A combined planetary mechanism reducer assembly

Abstract

The utility model provides a combined planetary mechanism speed reducer assembly relates to planetary mechanism speed reducer technical field, including front planetary gear train component, rear planetary gear train component, motor casing and speed reducer casing, and front planetary gear train component includes sun gear motor shaft, front planetary gear shaft, front planetary gear, front inner gear ring, output gear and front planet carrier, and rear planetary gear train component includes double tooth big gear, rear planet carrier, rear planetary gear shaft, double tooth pinion, rear inner gear ring and output spline, the utility model discloses a combined planetary mechanism speed reducer assembly has the remarkable practical value, and the core advantage lies in can under the premise of guaranteeing power transmission steady, reliable, realizes above 30 transmission ratio, effectively satisfies the use condition of high -speed motor, both avoids the problem of traditional parallel shaft speed reducer transmission ratio deficiency, and ensures that power transmission is not jammed, and there is no load concentration phenomenon under high transmission ratio.

Description

Technical Field

[0001] This utility model mainly relates to the field of planetary mechanism reducer technology, specifically to a combined planetary mechanism reducer assembly. Background Technology

[0002] With the rapid development of the electric vehicle and electric forklift industries, higher demands are being placed on the power performance and structural compactness of drive systems. To achieve high power density in motors, the industry generally optimizes motor performance by increasing motor speed, but this trend presents new challenges to the transmission capacity of the matching reducers.

[0003] Traditional reducers mostly use a parallel shaft structure. This structure is limited by the gear meshing method and layout space, making it difficult to achieve a large transmission ratio and unable to effectively match the working conditions of high-speed motors. When the motor speed increases, traditional parallel shaft reducers are prone to problems such as unstable power transmission and reduced transmission efficiency. In some cases, concentrated loads can even lead to accelerated wear of parts and shorten their service life.

[0004] While some existing planetary gear reducers can achieve large transmission ratios, they often suffer from complex structural designs, such as numerous parts and cumbersome assembly processes. This not only increases manufacturing costs but also reduces the consistency and reliability of mass production, making it difficult to meet the comprehensive requirements of electric vehicles and electric forklifts for reducers that are "highly adaptable, highly stable, and easy to mass-produce." Therefore, there is an urgent need for a reducer assembly with a reasonable structure, reliable transmission, and compatibility with high-speed motors to overcome the shortcomings of existing technologies. Utility Model Content

[0005] 1. The technical problem to be solved by the utility model: This invention provides a combined planetary mechanism reducer assembly to solve the technical problems existing in the background art.

[0006] 2. Technical Solution: To achieve the above objectives, the technical solution provided by this utility model is as follows: a combined planetary mechanism reducer assembly, comprising a front planetary gear train component, a rear planetary gear train component, a motor housing, and a reducer housing. The front planetary gear train component includes a sun gear motor shaft, a front planetary gear shaft, a front planetary gear, a front internal gear ring, an output gear, and a front planetary carrier. The rear planetary gear train component includes a double-toothed large gear, a rear planetary carrier, a rear planetary gear shaft, a double-toothed small gear, a rear internal gear ring, and an output spline. The sun gear of the sun gear motor shaft meshes with several front planetary gears. The front planetary gears are rotatably mounted on the front planetary carrier via the front planetary gear shaft. The front internal gear ring is fixedly connected to the inner side of the motor housing and meshes with the front planetary gears. The double-toothed large gear and double-toothed small gear are an integral design, and both are rotatably mounted on the rear planetary carrier via the rear planetary gear shaft. The rear internal gear ring is fixedly connected to the inner side of the reducer housing and meshes with the double-toothed small gear. The output gear meshes with the double-toothed large gear, realizing the power transmission between the front and rear planetary gear trains.

[0007] Preferably, the output gear and the front planetary carrier are integrated into one piece, and the output spline and the rear planetary carrier are integrated into one piece.

[0008] Preferably, the sun gear motor shaft is an integrated structure of the sun gear structure and the motor shaft, and its axis coincides with the axis of the front planetary carrier.

[0009] Preferably, the front internal gear ring is fixed to the motor housing by bolts or interference fit, and the axis of the front internal gear ring is collinear with the axis of the sun gear motor shaft. The rear internal gear ring is fixed to the reducer housing by bolts or welding, and the axis of the rear internal gear ring coincides with the axis of the rear planetary carrier.

[0010] Preferably, the front planetary gear and the front planetary gear shaft are in clearance fit, and the front planetary gear can rotate around the axis of the front planetary gear shaft and revolve around the axis of the sun gear motor shaft along with the front planetary carrier.

[0011] Preferably, the double-toothed large gear and the double-toothed small gear can rotate synchronously around the axis of the rear planetary gear shaft, and then the planet carrier revolves around the axis of the rear internal gear ring.

[0012] 3. Beneficial effects: Compared with the prior art, the technical solution provided by this utility model has the following advantages: The combined planetary mechanism reducer assembly of this utility model has significant practical value. Its core advantage lies in its ability to achieve a transmission ratio of over 30 while ensuring smooth and reliable power transmission. This effectively meets the operating conditions of high-speed motors. Through the reasonable combination of the front and rear planetary gear trains, and by utilizing the multi-tooth meshing and uniform force characteristics of the planetary gear trains, it avoids the problem of insufficient transmission ratio in traditional parallel shaft reducers and ensures that power transmission is smooth and free from jamming or load concentration at high transmission ratios.

[0013] This invention incorporates an integrated design for several key components, such as the sun gear motor shaft, output gear, and front planetary carrier, reducing the number of parts and assembly errors, and further improving transmission accuracy and structural stability. The overall layout is simple and reasonable, meets standardized production requirements, simplifies manufacturing and assembly processes, reduces production costs, and, combined with the advantage of a high transmission ratio, can fully meet the comprehensive needs of electric vehicles and electric forklifts for reducers, with broad application prospects. Attached Figure Description

[0014] Figure 1 This is a schematic diagram of the overall structure of the present invention from a first angle; Figure 2 This is a schematic diagram of the overall structure of the present invention from a second angle; Figure 3 This is a schematic diagram of the overall structure of the present invention from a third angle; Figure 4 This is a schematic diagram of the rear planetary gear train component structure of this utility model; Figure 5 This is a schematic diagram of the front planetary gear train component structure of this utility model; Figure 6 This is a schematic diagram of the internal structure of the rear planetary gear train component of this utility model; Figure 7 This is a schematic diagram of the overall connection of this utility model.

[0015] Figure label: 1. Sun gear motor shaft; 2. Front planetary gear shaft; 3. Front planetary gear; 4. Front internal gear ring; 5. Output gear; 6. Front planetary carrier; 7. Double-toothed large gear; 8. Rear planetary carrier; 9. Rear planetary gear shaft; 10. Double-toothed small gear; 11. Rear internal gear ring; 12. Output spline. Detailed Implementation

[0016] To facilitate understanding of this utility model, a more comprehensive description of the utility model will be given below with reference to the accompanying drawings, which show several embodiments of the utility model. However, the utility model can be implemented in many different forms and is not limited to the embodiments described herein. Rather, these embodiments are provided so that the disclosure of the utility model will be more thorough and complete.

[0017] In the description of this utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "page", "bottom", "inner", "outer", "clockwise", "counterclockwise", etc., indicating the orientation or positional relationship are based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this utility model and simplifying the description, and are not intended to indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this utility model.

[0018] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of indicated technical features. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this utility model, "a plurality of" means two or more, unless otherwise explicitly specified.

[0019] In this utility model, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," "fixing," and "equipped with" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0020] It should be noted that the structures not described in this utility model are the same as or can be implemented using existing technology, and will not be elaborated here, as they do not involve the design points and improvement directions of this utility model. Example

[0021] See attached document Figures 1-7 A combined planetary gear reducer assembly includes a front planetary gear train component, a rear planetary gear train component, a motor housing, and a reducer housing. The front planetary gear train component includes a sun gear motor shaft 1, a front planetary gear shaft 2, a front planetary gear 3, a front internal gear ring 4, an output gear 5, and a front planetary carrier 6. The rear planetary gear train component includes a double-toothed large gear 7, a rear planetary carrier 8, a rear planetary gear shaft 9, a double-toothed small gear 10, a rear internal gear ring 11, and an output spline 12. The sun gear of the sun gear motor shaft 1 meshes with several front planetary gears 3. The front planetary gears 3 are rotatably mounted on the front planetary carrier 6 via the front planetary gear shaft 2. The front internal gear ring 4 is fixedly connected to the inner side of the motor housing and meshes with the front planetary gears 3. The double-toothed large gear 7 and the double-toothed small gear 10 are designed as a single unit and are rotatably mounted on the rear planetary carrier 8 via the rear planetary gear shaft 9. The rear internal gear ring 11 is fixedly connected to the inner side of the reducer housing and meshes with the double-toothed small gear 10. The output gear 5 meshes with the double-toothed large gear 7 to realize the power transmission between the front planetary gear train and the rear planetary gear train.

[0022] The output gear 5 and the front planetary carrier 6 are integrated into one piece, and the output spline 12 and the rear planetary carrier 8 are integrated into one piece.

[0023] The sun gear motor shaft 1 is an integrated structure of the sun gear structure and the motor shaft, and its axis coincides with the axis of the front planetary carrier 6.

[0024] The front internal gear ring 4 is fixed to the motor housing by bolts or interference fit. The axis of the front internal gear ring 4 is collinear with the axis of the sun gear motor shaft 1. The rear internal gear ring 11 is fixed to the reducer housing by bolts or welding. The axis of the rear internal gear ring 11 coincides with the axis of the rear planetary carrier 8.

[0025] The front planetary gear 3 and the front planetary gear shaft 2 are in clearance fit. The front planetary gear 3 can rotate around the axis of the front planetary gear shaft 2 and revolve around the axis of the sun gear motor shaft 1 along with the front planetary carrier 6.

[0026] The double-toothed large gear 7 and the double-toothed small gear 10 can rotate synchronously around the axis of the rear planetary gear shaft 9, and then the planet carrier 8 revolves around the axis of the rear internal gear ring 11.

[0027] Working principle: The power is generated by a motor driving the sun gear motor shaft 1 to rotate. The sun gear portion of the sun gear motor shaft 1 meshes with the front planetary gear 3. The front planetary gear 3 is rotatably mounted on the front planetary carrier 6 via the front planetary gear shaft 2. Under meshing action, the front planetary gear 3 rotates around the axis of the front planetary gear shaft 2 and simultaneously revolves with the front planetary carrier 6 around the axis of the sun gear motor shaft 1. The front planetary gear 3 meshes with the front internal gear ring 4, which is fixedly connected to the inner side of the motor housing 13. Its axis is collinear with the axis of the sun gear motor shaft 1, acting as a fixing element to constrain the revolution of the front planetary gear 3, so that the power is transmitted to the front planetary carrier 6 via the front planetary gear shaft 2. The sun gear of the sun gear motor shaft 1 is a pinion, and the front planetary gear 3 is a large gear. The sun gear motor shaft 1 is the driving gear on the power input side, and the front planetary gear 3 is the driven gear on the power transmission side. Since the number of teeth on the sun gear motor shaft 1 is less than the number of teeth on the front planetary gear 3, when the two mesh, the rotational speed of the front planetary gear 3 will be lower than that of the sun gear motor shaft 1.

[0028] The front planetary carrier 6 and the output gear 5 are integrated. The output gear 5 meshes with the double-toothed large gear 7, driving the double-toothed large gear 7 to rotate. The double-toothed large gear 7 and the double-toothed small gear 10 are also integrated, and both are rotatably mounted on the rear planetary carrier 8 via the rear planetary gear shaft 9. The double-toothed small gear 10 meshes with the rear internal gear ring 11, which is fixedly connected to the inner side of the reducer housing 14, and its axis coincides with the axis of the rear planetary carrier 8. The output gear 5 moves with the front planetary carrier 6 and is the driving gear in the engagement stage. The double-toothed large gear 7 is the driven gear for the power input of the rear planetary gear train. Because the number of teeth on the output gear 5 is less than the number of teeth on the double-toothed large gear 7, the rotational speed of the double-toothed large gear 7 will be lower than that of the output gear 5 when they mesh.

[0029] Driven by the output gear 5, the double-toothed large gear 7 rotates around the axis of the rear planetary gear shaft 9, while the subsequent planetary carrier 8 revolves around the axis of the rear internal gear ring 11. The double-toothed small gear 10 meshes with the rear internal gear ring 11, transmitting power to the rear planetary carrier 8. Power is transmitted to the rear planetary carrier 8 via the rear planetary gear shaft 9. The rear planetary carrier 8 and the output spline 12 are integrated, and power is ultimately output to the load end through the output spline 12. The entire working process achieves continuous power transmission from the sun gear motor shaft 1 to the output spline 12, with each component working together to complete its rotation and revolution, ensuring a high transmission ratio of over 30 and efficient transmission.

[0030] The tooth profiles of the sun gear 7, the double-toothed large gear 10, the sun gear motor shaft 1, and the front planetary gear 3 can be either spur or helical.

[0031] The above-described embodiments are merely illustrative of certain implementations of this utility model, and their descriptions are relatively specific and detailed. However, they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these modifications and improvements all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model patent should be determined by the appended claims.

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