of a first portion of the second outer wheel of the internal gearing mechanism illustrated in FIG. 1C as viewed from the rear to the front;

FIG. 7B is a perspective view of the first portion of the second outer wheel shown in FIG. 7A looking from the front to the back;

FIG. 8A is a perspective view of a second portion of the second outer wheel of the internal gearing mechanism illustrated in FIG. 1C, as viewed from the rear to the front;

FIG. 8B is a perspective view of the second portion of the second outer wheel shown in FIG. 8A looking from the front to the back;

FIG. 9A is a front elevational view of the internal gearing transmission mechanism illustrated in FIG. 1C;

FIG. 9B is an axial cross-sectional view of the internal gearing mechanism illustrated in FIG. 9A, as taken along line A-A of FIG. 9A;

FIG. 10 is a perspective view of the first and second roller sets of FIG. 9B;

FIG. 11 illustrates an axial cross-sectional view of an internal gearing mechanism according to another embodiment of the present application;

fig. 12 is a perspective view of the roller set of fig. 11.

Detailed Description

Various embodiments of the present application will now be described with reference to the accompanying drawings, which form a part hereof. It should be understood that although directional terms, such as "front," "rear," "left," "right," "inner" and "outer," are used herein to describe various example structural portions and elements of the application, these terms are used herein for convenience of description only and are to be determined based on example orientations shown in the drawings. Because the embodiments disclosed herein can be arranged in a variety of orientations, these directional terms are used for purposes of illustration only and are not to be construed as limiting. In the following drawings, like parts are given like reference numerals and similar parts are given like reference numerals.

Fig. 1A is a perspective view of an internal gearing mechanism 100 according to an embodiment of the present application, as viewed from the front to the rear. Fig. 1B is a perspective view of the internal gear transmission mechanism 100 shown in fig. 1A, as viewed from the rear to the front. Fig. 1C is a cross-sectional view of the internal gearing mechanism 100 shown in fig. 1A to illustrate further components of the internal gearing mechanism 100.

As shown in fig. 1A to 1C, the internal gear transmission mechanism 100 includes a first outer wheel 102, a second outer wheel 103, a drive shaft 112, two inner wheels 131,132 arranged side by side, a first flange body 104, a second flange body 106, a connecting member 109, and a transmission member 108. The first outer wheel 102 and the second outer wheel 103 are arranged side by side and are connected together by an outer wheel connection 105. The first outer wheel 102 and the second outer wheel 103 are fixed, the first outer wheel 102 is provided with internal teeth capable of meshing with external teeth of the two inner wheels 131,132, and the second outer wheel 103 is not provided with internal teeth but is configured to support or carry the first flange body 104. Two inner wheels 131,132 are fitted over the drive shaft 112 and are disposed between the first flange body 104 and the second flange body 106. The connecting member 109 extends through the two inner wheels 131,132 to connect the first flange body 104 and the second flange body 106 together, so that the first flange body 104 and the second flange body 106 can move together. The transmission member 108 penetrates the two pieces of inner wheels 131,132 and is connected to the first and

second flange bodies

104, 106 so that the power of the two pieces of inner wheels 131,132 can be transmitted to the first and

second flange bodies

104, 106 to rotate the first and

second flange bodies

104, 106.

When the internal gear transmission mechanism 100 operates, the power transmission relationship is substantially as follows:

the drive shaft 112 of the internal gear mechanism 100 is connected to a drive mechanism (not shown). The drive mechanism drives the drive shaft 112 to rotate. Because the first outer wheel 102 and the second outer wheel 103 are fixed and because of the meshing relationship between the teeth of the first outer wheel 102 and the teeth of the inner wheels 131,132, the rotation of the driving shaft 112 can drive the inner wheels 131,132 sleeved thereon to translate and rotate. The transmission member 108 transmits the rotation and torque of the inner wheels 131,132 to the first flange body 104 and the second flange body 106, and drives the first flange body 104 and the second flange body 106 to rotate. The first and

second flange bodies

104 and 106 are connected with a driven device (not shown) to realize speed change and torque output.

It should be noted that, although in the embodiment shown in fig. 1, the first outer wheel 102 and the second outer wheel 103 are stationary, the first flange body 104 and the second flange body 106 function as torque output members. In another embodiment, the first flange body 104 and the second flange body 106 may be fixed, and the first outer ring 102 and the second outer ring 103 may be used as torque output members. In addition, an internal gearing transmission mechanism 100 may be provided to achieve the purpose of speed increase or speed reduction.

The specific structure of each component in the internal gear transmission mechanism 100 is described in detail below.

Fig. 2A is a perspective view of the drive shaft 112 of the internal gear transmission mechanism 100 shown in fig. 1C, and fig. 2B is an axial sectional view of the drive shaft 112 shown in fig. 2A to show a specific structure of the drive shaft 112. As shown in fig. 2A-2B, the drive shaft 112 is a hollow shaft having a hollow portion 222. The drive shaft 112 has a central axis X. The end 224 of the drive shaft 112 is adapted to be coupled to a drive mechanism (not shown). The drive mechanism is capable of driving the drive shaft 112 to rotate about its central axis X. The hollow portion 222 of the drive shaft 112 is adapted to receive an output shaft (not shown) of the drive mechanism. As an example, the end 224 of the drive shaft 112 of the present application is provided with three holes 226 evenly distributed along its circumference for connecting the drive shaft 112 with the output shaft of the drive mechanism. Specifically, the output shaft with the hole is inserted into the hollow portion 222 of the drive shaft 112 such that the hole in the output shaft is aligned with at least one of the three holes 226 of the end portion 224. A connecting pin (not shown) extends through a hole in the output shaft and through a hole 226 in end 224 to connect drive shaft 112 to the output shaft of the drive mechanism.

The drive shaft 112 has a first eccentric portion 202 and a second eccentric portion 204 thereon. The first eccentric portion 202 and the second eccentric portion 204 are arranged eccentrically symmetrically with respect to the center axis X, and the eccentric amounts are equal. Specifically, the first eccentric portion 202 and the second eccentric portion 204 are both circular rings that are eccentrically disposed with respect to the central axis X of the drive shaft 112. The outer peripheral surface 252 of the first eccentric portion 202 forms a circumferential surface having a radius D1. The outer peripheral surface 254 of the second eccentric portion 204 forms a circumferential surface having a radius D2. The radius D1 is equal to the radius D2. More specifically, outer peripheral surface 252 and outer peripheral surface 254 each have a central axis N1 and a central axis N2. The center axis N1 and the center axis N2 both have a distance (eccentricity) e from the center axis X of the drive shaft 112. Wherein the eccentricity e is greater than 0. The central axis N1 is arranged symmetrically to the central axis N2 with respect to the central axis X. Wherein, in the cross-section shown in FIG. 2B, the central axis N1 of the first eccentric section 202 is located below the central axis X, and the central axis N2 of the second eccentric section 204 is located above the central axis X. The outer peripheral surface 254 of the second eccentric portion 204 is 180 out of phase with the outer peripheral surface 252 of the first eccentric portion 202. When the drive shaft 112 rotates about its central axis X, the central axis N1 of the first eccentric section 202 and the central axis N2 of the second eccentric section 204 both rotate about the central axis X.

The drive shaft 112 is also provided at the outer periphery with a first drive shaft bearing support portion 212 and a second drive shaft bearing support portion 214 for abutting against the inner walls of the first drive shaft bearing 901 and the inner wall of the second drive shaft bearing 902 (see fig. 9B). Wherein first drive shaft bearing support 212 is disposed to the left of first eccentric section 202 and second drive shaft bearing support 214 is disposed between second eccentric section 204 and end 224.

Fig. 3A is a perspective view of the first flange body 104 of the internal gear transmission mechanism 100 shown in fig. 1C, as viewed from the front to the rear. Fig. 3B is a perspective view of the first flange body 104 shown in fig. 3A as viewed from the rear to the front. Fig. 3C is an axial cross-sectional view of the first flange body 104 shown in fig. 3B. As shown in fig. 3A-3C, the first flange body 104 includes a first flange body 302, a radially projecting ring 304, and an axially projecting ring 306. The first flange body 302 is generally annular in shape and has a central axis F1. A radially protruding ring 304 is formed extending radially outward from the middle of the outer peripheral surface of the first flange body 302. The outer peripheral surfaces of the first flange body 302 on the left and right sides of the radially projecting ring 304 are a first outer peripheral surface 311 and a second outer peripheral surface 312, respectively. An axially projecting ring 306 is formed extending axially leftward from the left end of the first flange body 302. The outer diameter of the axially projecting ring 306 is smaller than the outer diameter of the first flange body 302, so that the axially projecting ring 306 forms a step with the first flange body 302, so that the first oil seal 911 can be hindered from moving axially to the right by the step after being mounted on the axially projecting ring 306 (see fig. 9B).

The first flange body 104 has an accommodating portion 309. A receptacle 309 extends through the first flange body 302 and the axially projecting ring 306 for receiving the drive shaft 112. The accommodating portion 309 is defined by an inner wall of the first flange body 104, and a diameter of the inner wall of a left portion of the accommodating portion 309 is smaller than a diameter of the inner wall of a right portion of the accommodating portion 309 to form an annular stepped portion 310. When the first drive shaft bearing 901 is mounted in the right portion of the accommodating portion 309 (see fig. 9B), the stepped portion 310 can block the first drive shaft bearing 901 from moving to the left side in the axial direction.

The right portion of the first flange body 302 is provided with three first connection holes 331 uniformly arranged circumferentially around the accommodating portion 309, formed extending axially leftward from the right end face of the first flange body 302 into the first flange body 302, for receiving the connection member 109. In the embodiment of the present application, the first connection hole 331 is provided with a screw thread on an inner wall thereof. The right portion of the first flange body 302 is further provided with nine first transmission holes 332 disposed around the accommodating portion 309, extending axially leftward from the right end of the first flange body 302 into the first flange body 302 to be formed, for receiving the transmission members 108. Specifically, the nine first transfer holes 332 are divided into three groups, each group including three first transfer holes 332. Each set of the first transfer holes 332 is uniformly circumferentially disposed between the two first connection holes 331. The centers of the three first connection holes 331 and the nine first transfer holes 332 are uniformly arranged in the circumferential direction. The axially projecting ring 306 is provided with eight output holes 321 arranged uniformly in the circumferential direction around the receiving portion 309. Formed to extend axially rightward from the left end face of the axially projecting ring 306 into the axially projecting ring 306 for connection to a driven device.

Fig. 4A is a perspective view of the second flange body 106 of the internal gear transmission mechanism 100 shown in fig. 1C, as viewed from the front to the rear. Fig. 4B is a perspective view of the second flange body 106 shown in fig. 4A as viewed from the rear to the front. Fig. 4C is an axial cross-sectional view of the second flange body 106 shown in fig. 4B. As shown in fig. 4A-4C, the second flange body 106 is generally annular in shape and has a central axis F2. The second flange body 106 has an accommodating portion 409. A receiving portion 409 is provided through the second flange body 106 for receiving the drive shaft 112. The accommodating portion 409 is defined by an inner wall of the second flange body 106, and a diameter of the inner wall of a left portion of the accommodating portion 409 is smaller than a diameter of the inner wall of a right portion of the accommodating portion 409 to form an annular stepped portion 410. When the second drive shaft bearing 902 is mounted in the accommodating portion 409 (see fig. 9B), the stepped portion 410 can block the second drive shaft bearing 902 from moving to the right in the axial direction.

The second flange body 106 is provided with three second connection holes 431 uniformly arranged in the circumferential direction around the accommodating portion 409. The second connecting hole 431 is a cylindrical counterbore and extends through the second flange body 106 for receiving the connecting member 109. The second flange body 106 also includes nine second transmission holes 432. A second transfer bore 432 is also a cylindrical counterbore and extends through the second flange body 106 for receiving the transfer member 108. Specifically, the nine second transfer holes 432 are divided into three groups, each group including three second transfer holes 432. Each set of second transfer holes 432 is uniformly circumferentially disposed between the two second connection holes 431. The axes of the three second connection holes 431 and the nine second transfer holes 432 are uniformly arranged in the circumferential direction. When the internal gear transmission 100 is assembled as shown in fig. 1A to 1C, the second connection hole 431 and the second transmission hole 432 of the second flange body 106 are aligned with the corresponding first connection hole 331 and the first transmission hole 332 of the first flange body 104, respectively.

Fig. 5 is a perspective view of the

inner wheels

131 and 132 shown in fig. 1C. Since the

inner wheels

132 and 131 have the same structure, the structure of the two inner wheels will be described below by taking the inner wheel 131 as an example.

As shown in fig. 5, the inner wheel 131 is substantially annular and has a thickness with a central axis. The outer periphery of the inner wheel 131 has external teeth 511. The outer teeth 511 can mesh with the inner teeth 602 (see fig. 6A-6B) of the first outer wheel 102. More specifically, at least a portion of the external teeth 511 can mesh with the internal teeth 602 of the first outer wheel 102 when the inner wheel 131 moves. The outer teeth 511 and the inner teeth 602 have a difference in the number of teeth (i.e., the number of teeth of the inner teeth 602 is greater than the number of teeth of the outer teeth 511), and the inner wheel 131 and the first outer wheel 102 are configured to: when the inner wheel 131 moves in the first outer wheel 102, the inner wheel 131 can perform rotation and translation (i.e., revolution and rotation).

The inner wheel 131 has a receiving portion 501. The receiving portion 501 is provided through the inner wheel 131 to receive the driving shaft 112 and the first inner wheel bearing 921. The wall 508 of the receiving portion 501 has a diameter substantially the same as the outer diameter of the first inner wheel bearing 921 of the drive shaft 112 (see fig. 9B), so that the inner wheel 131 can be fitted over the first inner wheel bearing 921 provided around the first eccentric portion 202 of the drive shaft 112. When the driving shaft 112 rotates, the driving shaft 112 can rotate the inner wheel 131 through the first inner wheel bearing 921.

Twelve through holes 504 are also provided on the inner wheel 131, which are evenly arranged in the circumferential direction around the receiving portion 501. Three of the twelve through holes 504 are used to receive the connection members 109, and nine of the twelve through holes 504 are used to receive the transmission members 108. The diameter of the twelve through holes 504 is larger than the diameter of the outer contour of the connection part 109 and also larger than the diameter of the outer contour of the receiving transmission part 108.

Fig. 6A is a perspective view of the first outer wheel 102 shown in fig. 1C. Fig. 6B is an axial sectional view of the first outer wheel 102 shown in fig. 6A. As shown in fig. 6A-6B, the first outer wheel 102 is substantially annular and has a central axis Y1. The first outer wheel 102 has a projection 631 projecting outwardly from the left end face thereof for insertion into the second outer wheel 103 to facilitate positioning and connection of the two. The first outer wheel 102 has a receiving portion 612, and the receiving portion 612 axially penetrates the first outer wheel 102 and is defined by an inner wall of the first outer wheel 102. The diameter of the inner wall of the left portion of the accommodating portion 612 is smaller than the diameter of the inner wall of the right portion of the accommodating portion 612 to form the annular stepped portion 610. When the second oil seal 912 is accommodated in the right portion of the accommodating portion 612 (see fig. 9B), the stepped portion 610 can block the second oil seal 912 from moving to the left side in the axial direction. The inner wall of the left part of the receiving portion 612 is provided with internal teeth 602 which can mesh with the external teeth 511 of the

inner wheels

131, 132.

The first outer wheel 102 is also provided with four first outer wheel connecting holes 622 uniformly arranged in the circumferential direction. Formed to extend axially rightward into the first outer wheel 102 from a left end face of the first outer wheel 102 for receiving four outer wheel connectors 105. In the embodiment of the present application, the first outer wheel attachment aperture 622 is a threaded aperture that is capable of mating with threads on the four outer wheel attachments 105.

Second outer wheel 103 includes a second outer wheel first portion 701 (shown in fig. 7A and 7B) and a second outer wheel second portion 801 (shown in fig. 8A and 8B). The first outer wheel 102, the second outer wheel first part 701 and the second outer wheel second part 801 are connected together by four outer wheel connections 105 to form an outer wheel of the internal gearing 100. Wherein the second outer wheel second portion 801 is disposed between the second outer wheel first portion 701 and the first outer wheel 102 (as shown in figure 9B). The specific structure of the second outer wheel 103 will now be described with reference to fig. 7A-8B.

Fig. 7A is a perspective view of the second outer wheel first part 701 as viewed from the rear to the front. Fig. 7B is a perspective view of the second outer wheel first part 701 shown in fig. 7A, viewed from the front to the rear. As shown in fig. 7A-7B, the second outer wheel first portion 701 is generally annular and has a central axis Y2. The second outer wheel first part 701 has a receiving portion 712. A receiving portion 712 is provided through the second outer wheel first portion 701 for receiving the axially projecting ring 306 of the first flange body 104 (see fig. 9B). The second outer wheel first part 701 is provided with four first part attachment holes 714 arranged circumferentially evenly around the receptacle 712 for receiving the four outer wheel attachments 105. In the embodiment of the present application, the four first portion connection holes 714 are cylindrical counterbores.

Fig. 8A is a perspective view of the second outer wheel second portion 801 as viewed from the rear to the front. Fig. 8B is a perspective view of the second outer wheel second portion 801 shown in fig. 8A as viewed from the front to the rear. 8A-8B, second outer wheel second portion 801 is generally annular in shape and has a central axis Y3. The second outer wheel second portion 801 has a receptacle 812. A receiving portion 812 is provided through the second outer wheel second portion 801 for receiving the first flange body 302 and the radially projecting ring 304 of the first flange body 104 (see fig. 9B). The second outer wheel second portion 801 is provided with four second portion connection holes 814 uniformly arranged circumferentially around the receptacle 812, which axially extend through the second outer wheel second portion 801 for receiving the four outer wheel connectors 105. The inner wall of the second outer wheel second portion 801 defines a receptacle 812. The diameter of the inner wall of the second outer wheel second portion 801 is greater than the diameter of the inner wall of the first outer wheel 102 so that the projection 631 of the first outer wheel 102 can be inserted into the receptacle 812. But the diameter of the inner wall of the second outer wheel second portion 801 is also larger than the diameter of the inner wall of the second outer wheel first portion 701. The above arrangement enables the formation of the first annular space 998 and the second annular space 999 as shown in fig. 9B.

Fig. 9A is a front view of the internal gearing mechanism 100 shown in fig. 1C. Fig. 9B is an axial cross-sectional view of the internal gearing mechanism 100 shown in fig. 9A, taken along line a-a in fig. 9A. As shown in fig. 9A-9B, the central axis X of the drive shaft 112, the central axis F1 of the first flange body 104, the central axis F2 of the second flange body 106, the central axis Y1 of the first outer wheel 102, the central axis Y2 of the second outer wheel first portion 701, and the central axis Y3 of the second outer wheel second portion 801 are coaxially disposed. The structure and mating relationship of the various components of the internal gearing mechanism 100 are described below with reference to fig. 9A-9B:

the first eccentric portion 202 of the driving shaft 112 is sleeved with a first inner wheel bearing 921. The inner wheel 131 is sleeved on the first inner wheel bearing 921. When the drive shaft 112 rotates about the central axis X, the inner wheel 131 revolves about the central axis X, that is, the central axis N1 of the inner wheel 131 rotates about the central axis X (i.e., translates). The second eccentric portion 204 of the driving shaft 112 is provided with a second inner bearing 922. The inner wheel 132 is fitted over the second inner wheel bearing 922. When the drive shaft 112 rotates about the central axis X, the inner wheel 132 revolves around the central axis X, that is, the central axis N2 of the inner wheel 132 rotates (i.e., translates) around the central axis X. Since the

inner wheels

131 and 132 are eccentrically disposed opposite to each other with respect to the central axis X, when the driving shaft 112 rotates the

inner wheels

131 and 132, the phase of the inner wheels 131 is 180 ° different from that of the inner wheels 132, so as to ensure that the internal gear transmission mechanism 100 maintains dynamic balance when the

inner wheels

131 and 132 move.

In addition, when the drive shaft 112 revolves the inner ring 131 and the inner ring 132, the outer teeth 511 of the inner ring 131 and the inner ring 132 are engaged with the inner teeth 602 of the first outer ring 102, and the outer teeth 511 and the inner teeth 602 have a difference in the number of teeth, and the first outer ring 102 is fixed, so that the inner ring 131 and the inner ring 132 can rotate about their respective central axes (i.e., the central axis N1 and the central axis N2). That is, the

inner wheels

131 and 132 rotate while revolving.

The first flange body 104 and the second flange body 106 are respectively disposed on both sides of the

inner wheels

131, 132. The first flange body 104 and the second flange body 106 are connected together by a connecting member 109. The first and

second flange bodies

104 and 106 are supported on the drive shaft 112 by first and second

drive shaft bearings

901 and 902, respectively. Specifically, the inner wall of the first driveshaft bearing 901 contacts the first driveshaft bearing support portion 212, and the outer wall of the first driveshaft bearing 901 contacts the right portion of the wall of the accommodating portion 309 of the first flange body 104. The inner wall of the second driveshaft bearing 902 contacts the second driveshaft bearing support portion 214, and the outer wall of the second driveshaft bearing 902 contacts the left portion of the inner wall of the accommodating portion 409 of the second flange body 106. The internal gear transmission 100 also includes three connecting members 109. In this application, the connecting member 109 includes a bolt 931 and a sleeve 932, the sleeve 932 being located in the inner wheel 131 and the inner wheel 132. The left end of the bolt 931 is threaded and can be engaged with the threads provided on the inner wall of the first coupling hole 331 of the first flange body 104. A sleeve 932 fits over the bolt 931 to protect the bolt 931 from rubbing against the inner wheel 131 and the inner wheel 132 with the bolt 931. The length of the sleeve 932 is configured to be shorter than the length of the bolt 931 so that both ends of the bolt 931 can protrude out of the sleeve 932. The sleeve 932 has an outer diameter smaller than the diameter of the through-holes 504 on the inner and

outer wheels

131 and 132 so that the sleeve 932 can be received in the through-hole 504. The bolt 931 extends from the right side of the internal gear transmission mechanism 100 through the second connection hole 431 of the second flange body 106 and the sleeve 932 in this order into the first connection hole 331 of the first flange body 104. The threads on the bolt 931 are engaged with the threads on the inner wall of the first coupling hole 331 to couple the first flange body 104 and the second flange body 106 together.

Internal gear 100 also includes nine transmission members 108. The transmission member 108 includes cylindrical pins 941 and pin bushes 942, which are located in the inner wheel 131 and the inner wheel 132. The pin sleeve 942 is fitted over the pins 941 to protect the pins 941 to reduce friction between the pins 941 and the

inner wheels

131 and 132. The length of the pin 941 is configured to be longer than the length of the pin bush 942 so that both ends of the pin 941 can be protruded. The pin bosses 942 are inserted into the first transfer holes 332 of the first flange body 104 and the second transfer holes 432 of the second flange body 106. The outer diameter of the peg sleeve 942 is smaller than the inner diameter of the through holes 504 on the inner wheel 131 and the inner wheel 132. The pin 941 sequentially passes through the second transmission hole 432 and the pin bush 942 of the second flange body 106 from the right side of the internal gear transmission 100 and then extends into the first transmission hole 332 of the first flange body 104, thereby connecting the first flange body 104 and the second flange body 106. In an embodiment of the present application, the diameter of the pin 941 is slightly larger than the diameter of the first transmission hole 332 of the first flange body 104 and the second transmission hole 432 of the second flange body 106, so that the pin 941 is connected with the first flange body 104 and the second flange body 106 by interference fit.

The outer wheel comprises a first outer wheel 102, a second outer wheel first part 701 and a second outer wheel second part 801 connected together by an outer wheel connector 105, the second outer wheel second part 801 being located between the first outer wheel 102 and the second outer wheel first part 701. Wherein the first outer wheel 102 is made of a material having a first hardness and the second outer wheel first part 701 and the second outer wheel second part 801 are made of a material having a second hardness. In the embodiment of the present application, the outer wheel attachment 105 is a bolt. The right end of the bolt has threads that mate with threads on the inner wall of the first outer wheel attachment hole 622. The outer wheel link 105 extends from the left side of the inner gearing 100 through a first portion attachment aperture 714 in the second outer wheel first portion 701 and a second portion attachment aperture 814 in the second outer wheel second portion 801 in that order and into a first outer wheel attachment aperture 622 in the first outer wheel 102. The threads on the outer wheel connector 105 mate with the threads on the inner wall of the first outer wheel connector aperture 622 to connect the first outer wheel 102, the second outer wheel first portion 701 and the second outer wheel second portion 801 together.

The first flange body 104 encloses two annular spaces with the second outer wheel first portion 701 and the second outer wheel second portion 801. More specifically, the first outer peripheral surface 311 of the first flange body 104, the left surface of the radially projecting ring 304 of the first flange body 104, the inner wall of the receiving portion 812 of the second outer wheel second portion 801, and the right side wall of the second outer wheel first portion 701 surround to form a first annular space 998. The second outer peripheral surface 312 of the first flange body 104, the right surface of the radially projecting ring 304 of the first flange body 104, the inner wall of the receiving portion 812 of the second outer wheel second portion 801, and the left side wall of the first outer wheel 102 enclose a second annular space 999.

The internal gearing mechanism 100 also includes a first roller set 991 and a second roller set 992, the first roller set 991 and the second roller set 992 being received in the first annular space 998 and the second annular space 999, respectively. In this embodiment, the first and second roller sets 991 and 992 are identical in structure. Specific structures of the first and second roller sets 991 and 992 are described below with reference to fig. 1C and 10:

fig. 10 is a perspective view of the first and second roller sets 991 and 992 to show a specific structure of the first and second roller sets 991 and 992. Since the first and second roller sets 991 and 992 have the same structure, fig. 10 shows only a specific structure of the first roller set 991. As shown in fig. 10, the first roller set 991 includes thirty-two rollers 1001. Each roller 1001 is a cylinder. A separator 1002 is disposed between two adjacent rollers 1001 to prevent the two adjacent rollers 1001 from contacting. Thirty-two rollers 1001 and thirty-two spacers 1002 are accommodated in the annular spaces (i.e., the first annular space 998 and the second annular space 999), and are arranged in a ring shape. As an example, in the present embodiment, the axes of the adjacent two rollers 1001 are perpendicular to each other. In other words, the axes of sixteen rollers 1001 of the thirty-two rollers 1001 are arranged parallel to the central axis X of the ring gear transmission mechanism 100, and the axes of the other sixteen rollers 1001 are arranged perpendicular to the central axis X of the ring gear transmission mechanism 100. As another example, thirty-two rollers 1001 may also be arranged: the axis of each roller 1001 is arranged in parallel with the central axis X of the ring gear 100, or the axis of each roller 1001 is arranged perpendicular to the central axis X of the ring gear 100.

The first and second roller sets 991, 992 are configured to respectively bear two axial forces parallel to the central axis X in opposite directions. As one example, the first roller set 991 is configured to bear axial forces parallel to the central axis X from left to right. The second roller set 992 is configured to bear a right-to-left radial force parallel to the central axis X.

Internal gear 100 also includes a spacer 903. The spacer 903 is ring-shaped, and is disposed in the second annular space 999 and to the right of the second roller group 992. Isolator 903 is used to space second roller set 992 from first outer wheel 102 such that second roller set 992 does not contact first outer wheel 102 (i.e., second roller set 992 is a distance from first outer wheel 102). It should be noted that the radially projecting ring 304 of the first flange body 104 has a certain mounting clearance with the second outer wheel second portion 801, so that the second outer wheel second portion 801 does not interfere with the rotation of the first flange body 104.

The internal gear transmission 100 also includes a first oil seal 911 and a second oil seal 912. The first oil seal 911 and the second oil seal 912 are both annular. The inner wall of the first oil seal 911 contacts the outer wall of the axially projecting ring 306 of the first flange body 104, and the outer wall of the first oil seal 911 contacts the inner wall of the accommodating portion 712 of the second outer wheel first part 701. The inner wall of the second oil seal 912 contacts the outer wall of the second flange body 106. The outer wall of the second oil seal 912 contacts the right portion of the wall of the accommodating portion 612 of the first outer wheel 102. As one example, the first oil seal 911 and the second oil seal 912 are made of rubber.

The process of torque transmission during operation of internal-gearing transmission 100 is described in detail below:

a drive mechanism (e.g., a motor, not shown) drives the drive shaft 112 for rotation about the central axis X. The driving shaft 112 drives the

inner wheels

131 and 132 to translate (i.e., the central axes N1 and N2 rotate around the central axis X) through the first inner wheel bearing 921 and the second inner wheel bearing 922. The external teeth 511 of the

inner wheels

131 and 132 are engaged with the internal teeth 602 of the first outer wheel 102, thereby causing the

inner wheels

131 and 132 to rotate (i.e., the

inner wheels

131 and 132 can rotate about the respective central axes N1 and N2). Thus, the inner ring 131 and the inner ring 132 can rotate while revolving.

When the

inner wheels

131 and 132 revolve and rotate, the transmission member 108 (including the pins 941 and the pin sleeves 942) transmits the rotation of the

inner wheels

131 and 132 to the first flange body 104 and the second flange body 106 by the engagement of the transmission member 108 (including the pins 941 and the pin sleeves 942) with the through holes 504, so that the first flange body 104 and the second flange body 106 rotate around the central axis X. The first flange body 104 may be coupled to a driven device (not shown). Thereby, the torque of the drive mechanism can be output to the driven device through the internal gear transmission mechanism 100.

It should be noted that, since the first flange body 104 is mounted or supported in the second outer wheel second portion 801 by the first roller set 991 and the second roller set 992, and the second outer wheel second portion 801 is stationary, the first flange body 104 and the second flange body 106 can only rotate around the central axis X, and cannot generate translational motion in the second outer wheel second portion 801. Since the transmission member 108 is connected to the first flange body 104 and the second flange body 106, the transmission member 108 can only rotate around the central axis X and cannot translate due to the limitation of the first flange body 104. This enables the transmission member 108 to transmit only the rotation (i.e., rotation) of the

inner wheels

131 and 132 to the first and

second flange bodies

104 and 106 without transmitting the translation (i.e., revolution) of the

inner wheels

131 and 132 to the first and

second flange bodies

104 and 106 during the transmission of power from the

inner wheels

131 and 132 to the transmission member 108.

It should be noted that although the inter-ring transmission mechanism 100 includes a specific number of components such as the three first connection holes 331, the nine first transmission holes 332, the three second connection holes 431, the nine second transmission holes 432, the thirty-two rollers 1001, and the thirty-two spacers 1002 in the above-described embodiments, the present application is not intended to limit the specific number of these components, and the inter-ring transmission mechanism 100 including any number of the above-described components falls within the scope of the present application.

It should be noted that although the transmission member 108 includes the cylindrical pin 941 and the pin sleeve 942 in the embodiment of the present application, in other embodiments, the transmission member 108 may not include the pin sleeve 942.

It should also be noted that although in the embodiment of the present application second outer wheel first portion 701 and second outer wheel second portion 801 are two separate pieces and are connected together by outer wheel connector 105, it will be understood by those skilled in the art that second outer wheel first portion 701 and second outer wheel second portion 801 may be integrally formed as a single piece.

Fig. 11 is an axial cross-sectional view of an inter-ring gear system 1100 according to another embodiment of the present application. The internal gearing mechanism 1100 shown in fig. 11 has the same structure as the internal gearing mechanism 100 shown in fig. 1A to 10, and the description thereof is omitted. The transmission process of the internal gearing mechanism 1100 shown in fig. 11 is also the same as that of the internal gearing mechanism 100 shown in fig. 1A-10, and therefore, the description thereof is omitted. The internal gear transmission mechanism 1100 shown in fig. 11 differs from the internal gear transmission mechanism 100 shown in fig. 1A to 10 in that: internal gear system 1100 includes an annulus 1199 and a set of rollers 1200 disposed in annulus 1199. Specifically, annulus 1199 is enclosed by first flange body 1104, second outer wheel first portion 1111, and second outer wheel second portion 1112. The first flange body 1104 includes a first flange body radially recessed ring 1301 formed recessed radially inward from the outer edge of the first flange body. In axial cross-section of the internal geared drive mechanism 1100, the first flange body radially recessed ring 1301 is substantially triangular to form two adjacent walls of the annular space 1199. An annular recess 1302 is provided at the inner edge of the right portion of the second outer wheel first portion 1111, and the wall surface of the annular recess 1302 is provided obliquely to the center axis X of the ring gear transmission 1100. An annular recess 1303 is provided at the inner edge of the left portion of the second outer wheel second portion 1112, and the wall surface of the annular recess 1303 is also provided obliquely to the center axis X of the internal gear transmission mechanism 1100. In this embodiment, two wall surfaces of the first flange radial recessed ring 1301, a wall surface of the annular recess 1302, and a wall surface of the annular recess 1303 enclose an annular space 1199. The annular space 1199 accommodates the roller set 1200 therein. The specific structure of the roller set 1200 is described below with reference to fig. 12:

fig. 12 is a perspective view of the roller group 1200 to show a specific structure of the roller group 1200. As shown in fig. 12, the roller set 1200 includes forty rollers 1201. Each roller 1201 is a cylinder. Forty rollers 1201 are received in the annular space 1199 and are arranged in a ring. As an example, in the present embodiment, the axes of two adjacent rollers 1201 are perpendicular to each other. In other words, the axes of twenty of the forty rollers 1201 are arranged in a first direction and the axes of the other twenty rollers 1001 are arranged in a second direction, wherein the first direction is perpendicular to the second direction. In the present embodiment, the axis of any one of the rollers 1201 is inclined with respect to the central axis X of the internal gear transmission 1100. The rollers 1201, whose axes are oblique to the central axis X, are able to take up axial forces parallel to the central axis X.

In addition, annular space 1199 is enclosed by first flange body 1104, second outer wheel first portion 1111, and second outer wheel second portion 1112. Roller set 1200 in the middle of the annulus does not contact first outer wheel 1102 (i.e., roller set 1200 is spaced a distance from first outer wheel 1102). The internal gear system 1100 is therefore not provided with a spacer ring for spacing the roller set 1200 from the first outer wheel 1102.

It will be appreciated by those skilled in the art that although in the embodiment of the present application the second outer wheel first portion 1111 and the second outer wheel second portion 1112 are two separate parts and are connected together by the outer wheel connection 105, those skilled in the art will appreciate that the second outer wheel first portion 1111 and the second outer wheel second portion 1112 may be integrally formed as a single piece and the inner wall of the inner cavity of the second outer wheel is provided with a second outer wheel radially recessed ring.

Due to the arrangement of the outer wheel, the inner gearing transmission mechanism 100 and the inner gearing transmission mechanism 1100 in the embodiment of the application have the advantages of long service life, good processing performance, low manufacturing cost and the like. In particular, the present application divides the outer wheel of the internal gear transmission into two main parts, namely a first outer wheel and a second outer wheel, wherein only the first outer wheel is provided with the gear teeth, while the second outer wheel is not provided with the gear teeth, and the second outer wheel is only used for supporting or carrying the flange part. That is, only the first outer wheel performs the meshing transmission, while the second outer wheel only functions as a support/carrier member. Configuring the first outer wheel to assume a meshing transmission role and the second outer wheel to assume a load-bearing role has at least the following advantages:

first, configuring the first outer wheel to assume a meshing transmission role and the second outer wheel to assume a load-bearing role can reduce machining costs. Specifically, in the conventional internal gear transmission mechanism, the outer wheel needs to perform both the bearing function and the meshing transmission function. When a machining factory is selected, machining equipment is required to machine the bearing part and machining equipment is not required to machine the teeth. This requires both processing techniques for the processing plant and the processing requirements are high, resulting in high processing costs. In the internal gear transmission mechanism 100 and the internal gear transmission mechanism 1100 according to the embodiment of the present application, the first outer wheel performs a mesh transmission function and the second outer wheel performs a load bearing function. Thus, during machining, the manufacturer can choose a machining factory for the specific machining of the carrier part and then a machining factory for the specific machining of the teeth, and then assemble the first outer wheel with the second outer wheel. Thus, it is sufficient for one processing factory to have one processing technology, and the manufacturer has a large choice of selecting the processing factory, so that the processing cost can be reduced.

Second, configuring the first outer wheel to take on the meshing transmission role and the second outer wheel to take on the bearing role can reduce part replacement costs. Specifically, in the conventional internal gear transmission mechanism, the outer wheel needs to perform both the bearing function and the meshing transmission function. When the outer wheel wears, the entire outer wheel needs to be replaced. In the inner gearing transmission mechanism 100 and the inner gearing transmission mechanism 1100 according to the embodiment of the present application, when the first outer wheel is worn, the first outer wheel may be replaced; or when the second outer wheel is worn, the second outer wheel can be replaced. The operation is high in convenience and low in cost.

The above two advantages can be obtained regardless of whether the hardness of the material of the first outer ring and the second outer ring is the same.

Furthermore, the first outer wheel and the second outer wheel may be manufactured using materials having different hardnesses, for example the first outer wheel is made of a material of a first hardness, the second outer wheel is made of a material of a second hardness, and the first hardness is lower than the second hardness.

For example, when it is desired that the second outer wheel have a higher load carrying capacity than the first and second flange bodies, the first and second outer wheels may be configured to: the first hardness is lower than the second hardness. At this time, the second outer wheel having the higher second hardness can satisfy the requirement of higher bearing capacity requirement of the first flange body and the second flange body, and the internal teeth of the first outer wheel having the lower first hardness are engaged with the external teeth of the inner wheel. Although the internal teeth of the first outer wheel have low hardness, the requirement of meshing can be fully satisfied. For materials with lower hardness, the processing time is shorter and the processing cost is lower. In the conventional internal gearing transmission mechanism, the outer wheel needs to have both the bearing function and the meshing transmission function, so that in order to meet the requirement of high bearing capacity, the whole outer wheel needs to be made of a material with high hardness, which results in that the outer wheel part with low hardness requirement is made of a high-hardness material, thereby increasing the processing time and the processing cost.

It should be noted that although the present application illustrates an embodiment in which the roller set is disposed in the annular space, those skilled in the art will appreciate that existing bearings may be disposed in the annular space. As long as it can take up axial forces parallel to the central axis X. It should be noted that the external teeth and the internal teeth that mesh with each other in the present application may be any type of tooth profile, for example, cycloid teeth, circular arc teeth, involute teeth, or plane teeth.

The number of inner rings is not limited to two as shown in the embodiments of the present application, and the number and arrangement of the inner rings may be set so as to maintain the overall dynamic balance during eccentric rotation.

It should be noted that although two annular spaces are shown in the first embodiment of the present application and one annular space is shown in the second embodiment of the present application, at least one annular space is within the scope of the present application.

It is noted that at least two outer wheel attachments, at least two connecting members and at least two transmission members are within the scope of the present application.

While only certain features of the application have been illustrated and described herein, many modifications and changes will occur to those skilled in the art. It is, therefore, to be understood that the appended claims are intended to cover all such modifications and changes as fall within the true spirit of the application.

Claims

1. An internal gearing transmission, comprising:

at least one inner wheel having external teeth;

a first flange body and a second flange body disposed on opposite sides of the at least one inner wheel and connected to each other for common rotation;

a first outer wheel disposed about the at least one inner wheel and having internal teeth engageable with the external teeth, and a second outer wheel disposed about the first flange body and forming at least one annular space with the first flange body; and

at least one roller set, each of the at least one roller set disposed in a respective one of the at least one annular space, the first flange body rotatably supported by the second outer wheel by the at least one roller set.

2. An internal gearing mechanism according to claim 1, wherein:

wherein the first outer wheel is made of a material having a first hardness and the second outer wheel is made of a material having a second hardness, and wherein the first hardness is equal to the second hardness.

3. An internal gearing mechanism according to claim 1, wherein:

wherein the first outer wheel is made of a material having a first hardness and the second outer wheel is made of a material having a second hardness, and wherein the first hardness is lower than the second hardness.

4. An internal gearing mechanism according to claim 1, wherein:

the first outer wheel and the second outer wheel are arranged side by side and connected to each other.

5. An internal gearing mechanism according to claim 1, wherein:

the at least one roller set is spaced a distance from the first outer wheel.

6. An internal gearing mechanism according to claim 1, wherein:

each of the at least one roller set includes a plurality of rollers arranged in a ring in an annular space.

7. An internal gearing mechanism according to claim 1, wherein:

the first flange body comprises a first flange body and a radially protruding ring, and the radially protruding ring is formed by extending outwards from the first flange body in a radial direction;

wherein the at least one annular space includes a first annular space and a second annular space formed on both sides of the radially protruding ring;

wherein the at least one roller set comprises a first roller set and a second roller set disposed in the first annular space and the second annular space, respectively;

wherein an axis of each roller in the first and second roller sets is arranged parallel or perpendicular to an axis of the first flange body.

8. An internal gearing mechanism according to claim 7, wherein:

the inner gearing transmission mechanism further comprises an isolating piece, and the isolating piece is arranged between the second roller group and the first outer wheel.

9. An internal gearing mechanism according to claim 7, wherein:

the second outer wheel comprises a second outer wheel first portion and a second outer wheel second portion arranged side-by-side, the second outer wheel second portion being arranged between the first outer wheel and the second outer wheel first portion;

wherein the second outer wheel second portion is disposed around the first and second roller sets, and the second outer wheel first portion is disposed at one side of the first roller set to enclose the first annular space.

10. An internal gearing mechanism according to claim 1, wherein:

the first flange body comprises a first flange body and a first flange body radial recessed ring, and the first flange body radial recessed ring is formed by inwards recessed from the first flange body in the radial direction;

the second outer wheel comprises a second outer wheel radial recessed ring, the second outer wheel is provided with a second outer wheel inner cavity used for containing the first flange body, and the second outer wheel radial recessed ring is arranged on the inner wall of the second outer wheel inner cavity;

the at least one annular space comprises an annular space which is formed by the first flange body radial sunken ring and the second outer wheel radial sunken ring in a surrounding mode;

the at least one roller group is a group of roller groups, and the axis of each roller in the group of roller groups is inclined to the axis of the first flange body.

11. An internal gearing mechanism according to claim 10, wherein:

the second outer wheel includes a second outer wheel first portion and a second outer wheel second portion arranged side-by-side, the second outer wheel first portion being disposed between the first outer wheel and the second outer wheel second portion;

wherein the second outer wheel first portion, the second outer wheel second portion, and the first flange body enclose the annular space.