CN112833146A - External meshing planetary gear mechanism with high transmission efficiency - Google Patents
External meshing planetary gear mechanism with high transmission efficiency Download PDFInfo
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- CN112833146A CN112833146A CN202110248405.7A CN202110248405A CN112833146A CN 112833146 A CN112833146 A CN 112833146A CN 202110248405 A CN202110248405 A CN 202110248405A CN 112833146 A CN112833146 A CN 112833146A
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- 230000007246 mechanism Effects 0.000 title claims abstract description 25
- 230000005540 biological transmission Effects 0.000 title claims abstract description 19
- 230000009467 reduction Effects 0.000 description 5
- 239000003638 chemical reducing agent Substances 0.000 description 4
- 238000010586 diagram Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/46—Systems consisting of a plurality of gear trains each with orbital gears, i.e. systems having three or more central gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H1/34—Toothed gearings for conveying rotary motion with gears having orbital motion involving gears essentially having intermeshing elements other than involute or cycloidal teeth
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/08—General details of gearing of gearings with members having orbital motion
- F16H57/082—Planet carriers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H1/00—Toothed gearings for conveying rotary motion
- F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
- F16H2001/289—Toothed gearings for conveying rotary motion with gears having orbital motion comprising two or more coaxial and identical sets of orbital gears, e.g. for distributing torque between the coaxial sets
Abstract
This patent provides a high transmission efficiency's that transmission efficiency is high, axial force is little outer meshing planetary gear mechanism. It includes planet wheel carrier, sun gear, at least a set of planetary gear set, characterized by: each group of planetary gear sets comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are provided with helical teeth on the planetary gear carrier in a rotating way, and the helical directions of two axially adjacent planetary gears are opposite; the sun gear comprises a first helical gear, a second helical gear, a third helical gear and a fourth helical gear which are coaxially and sequentially arranged along the axis and are respectively externally meshed with the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear; the first planetary gear and the fourth planetary gear are fixedly connected, the second planetary gear and the third planetary gear are fixedly connected, and the first planetary gear and the second planetary gear and the third planetary gear and the fourth planetary gear can rotate relatively; the first and second sun gears are fixedly connected, the third and fourth sun gears are fixedly connected, and the first and second sun gears which are fixedly connected coaxially and relatively rotate with the third and fourth sun gears which are fixedly connected.
Description
Technical Field
This patent relates to an external gearing planetary gear mechanism.
Background
With the increasingly wide use of the motor, the speed reducer becomes a key part for matching between the motor and a driving object, the conventional external-meshing cylindrical gear speed reducer is simple to process, low in cost and capable of achieving high precision and efficiency, but the reduction ratio of external-meshing cylindrical gear transmission is small, and the structure is not suitable for the speed reducer with a large transmission ratio. In addition, although the planetary gear structure with the inner gear ring can realize a larger transmission ratio and has a small volume, the inner gear ring is complex in processing technology, high in cost and difficult to achieve high precision. The external meshing planetary gear mechanism has the advantages of the two gears, but when the planetary gears of the gear train are meshed in and out, the planetary gears are under the action of large tooth surface friction force, and the transmission efficiency is low. Although the transmission efficiency of gear engagement is improved by adopting the structure with the helical angles in the opposite rotating directions, the bearing load is large due to the large axial force, and the system efficiency is reduced, so that a speed reducer with small axial force and high efficiency is required.
Disclosure of Invention
The purpose of this patent is to provide a high transmission efficiency's of high transmission efficiency, axial force is little external gearing planetary gear mechanism.
In order to realize the purpose, the technical scheme adopted by the patent is as follows:
the external engagement planetary gear mechanism with high transmission efficiency comprises a planetary gear carrier, a sun gear and at least one group of planetary gear sets, and is characterized in that: each group of planetary gear sets comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are provided with helical teeth on the planetary gear carrier in a rotating way, and the helical directions of two axially adjacent planetary gears are opposite; the sun gear comprises a first helical gear, a second helical gear, a third helical gear and a fourth helical gear which are coaxially and sequentially arranged along the axis and are respectively externally meshed with the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear; the first planetary gear and the fourth planetary gear are fixedly connected, the second planetary gear and the third planetary gear are fixedly connected, and the first planetary gear and the second planetary gear and the third planetary gear and the fourth planetary gear can rotate relatively; the first and second sun gears are fixedly connected, the third and fourth sun gears are fixedly connected, and the first and second sun gears which are fixedly connected coaxially and relatively rotate with the third and fourth sun gears which are fixedly connected.
In the external-engagement planetary gear mechanism, the first planetary gear and the fourth planetary gear are rotationally connected to the planetary gear carrier through the intermediate member, and the first planetary gear and the fourth planetary gear are fixedly connected with each other through the connecting member; the second planetary gear and/or the third planetary gear are rotatably disposed on the connecting member. Preferably, the intermediate member comprises a planetary gear shaft or a planetary gear shaft sleeve, the planetary gear shaft or the planetary gear shaft sleeve is rotatably connected to the planetary gear carrier, the connecting member is the planetary gear shaft or the planetary gear shaft sleeve, and the first planetary gear and the fourth planetary gear are fixedly connected to the planetary gear shaft or the planetary gear shaft sleeve.
In the external meshing planetary gear mechanism, the second sun gear and the third sun gear can freely rotate. Preferably, an axial rotation support is arranged between the second sun gear and the third sun gear.
In the external meshing planetary gear mechanism, axial rotating supports are arranged between the first planetary gear and the second planetary gear and between the third planetary gear and the fourth planetary gear.
In order to achieve the purpose, the patent adopts another technical scheme that:
the external engagement planetary gear mechanism with high transmission efficiency comprises a planetary gear carrier, a sun gear and at least one group of planetary gear sets, and is characterized in that: each group of planetary gear sets comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are rotationally arranged on the planetary gear carrier, and the sun gear comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are respectively externally meshed with the first, second, third and fourth planetary gears; the first planetary gear and the second planetary gear are fixedly connected, the third planetary gear and the fourth planetary gear are fixedly connected, and the second planetary gear and the third planetary gear can rotate relatively; the first and fourth sun gears are fixedly connected, the second and third sun gears are fixedly connected, and the first and fourth sun gears which are fixedly connected coaxially and relatively rotate with the second and third sun gears which are fixedly connected.
In the external-engagement planetary gear mechanism, the first planetary gear and/or the second planetary gear are/is rotationally connected with the planet carrier through an intermediate member, and the third planetary gear and/or the fourth planetary gear are/is rotationally connected with the planet carrier through the intermediate member. Preferably, the first planet gear or/and the second planet gear is/are rotationally connected to the planet gear shaft or the planet gear shaft sleeve, and the third planet gear or/and the fourth planet gear is/are rotationally arranged on the planet gear shaft or the planet gear shaft sleeve; the planet gear shaft or the planet gear shaft sleeve is fixedly connected with the planet gear carrier, and the intermediate member comprises the planet gear shaft or the planet gear shaft sleeve.
In the externally-meshed planetary gear mechanism, the first sun gear and the second sun gear, and the third sun gear and the fourth sun gear can rotate mutually.
The beneficial effect of this patent: therefore, all the planet gears are stressed less, the tooth surface micro-deformation is small, the friction force of the teeth of the planet gears is reduced when the teeth of the planet gears are meshed in and out, and the transmission efficiency is high. Meanwhile, the axial resultant force of the planetary gear is basically zero, and a large bearing is not required to be designed to support the planetary gear shaft or the planetary gear shaft sleeve.
Drawings
FIG. 1 is a schematic diagram of example 1;
FIG. 2 is a force applying schematic diagram of the planetary gear in embodiment 1;
FIG. 3 is a schematic view of example 2;
FIG. 4 is a force applying schematic diagram of the planetary gear in embodiment 2;
FIG. 5 is a schematic view of example 3.
In the figure, a first planetary gear 11, a second planetary gear 12, a third planetary gear 13, a fourth planetary gear 14, a planetary gear connecting pipe 15, a third planetary gear, a fourth planetary,
A first sun gear 21, a second sun gear 22, a third sun gear 23, a fourth sun gear 24, a sun gear connecting pipe 25,
Detailed Description
Example 1:
referring to fig. 1 and 2, the external-engagement planetary gear mechanism with high transmission efficiency includes a planetary carrier, a sun gear, at least one planetary gear set, each planetary gear set includes a first planetary gear 11, a second planetary gear 12, a third planetary gear 13 and a fourth planetary gear 14 which are coaxially arranged in sequence along an axis and are rotatably arranged on the planetary carrier 3, and the gear teeth of two axially adjacent planetary gears are opposite in spiral direction (for example, the gear teeth of the first planetary gear 11 and the third planetary gear 13 are right-handed, and the gear teeth of the second planetary gear 12 and the fourth planetary gear 14 are left-handed); the sun gears comprise a helical first sun gear 21, a second sun gear 22, a third sun gear 23 and a fourth sun gear 24 which are coaxially and sequentially arranged along the axis, and the first planetary gear 11, the second planetary gear 12, the third planetary gear 13 and the fourth planetary gear 14 are externally meshed with the first sun gear 21, the second sun gear 22, the third sun gear 23 and the fourth sun gear 24 respectively.
The first planetary gear 11 and the fourth planetary gear 14 are both fixedly connected to the planetary gear shaft 4. Two ends of the planet gear shaft 4 are rotatably arranged on the planet carrier 3 through bearings. That is, the first planetary gear 11 and the fourth planetary gear 14 are each rotatably connected to the carrier via an intermediate member including the pinion shaft 4, bearings at both ends of the pinion shaft 4, and the like. The planetary gear shaft 4 serves as a connecting member to fixedly connect the first planetary gear with the four planetary gears.
The second planetary gear 12 and the third planetary gear 13 are fixed to a planetary gear connecting pipe 15, and the planetary gear connecting pipe 15 is rotatably provided on the planetary gear shaft 4 through a bearing. Axial rotation supports (such as thrust bearings) 5 are arranged between the first planet gears 11 and the second planet gears 12 and between the third planet gears 13 and the fourth planet gears 14. Of course, the axial rotation support 5 may not be provided between the first planet gear 11 and the second planet gear 12, or between the third planet gear 13 and the fourth planet gear 14, as long as the first planet gear 11 and the second planet gear 12 can relatively rotate around the axis of the planet gear shaft, and the third planet gear 13 and the fourth planet gear 14 can relatively rotate around the axis of the planet gear shaft.
The first sun gear 21, the second sun gear 22 are fixedly connected, the third sun gear 23, the fourth sun gear 24 are fixedly connected, and the planet carrier 3, the fixedly connected first and second sun gears, and the fixedly connected third and fourth sun gears are all relatively rotatable on the same axis (when in use, one of the three components is fixed and the other two components are coaxially rotatable; for example, the fixedly connected third and fourth sun gears are fixed, the planet carrier 3 serves as an input component, and the fixedly connected first and second sun gears 21, 22 serve as an output component and coaxially rotatable with respect to the input component).
An axial rotation support (such as a thrust bearing) 5 is provided between the second sun gear 22 and the third sun gear 23. Of course, the axial rotation support 5 may not be provided between the second sun gear 22 and the third sun gear 23, as long as the second sun gear 22 and the third sun gear 23 can relatively rotate about their coaxial axes.
When the carrier 3 is used as the input member and the first sun gear 21 and the second sun gear 22 connected to each other are fixed as the output member, if the left tooth face of the first pinion 11 is subjected to a normal force of F1, the axial component Z1 of the normal force F1 is downward and the circumferential component Q1 is rightward, see fig. 2; meanwhile, the left side tooth surface of the second planetary gear 12 is subjected to the normal force F2, the axial component force Z2 of the normal force F2 is upward, and the circumferential component force Q2 is rightward; when the right side tooth surface of the third planetary gear 13 is subjected to the normal force F3, the axial component Z3 of the normal force F3 is upward, the circumferential component Q3 is leftward (opposite to the force receiving direction of the first planetary gear 11), and the right side tooth surface of the fourth planetary gear 14 is subjected to the normal force F4, the axial component Z4 of the normal force F4 is downward, and the circumferential component Q4 is rightward (opposite to the force receiving direction of the second planetary gear 12).
The axial component forces Z1, Z2, Z3 and Z4 are substantially equal, so that the resultant force in the axial direction of the pinion shaft 4 is substantially zero. The normal force F1 contributes to the reduction of the normal force F4, and the normal force F2 contributes to the reduction of the normal force F3, so that the stress of each planetary gear is small, the microcosmic deformation of the tooth surface is small, the friction force of the teeth of the planetary gears is reduced when the teeth of the planetary gears are meshed in and out, and the transmission efficiency is high.
Example 2:
referring to fig. 3 and 4, the main difference between the embodiment 2 and the embodiment 1 is that:
the first planet gear 11 and the second planet gear 12 are fixedly connected and are rotatably arranged on the planet gear shaft 4 through a bearing. The third planetary gear 13 and the fourth planetary gear 14 are fixedly connected and are rotatably arranged on the planetary gear shaft 4 through a bearing. Two ends of the planet gear shaft 4 are fixedly connected to the planet carrier 3. That is, the first planetary gear 11 and the second planetary gear 12 which are fixedly connected are rotatably connected to the carrier 3 through the intermediate members such as the pinion shaft 4, the bearings between the pinion shaft 4 and the first planetary gear 11 and the second planetary gear 12, and the like; the third planetary gear 13 and the fourth planetary gear 14 are fixedly connected to each other and rotatably connected to the carrier 3 through intermediate members such as the pinion shaft 4, bearings between the pinion shaft 4 and the third planetary gear 13 and the fourth planetary gear 14, and the like.
An axial rotation support (such as a thrust bearing) 5 is arranged between the second planetary gear 12 and the third planetary gear 13. Of course, the axial rotation support 5 may not be provided between the second planetary gear 12 and the third planetary gear 13, as long as the second planetary gear 12 and the third planetary gear 13 can relatively rotate around the axis of the planetary gear shaft.
The first sun gear 21, the fourth sun gear 24 are fixedly connected, the second sun gear 22, the third sun gear 23 are fixedly connected, and the planet carrier 3, the fixedly connected first and fourth sun gears, and the fixedly connected second and third sun gears are all relatively rotatable on the same axis (in use, one of the three components is fixed and the other two components are coaxially rotatable; for example, the fixedly connected first and fourth sun gears are fixed, the planet carrier 3 serves as an input component, and the fixedly connected second and third sun gears 22, 23 serve as output components and are coaxially rotatable with respect to the input component).
Axial rotation supports (such as thrust bearings) 5 are arranged between the first sun gear 21 and the second sun gear 22, and between the third sun gear 23 and the fourth sun gear 24. Of course, the axial rotation support 5 may not be provided between the first sun gear 21 and the second sun gear 22, or between the third sun gear 23 and the fourth sun gear 24, as long as the first sun gear 21 and the second sun gear 22 are relatively rotatable about their coaxial axes, and the third sun gear 23 and the fourth sun gear 24 are relatively rotatable about their coaxial axes.
The second sun gear 22 and the third sun gear 23 which are fixedly connected are rotatably provided on the outer periphery of the sun gear connecting pipe 25 via bearings, and the sun gear connecting pipe 25 fixedly connects the first sun gear 21 and the fourth sun gear 24 (the sun gear connecting pipe 25 may also be regarded as a part of the first sun gear 21 or the fourth sun gear 24).
When the carrier 3 is used as the input member and the third sun gear 23 and the second sun gear 22, which are connected, are fixed as the output member, if the left tooth face of the first pinion 11 is subjected to a normal force of F1, the axial component Z1 of the normal force F1 is downward and the circumferential component Q1 is rightward, see fig. 4; meanwhile, the right side tooth surface of the second planetary gear 12 is subjected to a normal force F2, the axial component force Z2 of the normal force F2 is downward, and the circumferential component force Q2 is leftward; when the right side tooth surface of the third planetary gear 13 is subjected to the normal force F3, the axial component Z3 of the normal force F3 is upward, the circumferential component Q3 is leftward (opposite to the force receiving direction of the first planetary gear 11), and the left side tooth surface of the fourth planetary gear 14 is subjected to the normal force F4, the axial component Z4 of the normal force F4 is upward, and the circumferential component Q4 is rightward (opposite to the force receiving direction of the second planetary gear 12).
The axial component forces Z1, Z2, Z3 and Z4 are substantially equal, so that the resultant force in the axial direction of the pinion shaft 4 is substantially zero. The normal force F1 contributes to the reduction of the normal force F2, and the normal force F3 contributes to the reduction of the normal force F4, so that the stress of each planetary gear is small, the microcosmic deformation of the tooth surface is small, the friction force of the teeth of the planetary gears is reduced when the teeth of the planetary gears are meshed in and out, and the transmission efficiency is high.
Example 3:
referring to fig. 5, the main difference between embodiment 3 and embodiment 1 is that:
the first planetary gear 11 and the fourth planetary gear 14 are both fixedly connected to the planetary gear shaft sleeve 6, and the planetary gear shaft sleeve 6 is rotatably arranged on the planetary gear shaft 4 through a bearing. The planet gear shaft 4 is fixed at both ends to the planet carrier 3. That is, the first planetary gear 11 and the fourth planetary gear 14 are each rotatably connected to the carrier via intermediate members including the planetary carrier 6, the planetary gear shaft 4, and bearings between the planetary carrier 6 and the planetary gear shaft 4. The planetary carrier 6 serves as a connecting member to fixedly connect the first planetary gear with the four planetary gears.
The second planet gear 12 and the third planet gear 13 are fixed on a planet gear connecting pipe 15, and the planet gear connecting pipe 15 is rotatably arranged on the planet gear shaft sleeve 6 through a bearing. Axial rotation supports (such as thrust bearings) 5 are arranged between the first planet gears 11 and the second planet gears 12 and between the third planet gears 13 and the fourth planet gears 14. Of course, the axial rotation support 5 may not be provided between the first planet gear 11 and the second planet gear 12, or between the third planet gear 13 and the fourth planet gear 14, as long as the first planet gear 11 and the second planet gear 12 can relatively rotate around the axis of the planet gear shaft, and the third planet gear 13 and the fourth planet gear 14 can relatively rotate around the axis of the planet gear shaft.
In this patent, fixed connection between two gears, no matter be fixed connection between two sun gears, still be fixed connection between two planetary gear, both can be two into one for the preparation on same gear, also can be two independent gears through direct or through transition piece indirect connection such as welding, key, riveting.
The specific structure of the planet shafts and the planet carrier does not affect the scope of protection of the claims of this patent.
The planetary gear sets may be at least one set or multiple sets, which does not affect the protection scope of the claims of the present patent.
The specific connection structure of the planetary gear set and the planetary carrier does not affect the protection scope of the claims of the patent.
The external engagement planetary gear mechanism can be fixed by any two rigidly connected sun gears, the output of the other two rigidly connected sun gears and the input of the planet carrier, or fixed by the planet carrier, the input of any one sun gear set and the output of the other sun gear set, which does not affect the protection scope of the claims of the patent.
The specific connection structure between the fixedly connected planetary gears does not affect the protection scope of the patent claims. The specific structure of the rotary support and the axial support between the two groups of planet gears does not influence the protection scope of the patent claims. The specific structure of the fixed connection between the gears does not affect the protection scope of the patent claims.
Claims (10)
1. The external engagement planetary gear mechanism with high transmission efficiency comprises a planetary gear carrier, a sun gear and at least one group of planetary gear sets, and is characterized in that: each group of planetary gear sets comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are provided with helical teeth on the planetary gear carrier in a rotating way, and the helical directions of two axially adjacent planetary gears are opposite; the sun gear comprises a first helical gear, a second helical gear, a third helical gear and a fourth helical gear which are coaxially and sequentially arranged along the axis and are respectively externally meshed with the first planetary gear, the second planetary gear, the third planetary gear and the fourth planetary gear; the first planetary gear and the fourth planetary gear are fixedly connected, the second planetary gear and the third planetary gear are fixedly connected, and the first planetary gear and the second planetary gear and the third planetary gear and the fourth planetary gear can rotate relatively; the first and second sun gears are fixedly connected, the third and fourth sun gears are fixedly connected, and the first and second sun gears which are fixedly connected coaxially and relatively rotate with the third and fourth sun gears which are fixedly connected.
2. The externally meshed planetary gear mechanism as in claim 1, wherein: the first planetary gear and the fourth planetary gear are rotationally connected to the planetary gear carrier through an intermediate component and are fixedly connected with each other; the second planet gears or/and the third planet gears are rotatably arranged on the connecting component.
3. The externally meshed planetary gear mechanism as in claim 2, wherein: the middle component comprises a planetary gear shaft or a planetary gear shaft sleeve, the planetary gear shaft or the planetary gear shaft sleeve is rotationally connected to the planetary gear carrier, the connecting component is the planetary gear shaft or the planetary gear shaft sleeve, and the first planetary gear and the fourth planetary gear are fixedly connected to the planetary gear shaft or the planetary gear shaft sleeve.
4. The externally meshed planetary gear mechanism as in claim 1, wherein: the second and third sun gears can rotate freely.
5. The externally meshed planetary gear mechanism as in claim 4, wherein: an axial rotation support is arranged between the second sun gear and the third sun gear.
6. The externally meshed planetary gear mechanism as in claim 1, wherein: axial rotation supports are arranged between the first planetary gear and the second planetary gear and between the third planetary gear and the fourth planetary gear.
7. The external engagement planetary gear mechanism with high transmission efficiency comprises a planetary gear carrier, a sun gear and at least one group of planetary gear sets, and is characterized in that: each group of planetary gear sets comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are rotationally arranged on the planetary gear carrier, and the sun gear comprises first, second, third and fourth helical gears which are coaxially and sequentially arranged along the axis and are respectively externally meshed with the first, second, third and fourth planetary gears; the first planetary gear and the second planetary gear are fixedly connected, the third planetary gear and the fourth planetary gear are fixedly connected, and the second planetary gear and the third planetary gear can rotate relatively; the first and fourth sun gears are fixedly connected, the second and third sun gears are fixedly connected, and the first and fourth sun gears which are fixedly connected coaxially and relatively rotate with the second and third sun gears which are fixedly connected.
8. The externally meshed planetary gear mechanism as in claim 7, wherein: the first planetary gear or/and the second planetary gear is/are rotationally connected with the planetary carrier through an intermediate component, and the third planetary gear or/and the fourth planetary gear is/are rotationally connected with the planetary carrier through an intermediate component.
9. The externally meshed planetary gear mechanism as in claim 8 wherein: the first planet gear or/and the second planet gear is/are rotationally connected with the planet gear shaft or the planet gear shaft sleeve, and the third planet gear or/and the fourth planet gear is/are rotationally arranged on the planet gear shaft or the planet gear shaft sleeve; the planet gear shaft or the planet gear shaft sleeve is fixedly connected with the planet gear carrier, and the intermediate member comprises the planet gear shaft or the planet gear shaft sleeve.
10. The externally meshed planetary gear mechanism as in claim 7, wherein: the first and second sun gears and the third and fourth sun gears are rotatable with respect to each other.
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| CN202110248405.7A CN112833146A (en) | 2021-03-08 | 2021-03-08 | External meshing planetary gear mechanism with high transmission efficiency |
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| CN202110248405.7A CN112833146A (en) | 2021-03-08 | 2021-03-08 | External meshing planetary gear mechanism with high transmission efficiency |
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