CN111520442A - Novel planetary reducer - Google Patents

Novel planetary reducer Download PDF

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Publication number
CN111520442A
CN111520442A CN202010414523.6A CN202010414523A CN111520442A CN 111520442 A CN111520442 A CN 111520442A CN 202010414523 A CN202010414523 A CN 202010414523A CN 111520442 A CN111520442 A CN 111520442A
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CN
China
Prior art keywords
gear
planet
sun
ring
wheel
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Application number
CN202010414523.6A
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Chinese (zh)
Inventor
唐昌宁
杨晓东
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Chengdu Feiya Airborne Equipment Application Research Co ltd
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Chengdu Feiya Airborne Equipment Application Research Co ltd
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Priority to CN202010414523.6A priority Critical patent/CN111520442A/en
Publication of CN111520442A publication Critical patent/CN111520442A/en
Withdrawn legal-status Critical Current

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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
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • 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
    • 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
    • F16H1/32—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • F16H2001/327—Toothed gearings for conveying rotary motion with gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear with orbital gear sets comprising an internally toothed ring gear
    • 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
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F16H2055/176—Ring gears with inner teeth

Abstract

The invention discloses a novel planetary reducer, which comprises an input shaft and a plurality of planetary shafts, wherein the input shaft is provided with a sun wheel set, the novel planetary reducer has better output torque capacity, can obtain a great reduction ratio, improves the bearing capacity of the reducer by dispersing force on more planetary wheels, has a compact structure, and meets the requirement of tooth number Z of a sun wheel A, a gear ring B and a gear ring EA、ZBAnd ZCBe the integral multiple of planet axle number, can guarantee that planet wheel D on same root planet axle is identical with planet wheel C phase difference completely to possess good equal load characteristic, the input-output relation is not unique, can design the novel planetary reducer who satisfies oneself demand as required, planet wheel C equals with planet wheel D phase difference, need not calculate the phase difference of each planet wheel C and planet wheel D, it is convenient, succinct to join in marriage the toothThe cost is saved, and the production efficiency is improved.

Description

Novel planetary reducer
Technical Field
The invention relates to a speed reducer, in particular to a novel planetary speed reducer.
Background
The traditional planetary reducer is mostly accelerated and decelerated step by step and shunted at the same stage. The characteristics of large output torque, small space volume and the like required in the aviation field lead the prior planetary reducer to be insufficient in output torque exposure in application.
In the NGWN type mechanism of the planetary reducer, the reduction ratio is increased, the structure is compact, the volume is reduced, and the NGWN type mechanism is accepted by the aviation field. But the bearing capacity is insufficient and the output torque is limited.
The defects brought by a gear speed increaser system are not overcome, and the capability of shunting large torque in the system is not realized.
Disclosure of Invention
The present invention is directed to a novel planetary reducer to solve the problems set forth in the background art.
In order to achieve the purpose, the invention provides the following technical scheme:
the utility model provides a novel planetary reducer, includes input shaft and a plurality of planet axle, be provided with the sun gear group on the input shaft, a plurality of planet axle middle parts all are provided with planet wheel C and both ends and all are provided with planet wheel D, the input shaft peripheral survey is provided with ring gear B, and ring gear B both sides all are provided with ring gear E, float between sun gear A and the ring gear B and install and be used for carrying out spacing support ring to the planet axle, ring gear B and a plurality of planet wheel C internal gearing, ring gear E and a plurality of its homonymy the planet wheel D internal gearing, sun gear group and planet wheel C or the meshing of planet wheel D, one of them fixed mounting is selected to ring gear B and ring gear E in assembly process.
The sun wheel set comprises a sun wheel A, the sun wheel A is arranged on the input shaft, and the sun wheel A is meshed with the planet wheel C.
The sun wheel set comprises two sun wheels A, the two sun wheels A are both arranged on the input shaft, and the two sun wheels A are respectively meshed with a plurality of planet wheels D on the same side.
And the gear ring B is fixedly installed in the assembling process.
The ring gear E is fixedly mounted during assembly.
And a rocker arm is arranged on the outer side of the gear ring B.
The tooth numbers of the sun gear A, the gear ring B and the gear ring E are integral multiples of the number of the planet shafts.
The invention has the beneficial effects that:
1. the invention has better output torque capacity, can obtain a large reduction ratio, improves the bearing capacity of the reducer by dispersing force on more planet wheels, and has a compact structure.
2. The number of teeth Z of the sun gear A, the gear ring B and the gear ring E needs to be satisfiedA、ZBAnd ZCThe phase difference between the planet wheel D and the planet wheel C on the same planet shaft can be ensured to be completely consistent, and the device has good load-balancing characteristic.
3. The input-output relationship of the planetary speed reducer is not unique, and a novel planetary speed reducer meeting the requirements of the planetary speed reducer can be designed according to the requirements.
4. According to the invention, the phase difference between the planet wheel C and the planet wheel D is equal, the phase difference between each planet wheel C and the planet wheel D does not need to be calculated, the gear matching is convenient and simple, the cost is saved, and the production efficiency is improved.
Drawings
FIG. 1 is a schematic diagram of a prior art NGWN I type transmission;
FIG. 2 is a schematic diagram of a transmission according to a first embodiment of the present invention;
FIG. 3 is a schematic structural diagram according to a first embodiment of the present invention;
FIG. 4 is a schematic diagram of the transmission according to the second embodiment of the present invention;
fig. 5 is a schematic structural diagram of a second embodiment of the present invention.
In the figure, 1-sun gear A, 2-gear ring B, 3-planet gear C, 4-planet gear D, 5-gear ring E, 6-support ring, 7-input shaft, 8-planet shaft, 9-rocker arm, 10-sun gear f, 11-gear ring g, 12-planet gear h, 13-planet gear i, 14-gear ring j and 15-planet carrier k.
Detailed Description
The technical solutions of the present invention are further described in detail below with reference to the accompanying drawings, but the scope of the present invention is not limited to the following.
Referring to fig. 1 of the drawings, a drawing,
the sun gear f10, the planet carrier k15, the ring gear g11 and the ring gear j14 are all free to rotate, i.e. their rotational degrees of freedom are not limited, and the NGWNI-type structure works as long as any of the above parts is fixed during assembly.
Now, the ring gear g11 is fixed, the sun gear f10 is used as an input end, and the transmission path is as follows:
the gear ring g11 is fixed, the input of the sun gear f10 is transmitted to the external meshing planetary gear h12, then transmitted to the planetary gear i13, and finally output through the internal meshing gear ring j14, and the structure and the transmission path of the gear ring g11 show that the gear ring g still has the capability of shunting a large moment in a system.
Through combing analysis, the final output capacity of the conventional NGWN I type planetary reducer is greatly influenced by a final-stage gear ring. The bearing capacity is not effectively improved. By distributing the force over more planet wheels, the bearing capacity of the reducer is improved.
Example one
Referring to fig. 2 to 3, the present embodiment provides a novel planetary reducer, including an input shaft 7 and a plurality of planetary shafts 8, where the input shaft 7 is provided with a sun gear a1, the middle portions of the planetary shafts 8 are provided with planetary gears C3, and both ends of the planetary shafts are provided with planetary gears D4, the outside of the input shaft 7 is provided with a ring gear B2, both sides of the ring gear B2 are provided with ring gears E5, a support ring 6 for limiting the planetary shafts 8 is installed between the sun gear a1 and the ring gear B2 in a floating manner, the ring gear B2 is internally engaged with the planetary gears C3, the ring gear E5 is internally engaged with the planetary gears D4 on the same side, the sun gear a1 is externally engaged with the planetary gears C3, the ring gear B2 is fixedly installed in an assembly process, and the number of teeth of the sun gear a1, the ring gear B2, and the ring gear E5.
The transmission path is as follows:
in this embodiment, ring gear B2 is fixed, sun gear A1 is the input;
the worm gear can be selected as a power input mechanism, power is transmitted to the input shaft 7, the sun gear A1 rotates, the planet gear C3 is driven to rotate, the planet shaft 8 rotates, the planet gears D4 on two sides rotate, and the gear rings E5 on two sides rotate to output power.
The following conditions are satisfied during the assembly process:
1. concentric condition
The standard gear and the high conversion gear need to satisfy the following formula:
mtA(ZA+ZC)＝mtB(ZB-ZC)＝mtE(ZE-ZD)
the angle modified gear needs to satisfy the following formula:
Figure BDA0002494460720000041
the above formulas are all the existing NGWN type I coordination formulas.
2. Conditions of assembly
The number of teeth Z of the sun gear A1, the ring gear B2 and the ring gear E5 is required to be satisfiedA、ZBAnd ZCAre all integer multiples of the number of planet shafts 8.
3. Adjacent condition(s)
According to adjacent conditions of the gears, the following formula is required to be met to ensure that the installation does not interfere:
Zc>Zdtime of flight
Figure BDA0002494460720000042
Zc<ZdTime of flight
Figure BDA0002494460720000043
The above formulas are all the existing NGWN type I coordination formulas.
4. Same phase condition
According to the research calculation, Z needs to be satisfiedA、ZBAnd ZCThe phase difference between the planet wheel D4 on the same planet shaft 8 and the planet wheel C3 is ensured to be completely consistent, and the planet shaft has good uniform load characteristic.
Although the gear ring E5 and the planet wheel D4 meet the NGWN I gear matching relationship;
the sun gear A1, the planet gear C3 and the ring gear B2 meet the NGW gear matching relationship;
because planet wheel C3 all is fixed mounting on same root planet axle 8 with planet wheel D4, if adopt the same planet wheel (planet wheel C3 is the same with planet wheel D4 each item parameter promptly), just need to guarantee that all planet wheels C3 are the same with the angular relation between planet wheel D4, can satisfy the installation.
And then satisfy ZA、ZBAnd ZCThe condition of integral multiple of the number of the planet shafts 8 is adopted, the tooth matching process can be simplified, the cost is saved, and the production efficiency is improved.
Example two
Referring to FIGS. 4 to 5, the following drawings are provided,
different from the first embodiment, the input shaft 7 is provided with two sun gears a1, the two sun gears a1 are respectively meshed with a plurality of planet gears D4 on the same side, the gear ring E5 is fixedly arranged in the assembling process, and the outer side of the gear ring B2 is provided with the rocker arm 9.
The transmission path is as follows:
in this embodiment, ring gear E5 is fixed, sun gear A1 is the input;
the power input mechanism can be selected from a worm gear, power is transmitted to the input shaft 7, the sun gears A1 on two sides rotate, the planet gears D4 on two sides are driven to rotate, the planet shaft 8 rotates, the planet gears C3 rotate, the gear ring B2 rotates, and the power is output by the aid of the rocker arm 9.
The foregoing is illustrative of the preferred embodiments of this invention, and it is to be understood that the invention is not limited to the precise form disclosed herein and that various other combinations, modifications, and environments may be resorted to, falling within the scope of the concept as disclosed herein, either as described above or as apparent to those skilled in the relevant art. And that modifications and variations may be effected by those skilled in the art without departing from the spirit and scope of the invention as defined by the appended claims.

Claims (7)

1. A novel planetary reducer comprises an input shaft (7) and a plurality of planetary shafts (8), and is characterized in that: be provided with the sun gear group on input shaft (7), a plurality of planet axle (8) middle parts all are provided with planet wheel C (3) and both ends all are provided with planet wheel D (4), input shaft (7) peripheral survey is provided with ring gear B (2), and ring gear B (2) both sides all are provided with ring gear E (5), float between sun gear A (1) and ring gear B (2) and install and be used for carrying out spacing support ring (6) to planet axle (8), ring gear B (2) and a plurality of planet wheel C (3) inner gearing, ring gear E (5) and a plurality of its homonymy planet wheel D (4) inner gearing, sun gear group and planet wheel C (3) or planet wheel D (4) meshing, one of them fixed mounting is selected in ring gear B (2) and ring gear E (5) the assembling process.
2. The novel planetary reducer according to claim 1, wherein: the sun wheel set comprises a sun wheel A (1), the sun wheel A (1) is installed on the input shaft (7), and the sun wheel A (1) is meshed with the planet wheel C (3).
3. The novel planetary reducer according to claim 1, wherein: the sun wheel set comprises two sun wheels A (1), the two sun wheels A (1) are installed on the input shaft (7), and the two sun wheels A (1) are respectively meshed with a plurality of planet wheels D (4) on the same side.
4. The novel planetary reducer according to claim 1, wherein: and the gear ring B (2) is fixedly installed in the assembling process.
5. The novel planetary reducer according to claim 1, wherein: the gear ring E (5) is fixedly mounted in the assembly process.
6. The novel planetary reducer according to claim 5, wherein: and a rocker arm (9) is arranged on the outer side of the gear ring B (2).
7. The novel planetary reducer according to claim 1, wherein: the tooth numbers of the sun gear A (1), the gear ring B (2) and the gear ring E (5) are integral multiples of the number of the planet shafts (8).
CN202010414523.6A 2020-05-15 2020-05-15 Novel planetary reducer Withdrawn CN111520442A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113108036A (en) * 2021-03-11 2021-07-13 重庆大学 Modular heavy load big velocity ratio transmission system modular mechanism

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1483949A (en) * 2003-08-09 2004-03-24 宁国聚隆实业有限公司 Multe-gear large transmission ratio single-stage planetary gear wheel speed variator
CN101021245A (en) * 2007-03-21 2007-08-22 重庆大学 Coaxle contrarotating high-speed planetary gear transmission
CN103206491A (en) * 2013-04-18 2013-07-17 新疆金风科技股份有限公司 Speed reducer
CN103403396A (en) * 2011-01-19 2013-11-20 范戴尼超级涡轮有限公司 High torque traction drive
DE102012219215A1 (en) * 2012-10-22 2014-04-24 Schaeffler Technologies Gmbh & Co. Kg Spur gear for use in automotive manufacture application, has coupling planet whose tip cylinder diameter is adjusted such that coaxial cladding circle of circulation axles of head circles of planet is smaller than tip circle of ring wheel
CN104565234A (en) * 2013-10-17 2015-04-29 钱金虎 Transmission with twenty speed ratios
CN207523919U (en) * 2017-11-01 2018-06-22 成都飞亚航空设备应用研究所有限公司 There is the dual output rotary actuator being manually entered
US20190113107A1 (en) * 2017-10-18 2019-04-18 Toyota Jidosha Kabushiki Kaisha Compound planetary gear assembly
CN110030330A (en) * 2019-04-14 2019-07-19 西北工业大学 The multi-joint planetary reduction gear of WW-NGWN differential type
CN212429640U (en) * 2020-05-15 2021-01-29 成都飞亚航空设备应用研究所有限公司 Novel planetary reducer

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1483949A (en) * 2003-08-09 2004-03-24 宁国聚隆实业有限公司 Multe-gear large transmission ratio single-stage planetary gear wheel speed variator
CN101021245A (en) * 2007-03-21 2007-08-22 重庆大学 Coaxle contrarotating high-speed planetary gear transmission
CN103403396A (en) * 2011-01-19 2013-11-20 范戴尼超级涡轮有限公司 High torque traction drive
DE102012219215A1 (en) * 2012-10-22 2014-04-24 Schaeffler Technologies Gmbh & Co. Kg Spur gear for use in automotive manufacture application, has coupling planet whose tip cylinder diameter is adjusted such that coaxial cladding circle of circulation axles of head circles of planet is smaller than tip circle of ring wheel
CN103206491A (en) * 2013-04-18 2013-07-17 新疆金风科技股份有限公司 Speed reducer
CN104565234A (en) * 2013-10-17 2015-04-29 钱金虎 Transmission with twenty speed ratios
US20190113107A1 (en) * 2017-10-18 2019-04-18 Toyota Jidosha Kabushiki Kaisha Compound planetary gear assembly
CN207523919U (en) * 2017-11-01 2018-06-22 成都飞亚航空设备应用研究所有限公司 There is the dual output rotary actuator being manually entered
CN110030330A (en) * 2019-04-14 2019-07-19 西北工业大学 The multi-joint planetary reduction gear of WW-NGWN differential type
CN212429640U (en) * 2020-05-15 2021-01-29 成都飞亚航空设备应用研究所有限公司 Novel planetary reducer

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113108036A (en) * 2021-03-11 2021-07-13 重庆大学 Modular heavy load big velocity ratio transmission system modular mechanism

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Application publication date: 20200811