One-way planetary gear transmission

Abstract

The utility model relates to a one-way planetary gear transmission which comprises a large traveling wheel structure, a first overrun clutch, a satellite wheel structure, a second overrun clutch and a planet carrier. According to the one-way planetary gear transmission, the two overrun clutches with the same structure are combined with the two planetary gear structures respectively, the two overrun clutches are arranged reversely, the one-way planetary gear transmission compact and reasonable in structure is formed, the two overrun clutches are controlled by changing the steering direction of the sun gear, one overrun clutch is locked, and the other overrun clutch is separated; therefore, different transmission routes are switched, and different output rotating speeds and torques are obtained. The two planetary gear structures are controlled through the two overrun clutches correspondingly, the space utilization rate is increased, through the multi-stage planetary gear structures, power can be reasonably distributed, output steering is not changed, and speed change and steering are not changed.

Description

Technical Field

[0001] The utility model relates to the technical field of transmissions, in particular to a one-way planetary gear transmission. Background Art

[0002] One-way automatic transmissions are a widely used industrial product, suitable for various mechanical equipment, including escalators and conveyor belts, primarily in these industries. Traditional one-way automatic transmissions require switching transmission racks, resulting in excessive volume due to the increased number of stages, poor internal space utilization, and insufficient torque. Furthermore, existing gear reduction systems suffer from irrational power distribution, resulting in insufficient overall structural strength. This, combined with the resulting damage to the gears and shortened precision retention, makes them unsuitable for demanding applications.

[0003] How to reduce the size of the transmission without changing the output direction, increase the torque that the transmission can transmit, and extend the service life of the transmission has become an urgent problem to be solved. Summary of the Invention

[0004] The purpose of the utility model is to provide a one-way planetary gear transmission, aiming to solve the problems of large size, unreasonable power distribution and short life of traditional transmissions without changing the output direction.

[0005] In order to solve the above technical problems, the present invention provides a one-way planetary gear transmission, including: a large traveling wheel structure, including a sun wheel, a large traveling wheel and a first outer ring gear that are meshed in sequence; the sun wheel is the input end; a first overrunning clutch is sleeved on the periphery of the large traveling wheel structure, and the inner ring of the first overrunning clutch is integrated with the first outer ring gear; a satellite wheel structure, including an asteroid wheel, a satellite wheel and a second outer ring gear that are meshed in sequence; wherein the asteroid wheel is coaxial with the large traveling wheel; a second overrunning clutch is sleeved on the periphery of the satellite wheel structure, and the inner ring of the second overrunning clutch is integrated with the second outer ring gear; a planetary carrier, as the output end; the large traveling wheel, the asteroid wheel and the satellite wheel are all rotatably mounted on the planetary carrier; wherein the first overrunning clutch and the second overrunning clutch have the same structure and are installed in opposite directions to each other.

[0006] Furthermore, there are three large traveling wheels, three asteroid wheels and three satellite wheels; the sun wheel is engaged with the three large traveling wheels at the same time; the satellite wheels are spaced apart from the asteroid wheels in sequence along the circumferential direction, and the line connecting the axes of the asteroid wheels and the satellite wheels forms a regular hexagon.

[0007] Furthermore, the one-way planetary gear transmission includes: a cylindrical pin corresponding to the satellite wheel and fixedly connected to the planetary carrier, and the satellite wheel is mounted on the cylindrical pin through a needle bearing; a planetary shaft, rotatably mounted on the planetary carrier, and the large planetary wheel and the small planetary wheel are both fixedly connected to the planetary shaft.

[0008] Furthermore, one end of the sun gear corresponds to the rotation center of the planet carrier and is rotatably mounted on the planet carrier through a bearing.

[0009] Furthermore, a partition is provided between the large running wheel and the satellite wheel along the axial direction.

[0010] Furthermore, the overrunning clutch is a roller-type overrunning clutch.

[0011] Furthermore, the one-way planetary gear transmission also includes: a housing, which defines a tubular installation space, and the housing includes an inlet and an outlet; the large running wheel structure is installed in the installation space corresponding to the inlet; the planetary carrier is installed in the installation space corresponding to the outlet; the outer rings of the first overrunning clutch and the second overrunning clutch are integrated with the side wall of the housing.

[0012] Furthermore, the one-way planetary gear transmission further includes: a blocking plate, which is sandwiched between the first outer gear ring and the second outer gear ring and is used to isolate the first outer gear ring and the second outer gear ring.

[0013] Furthermore, the one-way planetary gear transmission also includes: a base, which is installed on the housing corresponding to the inlet, and the sun gear is installed on the base through a bearing at one end corresponding to the inlet; a cover, which is installed on the housing corresponding to the outlet, and the planet carrier is installed on the cover through a bearing.

[0014] Furthermore, the base, the box body and the cover are fastened together as a whole by bolts.

[0015] The implementation of the present invention will have the following beneficial effects:

[0016] The overrunning clutch is combined with the planetary gear structure, and the volume of the gear transmission structure is reduced by integrating the inner ring of the first overrunning clutch with the first outer gear ring and integrating the inner ring of the second overrunning clutch with the second outer gear ring.

[0017] The sun gear input drives the large traveling wheel to rotate, the asteroid wheel and the large traveling wheel are set coaxially but with different numbers of teeth, the asteroid wheel is engaged with the satellite wheel to drive the satellite wheel to rotate to drive the planetary carrier output, and the transmission path is controlled by the first overrunning clutch and the second overrunning clutch set in pairs in opposite directions, so that the planetary carrier output direction is always the same regardless of whether the sun gear input direction is clockwise or counterclockwise.

[0018] The main running wheel and the satellite wheel are separated by a partition, and the machine cover, the machine base and the box body are fixedly connected into one body by bolts, which increases the overall stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0020] Figure 1 A schematic diagram of the internal structure of a one-way planetary gear transmission provided by an embodiment of the present disclosure from one perspective;

[0021] Figure 2 A schematic diagram of the internal structure of a one-way planetary gear transmission provided by an embodiment of the present disclosure from another perspective;

[0022] Figure 3 A schematic cross-sectional view of a one-way planetary gear transmission according to an embodiment of the present disclosure;

[0023] Figure 4 A one-way planetary gear transmission according to an embodiment of the present disclosure is provided. Figure 3 Schematic diagram of the cross-sectional structure of AA;

[0024] Figure 5 A one-way planetary gear transmission according to an embodiment of the present disclosure is provided. Figure 3 Schematic diagram of the cross-sectional structure of the middle BB;

[0025] Figure 6 A schematic diagram of the installation of a large traveling wheel structure provided in one embodiment of the present disclosure;

[0026] Figure 7 A schematic diagram of the installation of a second planetary gear structure provided in one embodiment of the present disclosure;

[0027] Figure 8 A schematic diagram of the installation of the large running wheel structure and the second planetary gear structure provided in one embodiment of the present disclosure;

[0028] Figure 9 A schematic diagram of the external structure of a one-way planetary gear transmission provided in one embodiment of the present disclosure.

[0029] Reference numerals:

[0030] 100. One-way planetary gear transmission; 110. Large running wheel structure; 111. Sun gear; 112. Large running wheel; 113. First outer ring gear; 120. First overrunning clutch; 121. Roller; 122. Spring; 123. First inner ring; 124. Outer ring; 130. Satellite wheel structure; 131. Satellite wheel; 132. Asteroid wheel; 133. Second outer ring gear; 140. Second overrunning clutch; 141. Second inner ring; 150. Cylindrical pin; 160. Planet carrier; 170. Planet shaft; 180. Housing; 181. Installation space; 182. Inlet; 183. Outlet; 184. Machine base; 185. Machine cover; 190. Baffle; 200. Needle roller bearing; 210. Partition. DETAILED DESCRIPTION

[0031] To facilitate understanding of the present invention, a more comprehensive description of the present invention will be provided below with reference to the accompanying drawings. The drawings illustrate preferred embodiments of the present invention. However, the present invention can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided to provide a more thorough and comprehensive understanding of the disclosure of the present invention.

[0032] It should be noted that when an element is referred to as being "fixed to" another element, it may be directly attached to the other element or there may be an intermediate element. When an element is referred to as being "connected to" another element, it may be directly connected to the other element or there may be an intermediate element. The terms "vertical," "horizontal," "left," "right," and similar expressions used herein are for illustrative purposes only.

[0033] Unless otherwise defined, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art to which this invention pertains. The terms used herein in the specification of this invention are for the purpose of describing specific embodiments only and are not intended to limit this invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0034] A planetary gear transmission is a transmission that uses a planetary gear mechanism to achieve speed changes. The planetary gear mechanism is named because it resembles the solar system. Its center is the sun gear, surrounded by several planetary gears that rotate around it, and a common planet carrier is located between the planetary gears. Outside the planetary gears is a large outer ring gear. A planetary gear transmission is a type of gearbox that consists of a planetary outer ring gear, a sun gear, planetary gears (also called satellite gears), and gear axles. Depending on the motion relationship between the outer ring gear, sun gear, and planetary gears, the input shaft and output shaft can be separated from the rigid transmission relationship, the input shaft and output shaft can be driven in the same or opposite directions, and the transmission ratio between the input and output shafts can be changed. A planetary gear mechanism has three moving parts that can rotate relative to each other: the sun gear, the planet carrier, and the outer ring gear.

[0035] An overrunning clutch is a device that utilizes the speed change or rotation direction change of the master and slave parts to have a self-clutching function. It is mainly used for power transmission and separation between the prime mover and the working machine or between the driving shaft and the driven shaft inside the machine. The roller overrunning clutch provided in the embodiment of the present disclosure includes an inner ring, an outer ring and a brake assembly arranged between the inner ring and the outer ring, wherein the brake assembly includes rollers, springs, bearings and other components. When the inner ring rotates clockwise, the roller moves counterclockwise toward the narrow side of the groove under the action of centrifugal force, and is stuck between the outer ring and the inner ring. The friction force of the roller drives the outer ring to rotate. At this time, the overrunning clutch is in a working state. Since the outer ring is fixed to the housing and does not rotate in the embodiment of the present disclosure, when the inner ring and the outer ring are stuck, the inner ring stops rotating. The planetary gear structure drives the inner ring to rotate. The sun gear is the driving gear, which drives the planetary gear to rotate, and then drives the planetary carrier to rotate in the same direction as the sun gear.

[0036] Combine Figures 1 to 9As shown, the disclosed embodiment provides a one-way planetary gear transmission 100, comprising a large traveling gear structure 110, a first overrunning clutch 120, a satellite gear structure 130, a second overrunning clutch 140, and a planet carrier 160. The first overrunning clutch 120 and the second overrunning clutch 140 have identical mechanisms and are installed in pairs in opposite directions. The large traveling gear structure 110 includes a sun gear 111, a large traveling gear 112, and a first outer ring gear 113, which mesh in sequence. The sun gear 111, serving as the input end, meshes externally with the large traveling gear 112, which in turn meshes internally with the first outer ring gear 113. The first outer ring gear 113 is integrally formed with the inner ring (first inner ring 123) of the first overrunning clutch 120 to control the rotation or fixation of the first outer ring gear 113. The first overrunning clutch 120 is sleeved around the large traveling gear structure 110 and comprises a first inner ring 123, an outer ring 124, a spring 122, rollers 121, and bearings. The first inner ring 123 is integrally formed with the first outer ring gear 113. The satellite gear structure 130 includes a meshing asteroid gear 132, a satellite gear 131, and a second outer ring gear 133. The asteroid gear 132 is coaxial with the large traveling wheel 112. A second overrunning clutch 140 is sleeved around the satellite gear structure 130. The inner ring (second inner ring 141) of the second overrunning clutch 140 is integrally formed with the second outer ring gear 133 to control the rotation or fixation of the second outer ring gear 133. The planetary carrier 160 serves as the output terminal. The large traveling wheel 112, the asteroid gear 132, and the satellite gear 131 are all rotatably mounted on the planetary carrier 160. When the sun gear 111 rotates clockwise, it externally meshes with the large travel gear 112, driving the large travel gear 112 to rotate. The large travel gear 112 internally meshes with the first outer ring gear 113, driving the first outer ring gear 113 to rotate counterclockwise. At this time, the first overrunning clutch 120 is locked, immobilizing the first outer ring gear 113. This allows the large travel gear 112 to rotate while simultaneously driving the planet carrier 160 to rotate clockwise for output. At this time, the asteroid gear 132 rotates coaxially with the large travel gear 112, meshing with the satellite gear 131 and driving the satellite gear 131 to rotate. The satellite gear 131 internally meshes with the second outer ring gear 133, driving the second outer ring gear 133 to rotate clockwise, disengaging the second overrunning clutch 140. The second outer ring gear 133 rotates along with the satellite gear 131, and the output planet carrier 160 is driven by the movement of the large travel gear 112 to rotate clockwise for output. When the sun gear 111 rotates counterclockwise, the sun gear 111 is externally meshed with the large traveling wheel 112, driving the large traveling wheel 112 to rotate. The large traveling wheel 112 is internally meshed with the first outer ring gear 113, driving the first outer ring gear 113 to rotate counterclockwise. At this time, the first overrunning clutch 120 is disengaged, allowing the first outer ring gear 113 to rotate along with the large traveling wheel 112.Asteroid gear 132 rotates coaxially with large running gear 112. It meshes with satellite gear 131, driving rotation of satellite gear 131. Satellite gear 131 internally meshes with second outer ring gear 133, driving counterclockwise rotation of second outer ring gear 133, locking second overrunning clutch 140. Second outer ring gear 133 remains stationary, while satellite gear 131 drives planet carrier 160 clockwise. The output planet carrier 160, driven by the movement of satellite gear 131, rotates clockwise, ensuring constant output direction. Changing the direction of sun gear 111 allows for changes in output speed and torque.

[0037] Combine Figure 1 、 Figure 2 、 Figure 3 、 Figure 6 、 Figure 7 and Figure 8 As shown, in some embodiments, there are three large traveling wheels 112, three asteroid wheels 132, and three satellite wheels 131. The three large traveling wheels 112 are arranged around the sun gear 111. The sun gear 111 simultaneously meshes with the outer portions of the three large traveling wheels 112 at their centers, driving the three large traveling wheels 112 to rotate simultaneously. The three planetary wheels are fixedly mounted on the planetary shaft 170. The ends of the planetary shaft 170 are rotatably mounted to the planetary carrier 160 via needle bearings 200. The satellite wheels 131 are spaced circumferentially from the asteroid wheels 132. The asteroid wheels 132 are axially arranged parallel to the large traveling wheels 112. The axis connecting the asteroid wheels 132 and the satellite wheels 131 forms a regular hexagon. The orbital centers of the asteroid wheels 132, large traveling wheels 112, and satellite wheels 131 coincide.

[0038] Combine Figures 1 to 3 As shown, in some embodiments, the one-way planetary gear transmission 100 includes a cylindrical pin 150. Cylindrical pin 150 corresponds to the second planet gear and is fixedly connected to the planet carrier 160. Cylindrical pin 150 and the planet carrier 160 are fixedly connected by an interference fit. The satellite gear 131 is mounted on the cylindrical pin 150 via a needle bearing 200. The planet shaft 170 is rotatably mounted on the planet carrier 160. Both the large planetary gear 112 and the small planetary gear 132 are fixedly connected to the planet shaft 170.

[0039] Combine Figure 1 、 Figure 2 、 Figure 3 As shown, in some embodiments, one end of sun gear 111 corresponds to the rotation center of planet carrier 160 and is rotatably mounted to planet carrier 160 via a bearing. Sun gear 111 is mounted on a stepped shaft. Axially, on the side corresponding to outlet 183, the end of the stepped shaft on which sun gear 111 is mounted is mounted to planet carrier 160 via a bearing, so that the rotation center of planet carrier 160 coincides with the rotation center of sun gear 111. The stepped shaft on the side corresponding to inlet 182 is mounted to engine cover 185 via a bearing.

[0040] Combine Figures 1 to 3 As shown, in some embodiments, a partition plate 210 is provided between the large running wheel 112 and the satellite wheels 131 along the axial direction to prevent the large running wheel 112 and the satellite wheels 131 from interfering with each other in the axial direction.

[0041] Combine Figures 1 to 3 As shown, in some embodiments, the overrunning clutch is a roller 121-type overrunning clutch. The first overrunning clutch 120 and the second overrunning clutch 140 have the same structure. The inner wall of the housing 180 forms an outer ring 124 of the first overrunning clutch 120 and the second overrunning clutch 140, which mates with the first inner ring 123 and the second inner ring 141. Rollers 121 and springs 122 are respectively disposed between the first inner ring 123 and the outer ring 124, and between the second inner ring 141 and the outer ring 124. The overrunning clutch also includes a bearing and a retaining spring. The retaining spring is disposed on one side of the bearing to stop the bearing.

[0042] Combine Figure 1 、 Figure 2 、 Figure 3 and Figure 9 As shown, in some embodiments, the one-way planetary gear transmission 100 further includes a housing 180. The housing 180 defines a tubular installation space 181, and the housing 180 includes an inlet 182 and an outlet 183. The large running wheel structure 110 is installed in the installation space 181 corresponding to the inlet 182. The sun gear 111 is a driving wheel. The planet carrier 160 is installed in the installation space 181 corresponding to the outlet 183. The planet carrier 160 is an output end. The outer rings of the first overrunning clutch 120 and the second overrunning clutch 140 are integrally connected to the side wall of the housing 180. That is, the outer rings 124 of the first overrunning clutch 120 and the second overrunning clutch 140 formed by the inner wall of the housing 180 are fixed. Among them, the housing 180 at the inlet 182 can be connected to the base 184 by screws, and the sun gear 111 can be fixedly connected to the motor shaft through the base 184 to obtain power.

[0043] Combine Figures 1 to 3 As shown, in some embodiments, the one-way planetary gear transmission 100 further includes a blocking plate 190 . The blocking plate 190 is sandwiched between the first outer gear ring 113 and the second outer gear ring 133 to isolate the first outer gear ring 113 from the second outer gear ring 133 .

[0044] Combine Figures 1 to 3As shown, in some embodiments, the one-way planetary gear transmission 100 further includes a base 184 and a cover 185. The base 184 is mounted on the housing 180 corresponding to the inlet 182, and one end of the sun gear 111 is mounted on the base 184 via a bearing corresponding to the inlet 182. The cover 185 is mounted on the housing 180 corresponding to the outlet 183, and the planet carrier 160 is mounted on the cover 185 via a bearing. The one-way planetary gear transmission 100 also includes necessary components such as sealing rings to ensure sealing, which will not be detailed here.

[0045] Combine Figures 1 to 3 As shown, in some embodiments, the base 184 is integrally connected to the housing 180 and the cover 185 by bolts. A single bolt passes from the base 184 through the housing 180 and is screwed into the cover 185, thereby fixing the base 184, the housing 180, and the cover 185 together, thereby increasing the overall consistency of the one-way planetary gear transmission 100.

[0046] For example, the bidirectional planetary gear transmission provided by the embodiment of the present disclosure can be installed according to the following steps:

[0047] Step 1: First install the needle roller bearing 200 and the bearing of the sun gear 111 corresponding to the outlet 183 into the small hole of the planet carrier 160, and then install the needle roller bearing 200 corresponding to the satellite gear 131 into the inner hole of the satellite gear 131.

[0048] Step 2: Place the satellite wheel 131 equipped with the needle bearing 200 in the position to be installed. Note that you should not press-fit it at this time.

[0049] Step 3: Place the large running wheel 112 in the position to be installed, and install the asteroid wheel 132 accordingly, and insert the planetary shaft 170 and the cylindrical pin 150. Note that at this time, the large running wheel 112 must be positioned with the help of a tooling with the same parameters as the first outer gear ring 113 to ensure that the tooth positions of each set of large running wheels 112 and asteroid wheels 132 are consistent. Then use a press to press the asteroid wheel 132 and the cylindrical pin 150 into place together. The press-fit connection here needs to be carried out through an interference fit.

[0050] Step 4: Assemble the overrunning clutch. First, install the bearing of the second overrunning clutch on the housing 180, install the second outer ring gear 133 (second inner ring 141) accordingly, and fix it with screws. Install the spring 122 and the roller 121 into the corresponding mounting grooves of the second outer ring gear 133, install the baffle 190, install the first outer ring gear 113 corresponding to the second outer ring gear 133, install the spring 122 and the roller 121 to the first outer ring gear 113, install the bearing of the first overrunning clutch 120 in place, and fix it with screws.

[0051] Step 5: Install the sun gear 111. Install the bearing of the sun gear 111 corresponding to the inlet 182 to the base 184 and secure it with a retaining ring. Install the sun gear 111.

[0052] Step 6: Install the planet carrier 160 . Install the bearing of the planet carrier 160 corresponding to the inlet 182 to the base 184 , and insert one end of the planet carrier 160 corresponding to the inlet 182 into the corresponding sun gear 111 along the axial direction.

[0053] Step 7: Install the cover 185. Engage the second planetary gear with the second outer ring gear 133, install the bearing of the planetary carrier 160 corresponding to the outlet 183, install the cover 185 to the outlet 183, fix it with screws, and install the seal.

[0054] For example, the working principle of the one-way planetary gear transmission 100 provided in the embodiment of the present disclosure is as follows:

[0055] The housing 180, first outer ring gear 113, bearings, rollers 121, retaining springs, and springs 122 comprise the first overrunning clutch 120. The housing 180, second outer ring gear 133, bearings, rollers 121, retaining springs, and springs 122 comprise the second overrunning clutch 140. The first overrunning clutch 120 and the second overrunning clutch 140 are axially arranged side by side in opposite directions and separated by a retaining plate 190. The sun gear 111 meshes with the large traveling gear 112, which is coaxially fixed with the asteroid gear 132, which meshes with the satellite gear 131. The satellite gear 131 is mounted on the cylindrical pin 150 via a needle roller bearing 200.

[0056] When the sun gear 111 rotates clockwise, the sun gear 111 drives the large travel gear 112 to rotate, and the large travel gear 112 drives the first outer ring gear 113 to rotate in the opposite direction. The first overrunning clutch 120 is locked, the first outer ring gear 113 is fixed and does not rotate, and the large travel gear 112 drives the planetary carrier 160 to rotate counterclockwise. The speed ratio calculation formula at this time is:

[0057] i=Z 行大 / Z 太阳 ×Z 圈1 / Z 行大 ; where Z 行大 is the number of teeth of the large running wheel 112, Z 齿圈1 is the number of teeth of the first outer gear ring 113; Z 太阳 is the number of teeth of the sun gear 111.

[0058] When the sun gear 111 rotates counterclockwise, the two clutches are engaged and disengaged in opposite directions: the second overrunning clutch 140 is locked, and the first overrunning clutch 120 is disengaged. At this point, the sun gear 111 drives the large traveling gear 112, which in turn drives the asteroid gear 132. The asteroid gear 132 drives the satellite gear 131, which in turn drives the planetary carrier 160 counterclockwise. The output end achieves a larger speed ratio and output torque. The speed ratio calculation formula is:

[0059] i=Z 行大 / Z 太阳 ×Z 圈2 / Z 卫 Among them, Z 行大 is the number of teeth of the large running wheel 112; Z 太阳 is the number of teeth of the sun gear 111; Z 卫 is the number of teeth of satellite wheel 131; Z 圈2 The number of teeth of the second outer gear ring 133. In the present invention, the clutch 1 and the clutch 2 must be used in pairs, and the front and rear positions can be reversed, but the directions must be opposite.

[0060] The above description and accompanying drawings sufficiently illustrate the embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other variations. The embodiments represent only possible variations; unless expressly required, individual components and functions are optional, and the order of operations may vary. Portions and features of some embodiments may be included in or substituted for portions and features of other embodiments. Furthermore, the terms used in this application are intended only to describe the embodiments and are not intended to limit the claims. As used in the embodiments and in the claims, the singular forms "a," "an," and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. Similarly, the term "and / or," as used in this application, refers to any and all possible combinations of one or more of the associated listed items. In addition, when used in this application, the terms "comprise" and its variations "comprises" and / or "comprising" refer to the presence of the stated features, integers, steps, operations, elements, and / or components, but do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, and / or groups thereof. In the absence of further limitations, the phrase "comprising a..." does not preclude the presence of other identical elements in the process, method, or device comprising the elements. In this document, each embodiment may focus on the differences from other embodiments, and similar parts between the embodiments can be referenced to each other. For methods, products, etc. disclosed in the embodiments, if they correspond to the method section disclosed in the embodiments, then the relevant parts can be referenced to the description of the method section.

[0061] The embodiments described above only express several implementation methods of the present utility model, and their descriptions are relatively specific and detailed, but they cannot be understood as limiting the scope of the utility model patent. The technical features of the embodiments described above can be combined arbitrarily. In order to make the description concise, not all possible combinations of the various technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification. It should be pointed out that for ordinary technicians in this field, without departing from the concept of the present utility model, several variations and improvements can be made, which all fall within the scope of protection of the present utility model. Therefore, the scope of protection of the utility model patent shall be based on the attached claims.

Claims

1. A one-way planetary gear transmission, characterized in that: include: The large running wheel structure (110) comprises a sun wheel (111), a large running wheel structure (110) and a first outer gear ring (113) that are meshed in sequence; the sun wheel (111) is an input end; A first overrunning clutch (120) is sleeved on the periphery of the large running wheel structure (110), wherein the inner ring of the first overrunning clutch (120) is integrated with the first outer gear ring (113); The satellite wheel structure (130) comprises an asteroid wheel (132), a satellite wheel (131) and a second outer gear ring (133) that are meshed in sequence; wherein the asteroid wheel (132) is coaxial with the large planet wheel structure (110); A second overrunning clutch (140) is sleeved on the periphery of the satellite gear structure (130), wherein the inner ring of the second overrunning clutch (140) is integrated with the second outer gear ring (133); A planetary carrier (160) serves as an output end; the large wheel structure (110), the small planetary wheel (132), and the satellite wheel (131) are all rotatably mounted on the planetary carrier (160); The first overrunning clutch (120) and the second overrunning clutch (140) have the same structure and are installed in opposite directions.

2. The one-way planetary gear transmission according to claim 1, characterized in that: The number of the large traveling wheel structure (110), the asteroid wheel (132), and the satellite wheel (131) is three; the sun wheel (111) is simultaneously engaged with the three large traveling wheel structures (110); The satellite wheels (131) are sequentially spaced from the asteroid wheels (132) along the circumferential direction, and a line connecting the axis centers of the asteroid wheels (132) and the satellite wheels (131) forms a regular hexagon.

3. The one-way planetary gear transmission according to claim 2, characterized in that: include: A cylindrical pin (150) corresponds to the satellite wheel (131) and is fixedly connected to the planetary frame (160); the satellite wheel (131) is mounted on the cylindrical pin (150) via a needle bearing (200); A planetary shaft (170) is rotatably mounted on the planetary frame (160), and the large running wheel structure (110) and the small planetary wheel (132) are both fixedly connected to the planetary shaft (170).

4. The one-way planetary gear transmission according to claim 2, characterized in that: One end of the sun gear (111) corresponds to the rotation center of the planet carrier (160) and is rotatably mounted on the planet carrier (160) via a bearing.

5. The one-way planetary gear transmission according to any one of claims 2 to 4, characterized in that: Along the axial direction, a partition plate (210) is provided between the large traveling wheel structure (110) and the satellite wheel (131).

6. The one-way planetary gear transmission according to any one of claims 2 to 4, characterized in that: The overrunning clutch is a roller (121) type overrunning clutch.

7. The one-way planetary gear transmission according to any one of claims 2 to 4, characterized in that: Also includes: A box body (180) defines a tubular installation space (181), wherein the box body (180) includes an inlet (182) and an outlet (183); The large running wheel structure (110) is installed in the installation space (181) corresponding to the inlet (182); The planet carrier (160) is installed in the installation space (181) corresponding to the outlet (183); The outer rings of the first overrunning clutch (120) and the second overrunning clutch (140) are integrated with the side wall of the housing (180).

8. The one-way planetary gear transmission according to claim 7, characterized in that: Also includes: The baffle (190) is sandwiched between the first outer gear ring (113) and the second outer gear ring (133) to isolate The first outer gear ring (113) and the second outer gear ring (133).

9. The one-way planetary gear transmission according to claim 7, characterized in that: Also includes: The base (184) is mounted on the housing (180) corresponding to the inlet (182), and the sun gear (111) corresponds to One end of the inlet (182) is mounted on the machine base (184) via a bearing; A machine cover (185) is mounted on the box body (180) corresponding to the outlet (183), and the planet carrier (160) is mounted on the machine cover (185) via a bearing.

10. The one-way planetary gear transmission according to claim 9, characterized in that: The machine base (184), the box body (180) and the machine cover (185) are integrally connected by fastening with bolts.

Images