Coaxial and same-frame combined star wheel with small tooth difference speed reducer

Abstract

The utility model discloses a coaxial same frame combination star wheel few tooth difference speed reducer, including box assembly, primary planetary reduction mechanism and two -stage few tooth difference reduction mechanism, and primary planetary reduction mechanism and two -stage few tooth difference reduction mechanism coaxial heart are arranged in box assembly in proper order, the primary planetary reduction mechanism includes the inner tooth ring A, planetary carrier A and input gear shaft of coaxial heart setting, the inner tooth ring A fixedly arranged in the box assembly, the planetary carrier A rotatory mounting is in the box assembly, and a plurality of with the meshing of inner tooth ring A planetary gear is rotatory mounted on planetary carrier A, the input gear shaft rotatory setting is in planetary carrier A, and is engaged with planetary gear, two -stage few tooth difference reduction mechanism includes the inner tooth ring B, inner tooth ring C, output shaft and planetary carrier B of coaxial heart setting, the planetary carrier B rotatory mounting is in the box assembly of planetary carrier A one side, and is transmission connection with planetary carrier A, and planetary carrier A will drive planetary carrier B rotate at the same speed, the utility model discloses unique structure, clever design, not only can effectively solve the problem of big, heavy weight of existing speed reducer, can effectively solve the problem of high manufacturing cost, narrow speed ratio range, big transmission noise of existing speed reducer.

Description

Technical Field

[0001] This utility model belongs to the field of speed reducer technology, specifically relating to a coaxial, frame-connected star wheel speed reducer with small tooth difference. Background Technology

[0002] A planetary gear reducer is a power transmission device designed based on the principle of planetary gear transmission. Its core structure includes a sun gear, planet gears, an internal gear ring, and a planet carrier. During operation, the sun gear drives the planet gears to revolve and rotate around the internal gear ring, and the power is ultimately output through the planet carrier, achieving the core function of "speed reduction and torque increase". In the industrial field, planetary gear reducers are key components for power transmission in mechanical equipment: on the one hand, power sources such as motors typically output high speeds and low torques, which cannot directly meet the equipment's demand for low speeds and high torques, requiring planetary gear reducers to adjust the speed and torque matching; on the other hand, their high transmission efficiency and strong load-bearing capacity ensure minimal power loss and high stability during transmission, making them essential devices for ensuring precise equipment operation and extending service life. They are widely used in power, chemical, mining, and lifting and transportation machinery fields.

[0003] While traditional planetary gear reducers offer stable transmission, their speed ratio range is relatively narrow. To achieve a high speed ratio, multiple reducers need to be connected in series, resulting in a significant increase in overall size. Although low-tooth-difference gear reducers can achieve a high speed ratio through low-tooth-difference meshing, their single-stage transmission load capacity is limited, and they require a dedicated output mechanism, making their structure complex. Furthermore, while some existing low-tooth-difference gear reducers adopt a series design of "planetary reduction + low-tooth-difference reduction", the two mechanisms are independent, resulting in redundant axial dimensions. They require separate molds and step-by-step processing during manufacturing, and also suffer from problems such as high impact and noise during meshing. Utility Model Content

[0004] In view of the defects and problems of existing planetary reducers, this utility model provides a coaxial and frame integrated planetary gear reducer with small tooth difference. The reducer has a unique structure and ingenious design, which can not only effectively solve the problems of large size and heavy weight of existing reducers, but also effectively solve the problems of high manufacturing cost, narrow speed ratio range and high transmission noise of existing reducers.

[0005] The solution adopted by this utility model to solve its technical problem is: a coaxial, co-framed, integrated planetary gear reducer with a small tooth difference, comprising a housing assembly, a first-stage planetary reduction mechanism, and a second-stage small tooth difference reduction mechanism, wherein the first-stage planetary reduction mechanism and the second-stage small tooth difference reduction mechanism are coaxially and sequentially arranged within the housing assembly; the first-stage planetary reduction mechanism includes an internal gear ring A, a planet carrier A, and an input gear shaft arranged coaxially, wherein the internal gear ring A is fixedly arranged within the housing assembly, and the planet carrier A is rotatably mounted within the housing assembly, and multiple planetary gears that mesh with the internal gear ring A are rotatably mounted on the planet carrier A. The input gear shaft is rotatably mounted inside the planet carrier A and meshes with the planetary gears. The two-stage low-tooth-difference reduction mechanism includes an internal gear ring B, an internal gear ring C, an output shaft, and a planet carrier B arranged coaxially. The planet carrier B is rotatably mounted inside a housing assembly on one side of the planet carrier A and is connected to the planet carrier A in a transmission manner. The planet carrier A drives the planet carrier B to rotate at the same speed. The internal gear ring B is fixedly mounted inside the housing assembly, and the internal gear ring C is rotatably mounted inside the housing assembly and is connected to the output shaft in a transmission manner. Multiple planetary gears are rotatably mounted on the planet carrier B, and the planetary gears mesh with the internal gear ring B and the internal gear ring C respectively.

[0006] The tooth tips and roots of the internal gear ring A, planetary gear, internal gear ring B, internal gear ring C, and the integrated gear all adopt a full circular arc structure design.

[0007] The housing assembly includes a housing, a front cover, and a rear cover. The internal gear ring A and internal gear ring B are integrally formed with the housing. The front cover and rear cover are respectively installed at both ends of the housing to form a sealed protection for the first-stage planetary reduction mechanism and the second-stage low-tooth-difference reduction mechanism.

[0008] Multiple planetary gear shafts are evenly spaced along the circumference on the planetary carrier A. One end of the planetary gear shaft is connected to the planetary carrier A, and the other end of the planetary gear shaft is connected to the planetary carrier B. The planetary gears and planetary gears are rotatably mounted on the planetary gear shafts, and the planetary gears and planetary gears are arranged at intervals along the axial direction of the planetary gear shafts.

[0009] The planetary carrier A and planetary carrier B are an integral structure.

[0010] The planetary gear assembly includes gear B and gear C, which are fixed together on the same axis, with gear B having more teeth than gear C.

[0011] The internal gear ring C is integrally formed with the output shaft, and the end of the output shaft away from the planetary carrier is connected to the housing assembly through an output shaft bearing.

[0012] The pairing center distance between the planetary gear and the internal gear ring A is a, the pairing center distance between the integrated gear and the internal gear ring B is b, and the pairing center distance between the integrated gear and the internal gear ring C is c, where a=b=c.

[0013] The internal gear ring A, planetary gear, internal gear ring B, internal gear ring C, and integrated gear all adopt a standard involute gear structure.

[0014] The beneficial effects of this utility model: The coaxial, frame-integrated star wheel reducer with small tooth difference provided by this utility model achieves comprehensive advantages in four aspects: volume control, cost reduction, performance improvement, and scenario adaptability through structural integration and process optimization. Specifically, it includes: 1. The first-stage planetary reduction mechanism and the second-stage low-tooth-difference reduction mechanism share an integrated planetary carrier. Because the center distance of the paired gears is consistent (a=b=c), they share the same planetary gear shaft, eliminating the axial spacing of the independent planetary carrier and the assembly space of the independent gear shaft in the traditional series structure. The axial dimension is smaller than that of the traditional planetary-low-tooth-difference series reducer with the same speed ratio, and the overall volume is significantly reduced compared with the existing planetary reducer of the same power, directly achieving the utility model objective of "reducing volume and weight". The integrated planetary carrier reduces the design and processing of one planetary carrier, and the shared planetary gear shaft eliminates the mold opening and production process of differentiated gear shafts, which not only effectively reduces manufacturing costs but also improves processing efficiency. At the same time, it simplifies the assembly process and further reduces assembly costs.

[0015] 2. The full-circular arc tooth profile avoids the sharp contact between the tooth tip and tooth root of traditional involute gears, reducing tooth surface impact and meshing vibration. The transmission noise is lower than that of traditional reducers, making it suitable for noise-sensitive precision equipment. Furthermore, the full-circular arc structure can effectively disperse tooth root stress, avoid the risk of tooth root fracture, reduce tooth surface wear, improve transmission efficiency, and extend gear service life.

[0016] 3. The output shaft and the rotatable internal gear ring C are integrally formed, and the output shaft bearing is directly installed at the end of the internal gear ring C, forming a rigid support structure of "internal gear ring-output shaft-bearing". The output shaft stiffness is increased by more than 40%, which can withstand greater radial loads and avoid transmission errors caused by output shaft deformation, thus solving the problem of "insufficient output stiffness". The integrated structure eliminates the connecting parts of "output shaft-internal gear ring C" in the traditional solution, further shortening the axial dimension. Combined with the size advantage of the shared planetary carrier, the size of the reducer is minimized under the same power.

[0017] 4. A single-stage planetary reducer is connected in series with a two-stage low-tooth-difference reducer, resulting in a total speed ratio itotal = i1 × i2 × i3, which has a wide range and effectively improves the output torque. In use, it can meet the high reduction ratio requirement without the need for multiple reducers stacked together, effectively solving the problem of narrow speed ratio range and the need for multiple reducers to be connected in series in existing reducers. Under the same speed ratio and output torque, this application, through a three-stage integrated design, has a smaller volume than the traditional "planetary reducer + low-tooth-difference reducer" series scheme. Under the same volume, the output torque is greater than the traditional "planetary reducer + low-tooth-difference reducer" series scheme.

[0018] 5. When the planetary carrier rotates, it is driven synchronously by the integrated gear to reduce the speed of two stages with small tooth difference. This eliminates the need for independent gear shafts and transmission components in the traditional two-stage small tooth difference system, effectively shortening the transmission path, reducing error accumulation, avoiding interference problems in multiple shaft systems, and improving transmission accuracy. Attached Figure Description

[0019] Figure 1 This is a three-dimensional structural diagram of the present invention.

[0020] Figure 2 This is a schematic diagram of the meshing relationship of the internal gear rings of this utility model.

[0021] Figure 3 This is a schematic diagram of the structure of planetary carrier A and planetary carrier B of this utility model.

[0022] Figure 4 This is a schematic diagram of the co-directional output shaft assembly method of this utility model.

[0023] Figure 5 This is a schematic diagram of the bidirectional output shaft assembly method of this utility model.

[0024] Figure 6 This is a schematic diagram of the direct connection assembly method of this utility model.

[0025] In the diagram, the following numbers are used: 11 is the housing, 12 is the front cover of the housing, 13 is the rear cover of the housing, 21 is the internal gear ring A, 22 is the planetary carrier A, 23 is the input gear shaft, 24 is the planetary gear, 31 is the internal gear ring B, 32 is the internal gear ring C, 33 is the output shaft, 34 is the planetary integrated gear, 35 is the planetary carrier B, 341 is the gear B, 342 is the gear C, 4 is the planetary carrier bearing, 5 is the planetary gear shaft, 51 is the planetary bearing, 52 is the integrated bearing, 61 is the output shaft bearing, and 62 is the input shaft bearing. Detailed Implementation

[0026] The present invention will be further described below with reference to the accompanying drawings and embodiments. Example

[0027] This implementation provides a coaxial, frame-mounted, integrated star gear reducer with low tooth difference, such as... Figure 1-3 As shown, the device includes a housing assembly, a first-stage planetary reduction mechanism, and a second-stage low-tooth-difference reduction mechanism, all arranged coaxially. The housing assembly includes a housing 11, a front cover 12, and a rear cover 13. The front cover 12 and the rear cover 13 are respectively installed at both ends of the housing 11. There are various ways to install the front cover 12 and the rear cover 13. In this embodiment, the front cover and the rear cover are directly installed at both ends of the housing by bolts to form a sealed protection for the first-stage planetary reduction mechanism and the second-stage low-tooth-difference reduction mechanism.

[0028] The first-stage planetary reduction mechanism includes an internal gear ring A21, a planet carrier A22, and an input gear shaft 23 arranged coaxially. The internal gear ring A21 is integrally cast with the housing 11 and fixedly installed inside the housing assembly. The planet carrier A22 has a disc-shaped structure and is rotatably mounted inside the housing assembly. There are several ways to install the planet carrier A22, for example: the planet carrier A22 is directly rotatably mounted on the rear end cover 13 of the housing via the planet carrier bearing 4. Multiple planetary gears 24 that mesh with the internal gear ring A21 are rotatably mounted on the planet carrier A22. Specifically: The planetary carrier A22 has multiple planetary gear shafts 5 evenly spaced along the circumference. In this embodiment, three planetary gear shafts are evenly spaced along the circumference. The planetary gear shafts 5 are fixedly connected to the planetary carrier A22. Each planetary gear shaft of the planetary carrier A22 has a planetary gear 24 rotatably mounted on it through a planetary bearing 51. The planetary gears 24 mesh with the internal gear ring A21. The input gear shaft 23 is rotatably disposed in the planetary carrier A22 and meshes with each planetary gear 24. When the input gear shaft is driven to rotate, the input gear shaft will act as the sun gear of the first-stage planetary reduction mechanism to drive each planetary gear to rotate.

[0029] The two-stage low-tooth-difference reduction mechanism includes an internal gear ring B31, an internal gear ring C32, an output shaft 33, and a planetary carrier B35, all coaxially arranged. The planetary carrier B335 is rotatably mounted in a housing assembly on one side of the planetary carrier A22 and is connected to the planetary carrier A22 for transmission. When the planetary carrier A22 rotates, it drives the planetary carrier B35 to rotate at the same speed. The internal gear ring B31 is fixedly mounted in the housing assembly. In this embodiment, the internal gear ring B is the same as the internal gear ring A, both being integrally cast with the housing. The internal gear ring C32 is rotatably mounted in the housing assembly and is connected to the output shaft for transmission. The internal gear ring C32 is integrally formed with the output shaft 33, and the end of the output shaft away from the planetary carrier is connected to the housing assembly through an output shaft bearing 61. Compared with existing reducers, the coaxial, co-mounted, integrated planetary gear low-tooth-difference reducer provided in this embodiment eliminates the connection component of "output shaft-internal gear ring C" in the traditional solution by integrating the internal gear ring C with the output shaft, further shortening the axial dimension. Combined with the size advantage of the shared planetary carrier, the reducer minimizes its volume under the same power.

[0030] Three planetary gears 34 are rotatably mounted on the planetary carrier B35. These planetary gears 34 mesh with internal gear rings B31 and C32, respectively. Each planetary gear 34 includes gears B and C, which are coaxially fixed together. In this embodiment, gears B341 and C342 are an integral structure. Gear B341 has more teeth than gear C342. Gear B of the planetary gear meshes with the internal gear ring B, and gear C of the planetary gear meshes with the internal gear ring C. Specifically: Planetary carrier A22 and planetary carrier B35 are connected together by the same set of planetary gear shafts 5. Three planetary gear shafts 5 are evenly spaced along the circumference on planetary carrier A. One end of the planetary gear shaft 5 is connected to planetary carrier A, and the other end of the planetary gear shaft is connected to planetary carrier B. Planetary gears and planetary gears are rotatably mounted on the planetary gear shafts. The three planetary gears are rotatably mounted on the three planetary gear shafts through planetary bearings. The three planetary gears are rotatably mounted on the three planetary gear shafts through planetary bearings. The planetary gears and planetary gears are arranged at intervals along the axial direction of the planetary gear shafts.

[0031] Furthermore, planetary carrier B and planetary carrier A are an integral structure.

[0032] When the input gear shaft is driven to rotate, it drives the three planetary gears to rotate around their own axes. During this rotation, the planetary gears, constrained by the internal gear ring A, will revolve around the input gear shaft axis, thus driving the planet carrier A to rotate synchronously clockwise, achieving first-stage reduction (speed ratio i1). Simultaneously, the rotation of planet carrier A will drive the planet carrier B to rotate synchronously. The rotation of planet carrier B will drive the three planetary gears to revolve synchronously around the input gear shaft axis. During this process, gear B of the planetary gear set rotates under the constraint of the internal gear ring B, thus driving gear C of the planetary gear set to rotate synchronously, achieving second-stage reduction (speed ratio i2). Gear C of the planetary gear set… During rotation, the internal gear ring C drives the output shaft to rotate, achieving three-stage reduction (speed ratio i3). The total speed ratio itotal = i1 × i2 × i3, thus effectively reducing speed and increasing torque. In use, it can meet the high reduction ratio requirement without the need for multiple reducers to be stacked, effectively solving the problem of narrow speed ratio range and the need for multiple reducers to be connected in series in the existing reducers. Under the same speed ratio and the same output torque, the coaxial and frame integrated planetary gear reducer with small tooth difference provided in this embodiment has a smaller volume than the traditional "planetary reducer + small tooth difference reducer" series scheme through three-stage integrated design. Under the same volume, the output torque is greater than the traditional "planetary reducer + small tooth difference reducer" series scheme.

[0033] The coaxial, coaxial, integrated planetary gear reducer with a small tooth difference provided in this embodiment uses a standard involute gear structure for its internal gear ring A, planetary gears, internal gear ring B, internal gear ring C, and integrated gear. The mating center distance between the planetary gears and internal gear ring A is 'a', the mating center distance between the integrated gears and internal gear ring B is 'b', and the mating center distance between the integrated gears and internal gear ring C is 'c', where a=b=c. The first-stage planetary reduction mechanism and the second-stage small tooth difference reduction mechanism share an integrated planetary carrier, and because the mating gear center distances are consistent (a=b=c), they share the same planetary gear shaft. By eliminating the axial spacing of the independent planetary carrier and the assembly space of the independent gear shaft in the traditional series structure, the axial dimension is smaller than that of the traditional planetary-low tooth difference series reducer with the same speed ratio. The overall volume is significantly reduced compared with the existing planetary reducer of the same power, directly achieving the utility model objective of "reducing volume and weight". The integrated planetary carrier reduces the design and processing of one planetary carrier, and the shared planetary gear shaft eliminates the mold opening and production process of differentiated gear shafts. This not only effectively reduces manufacturing costs but also improves processing efficiency. At the same time, it simplifies the assembly process and further reduces assembly costs.

[0034] The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference provided in this embodiment can be assembled in a manner that suits actual needs. An example is the coaxial output shaft assembly method, such as... Figure 4 As shown, the output shaft is a stepped hollow shaft. The front end of the output shaft 33 is rotatably mounted on the front cover of the housing via two output shaft bearings 61, and the front end of the output shaft 33 extends forward out of the front cover of the housing. The front end of the planetary carrier B35 is rotatably mounted inside the output shaft 33 via planetary carrier bearing 4. The tail end of the planetary carrier A is rotatably mounted on the rear cover of the housing via planetary carrier bearing 4. The tail end of the input gear shaft 23 is rotatably mounted inside the planetary carrier A via input shaft bearing 62. The front end of the input gear shaft 23 passes through the planetary carrier B and the output shaft in sequence and extends out of the housing assembly. The front end of the input gear shaft 23 is rotatably mounted inside the planetary carrier B and the output shaft in sequence via input shaft bearing 62.

[0035] Example 2: Bidirectional output shaft assembly method, such as... Figure 5 As shown, the output shaft is a stepped shaft. The end of the output shaft 33 near the internal gear ring C is directly rotatably mounted in the housing 11 through the output shaft bearing 61. The front end of the output shaft 33 (i.e. the end of the output shaft away from the planetary carrier B) is also rotatably mounted on the front cover of the housing through the output shaft bearing 61, and the front end of the output shaft 33 extends forward out of the front cover of the housing. The front end of the planetary carrier B35 is rotatably mounted in the output shaft 33 through the planetary carrier bearing 4, and the tail end of the planetary carrier A is rotatably mounted on the rear cover of the housing through the planetary carrier bearing 4. The front and rear ends of the input gear shaft 23 are rotatably mounted in the planetary carrier B and the planetary carrier A respectively through the input shaft bearing 62, and the input gear shaft 23 passes through the planetary carrier B and the rear cover of the housing in sequence and extends backward out of the housing assembly.

[0036] Example 3 is a direct-drive assembly method. The difference between Example 3 and Example 2 is that the input gear shaft 23 and the input power source are integrated into one unit. Figure 6 As shown, the input gear shaft 23 passes through the rear end cover of the housing and is directly inserted into the first-stage planetary reduction mechanism, meshing with each planetary gear 24. Example

[0037] The difference between Example 2 and Example 1 is that the tooth tips and roots of the internal gear ring A, planetary gear, internal gear ring B, internal gear ring C, and the integrated gear all adopt a full-circular arc structure design. The full-circular arc tooth profile avoids the sharp contact between the tooth tip and tooth root of traditional involute gears, reduces tooth surface impact and meshing vibration, and has lower transmission noise than traditional reducers, making it suitable for noise-sensitive precision equipment. In addition, the full-circular arc structure can effectively disperse tooth root stress, avoid the risk of tooth root fracture, reduce tooth surface wear, improve transmission efficiency, and extend gear service life.

[0038] It should be understood that the above-described specific embodiments of this utility model are merely illustrative or explanatory of the principles of this utility model, and do not constitute a limitation thereof. Therefore, any modifications, equivalent substitutions, improvements, etc., made without departing from the spirit and scope of this utility model should be included within the protection scope of this utility model.

Claims

1. A coaxial, frame-mounted, integrated star wheel reducer with low tooth difference, characterized in that, The system includes a housing assembly, a first-stage planetary reduction mechanism, and a second-stage low-tooth-difference reduction mechanism. The first-stage and second-stage low-tooth-difference reduction mechanisms are coaxially arranged sequentially within the housing assembly. The first-stage planetary reduction mechanism includes an internal gear ring A, a planet carrier A, and an input gear shaft, all coaxially arranged. The internal gear ring A is fixedly mounted within the housing assembly. The planet carrier A is rotatably mounted within the housing assembly, and multiple planetary gears mesh with the internal gear ring A. The input gear shaft is rotatably mounted within the planet carrier A and meshes with the planetary gears. The second-stage low-tooth-difference reduction mechanism includes an internal gear ring B, an internal gear ring C, an output shaft, and a planet carrier B, all coaxially arranged. The planet carrier B is rotatably mounted within the housing assembly on one side of the planet carrier A and is drive-connected to the planet carrier A. The planet carrier A drives the planet carrier B to rotate at the same speed. The internal gear ring B is fixedly mounted within the housing assembly. The internal gear ring C is rotatably mounted within the housing assembly and is drive-connected to the output shaft. Multiple planetary gears are rotatably mounted on the planet carrier B, and these planetary gears mesh with both the internal gear ring B and the internal gear ring C. Meshing.

2. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The tooth tips and roots of the internal gear ring A, planetary gear, internal gear ring B, internal gear ring C, and the integrated gear all adopt a full circular arc structure design.

3. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The housing assembly includes a housing, a front cover, and a rear cover. The internal gear ring A and internal gear ring B are integrally formed with the housing. The front cover and rear cover are respectively installed at both ends of the housing to form a sealed protection for the first-stage planetary reduction mechanism and the second-stage low-tooth-difference reduction mechanism.

4. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, Multiple planetary gear shafts are evenly spaced along the circumference on the planetary carrier A. One end of the planetary gear shaft is connected to the planetary carrier A, and the other end of the planetary gear shaft is connected to the planetary carrier B. The planetary gears and planetary gears are rotatably mounted on the planetary gear shafts, and the planetary gears and planetary gears are arranged at intervals along the axial direction of the planetary gear shafts.

5. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 4, characterized in that, The planetary carrier A and planetary carrier B are an integral structure.

6. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The planetary gear assembly includes gear B and gear C, which are fixed together on the same axis, with gear B having more teeth than gear C.

7. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The internal gear ring C is integrally formed with the output shaft, and the end of the output shaft away from the planetary carrier is connected to the housing assembly through an output shaft bearing.

8. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The pairing center distance between the planetary gear and the internal gear ring A is a, the pairing center distance between the integrated gear and the internal gear ring B is b, and the pairing center distance between the integrated gear and the internal gear ring C is c, where a=b=c.

9. The coaxial, frame-mounted, integrated star wheel reducer with small tooth difference according to claim 1, characterized in that, The internal gear ring A, planetary gear, internal gear ring B, internal gear ring C, and integrated gear all adopt a standard involute gear structure.

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