CN113120221A - Heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings - Google Patents

Heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings Download PDF

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Publication number
CN113120221A
CN113120221A CN202110265231.5A CN202110265231A CN113120221A CN 113120221 A CN113120221 A CN 113120221A CN 202110265231 A CN202110265231 A CN 202110265231A CN 113120221 A CN113120221 A CN 113120221A
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China
Prior art keywords
gear
fixed
ring
gear ring
planetary
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CN202110265231.5A
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Chinese (zh)
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CN113120221B (en
Inventor
魏静
李思凡
王靖
郭爱贵
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Pengzhou Intelligent Chuangshi Technology Co ltd
Chongqing University
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Pengzhou Intelligent Chuangshi Technology Co ltd
Chongqing University
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B64—AIRCRAFT; AVIATION; COSMONAUTICS
    • B64C—AEROPLANES; HELICOPTERS
    • B64C3/00—Wings
    • B64C3/38—Adjustment of complete wings or parts thereof
    • B64C3/56—Folding or collapsing to reduce overall dimensions of aircraft
    • 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
    • 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
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Abstract

The invention discloses a heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings, which comprises a primary transmission system and a secondary transmission system; the primary transmission system comprises an input shaft, a sun gear I, a plurality of groups of duplex planetary gears, a fixed gear ring I, an output gear ring I, a planet carrier and a machine base I; the duplex planetary gear comprises a planet, a hollow gear shaft, a planet gear I and a planet gear II which are arranged on the hollow gear shaft at intervals; the secondary transmission system comprises a sun wheel shaft, a sun wheel II, a plurality of groups of triple planetary gears, an output gear ring II, a fixed gear ring III and a machine base II; the triple planetary gear comprises a gear shaft, and a planetary gear III, a planetary gear IV and a planetary gear V which are arranged on the gear shaft at intervals; according to the invention, the primary transmission structure and the secondary transmission structure are connected in series, so that the whole structure is compact, the size and the mass are smaller, and higher transmission ratio and high bearing performance can be realized.

Description

Heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings
Technical Field
The invention belongs to the technical field of aircrafts, and particularly relates to a heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings.
Background
When the aircraft is parked on the ground or on a deck, the wings occupy a large amount of space, which leads to the reduction of the number of aircraft which can be parked in the effective space, and the application of the wing overturning and folding technology for reducing the space for parking the aircraft is provided. Especially, for military aircrafts, more aircrafts can be placed for the maximum increase of the fighting capacity, and meanwhile, for the convenience of transportation and maintenance of the aircrafts, the wing folding technology has very important practical requirements.
The wing turning and folding system generally comprises a wing fixed end (inner wing), a wing movable end (outer wing), a folding mechanism, a driving mechanism, a control system, a locking system and the like. The wing driving mechanism is a key system for turning and folding the wing, and the driving mechanism provides power to drive the folding mechanism to operate, so that the movable end of the wing can be turned, folded and unfolded. The existing driving mechanism usually adopts a hydraulic linear driving or hydraulic motor technology, but the hydraulic driving structure is complex, the required mass and volume are large, and meanwhile, the stability of a hydraulic system is poor, so that the problems that the wings can be blocked in the movement, even the aircraft is damaged and the like can be caused.
There is therefore a need in the art for a rotary mechanism that overcomes the above-mentioned problems.
Disclosure of Invention
The technical scheme adopted for achieving the aim of the invention is that the heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding the wing comprises a primary transmission system and a secondary transmission system.
The primary transmission system comprises an input shaft, a sun gear I, a plurality of groups of duplex planetary gears, a fixed gear ring I, an output gear ring I, a planet carrier and a machine base I.
The input shaft and the sun gear I are of an integrated structure.
The duplex planetary gear comprises a planet, a hollow gear shaft, and a planet gear I and a planet gear II which are arranged on the hollow gear shaft at intervals. And rolling bearings are arranged in inner holes of the planetary gear I and the planetary gear II. And multiple groups of duplex planetary gears are arranged around the sun gear I. Wherein the planet gear I is externally meshed with the sun gear I.
The fixed gear ring I is internally meshed with the planetary gear I. The fixed gear ring I is fixedly connected with the base I, and the fixed gear ring I and the base I are of an integrated structure.
The output gear ring I is internally meshed with the planetary gear II, and an internal spline is processed on a base of the output gear ring I.
A plurality of flexible pin shafts are arranged on the planet carrier. Each flexible pin shaft penetrates through a group of duplex planetary gears and is connected with rolling bearings of inner holes of the planetary gear I and the planetary gear II.
The middle part of the planet carrier is connected with a rotating shaft through a rolling bearing. One end of the rotating shaft is rotatably connected to the sun gear I, and the other end of the rotating shaft is rotatably connected to the output gear ring I.
The secondary transmission system comprises a sun wheel shaft, a sun wheel II, a plurality of groups of triple planetary gears, an output gear ring II, a fixed gear ring III and a machine base II.
One end of the sun wheel shaft is connected with the output gear ring I base through a spline, and the other end of the sun wheel shaft is connected with the sun wheel II.
The triple planetary gear comprises a gear shaft, and a planetary gear III, a planetary gear IV and a planetary gear V which are arranged on the gear shaft at intervals. And multiple groups of the triple planetary gears are arranged around the sun gear II. Wherein, the planet gear IV is externally meshed with the sun gear II. The triple planetary gear is radially supported in a floating mode through two groups of radial support rings.
And the fixed gear ring II is internally meshed with the planetary gear III. The fixed gear ring II is fixedly connected with the base I and is of an integrated structure.
The fixed gear ring III is internally meshed with the planetary gear V. The fixed gear ring III is fixedly connected with the base II, and the fixed gear ring III and the base II are of an integrated structure.
And the outer walls of the fixed gear ring II and the fixed gear ring III are provided with fixed earrings. The fixed earrings are connected with fixed end wings in the wing electric turnover folding system.
The output gear ring II is positioned between the fixed gear ring II and the fixed gear ring III. And the output gear ring II is internally meshed with the planetary gear IV.
And an output ear ring is arranged on the outer wall of the output gear ring II. The output earrings are connected with movable end wings in the wing electric turnover folding system.
Further, the duplex planetary gear has 3 sets. The duplex planetary gear is of an integral structure. The planetary gear I and the planetary gear II form a planetary gear train with small tooth difference.
Further, the fixed gear ring I and the output gear ring I are both of an integrally formed structure.
Further, the triple planetary gear has 6 sets. The triple planetary gear is of an integral structure. The planetary gear III and the planetary gear V have the same gear parameters, and the planetary gear IV, the planetary gear III and the planetary gear V form a planetary gear train with small tooth difference.
Further, the output gear ring II, the fixed gear ring II and the fixed gear ring III are all of an integrally formed structure.
Furthermore, the output gear ring II is provided with a Gray ring on two sides. And the output gear ring II is respectively contacted with the fixed gear ring II and the fixed gear ring III through a sliding sleeve.
The technical effects of the present invention are undoubtedly as follows:
1. the invention adopts a primary transmission structure and a secondary transmission structure which are connected in series, and the two-linked planetary gear train and the triple planetary gear train are both integral part structures; all gear rings, output earrings and fixing earrings in the transmission system adopt an integrally formed structure, so that the whole structure is compact, and the volume and the mass are smaller.
2. Under the condition of comprehensively considering the mass and the volume, higher transmission ratio and high bearing performance can be realized.
3. In the two-stage transmission system, the output gear ring II is a power output gear, and the fixed gear rings II and III on the two sides are constraint fixed gears, so that a stronger supporting effect is provided.
4. In the two-stage transmission system, the triple planetary gear is radially and floatingly supported by two groups of radial support rings, and the structure ensures that the radial stress of an output gear ring II meshed with the triple planetary gear is more balanced.
Drawings
FIG. 1 is a mechanical schematic of the present invention;
FIG. 2 is a schematic cross-sectional view of the present invention;
FIG. 3 is a schematic structural diagram of a one-stage NGWN (I) type transmission system according to embodiment 1 of the present invention;
FIG. 4 is a schematic structural diagram of a two-stage NGWN (III) type transmission system of embodiment 1 of the present invention;
FIG. 5 is a schematic view of the planetary carrier structure of the first-stage NGWN (I) type transmission system of embodiment 1 of the present invention;
FIG. 6 is a schematic structural diagram of a fixed gear ring II and a fixed earring of a two-stage NGWN (III) type transmission system in accordance with embodiment 1 of the present invention;
fig. 7 is a schematic structural diagram of the output ring gear II and the output earring of the present invention.
In the figure: the planetary gear set comprises an input shaft 1, a sun gear I2, a fixed gear ring I3, an output gear ring I4, a planet carrier 5, a flexible pin shaft 51, a machine base I6, a planetary gear I7, a planetary gear II8, a rotating shaft 9, a sun gear shaft 10, a sun gear II11, an output gear ring II12, a fixed gear ring II13, a fixed gear ring III14, a machine base II15, a planetary gear III16, a planetary gear IV17, a planetary gear V18, a radial support ring 19, a fixed lug ring 20, an output lug ring 21 and a Glare ring 22.
Detailed Description
The present invention is further illustrated by the following examples, but it should not be construed that the scope of the above-described subject matter is limited to the following examples. Various substitutions and alterations can be made without departing from the technical idea of the invention and the scope of the invention is covered by the present invention according to the common technical knowledge and the conventional means in the field.
Example 1:
the embodiment discloses a heavy-load high-speed-ratio rotating mechanism for electric wing overturning and folding, and the mechanism comprises a first-stage NGWN (I) type transmission system and a second-stage NGWN (III) type transmission system, which are shown in fig. 1 and 2.
Referring to fig. 3, the one-stage ngwn (I) -type transmission system includes an input shaft 1, a sun gear I2, 3 sets of double planetary gears, a fixed ring gear I3, an output ring gear I4, a carrier 5, and a base I6.
The input shaft 1 and the sun gear I2 are of an integrated structure.
The double planetary gear comprises a planetary gear comprising a hollow gear shaft, and a planetary gear I7 and a planetary gear II8 which are arranged on the hollow gear shaft at intervals. Rolling bearings are mounted in inner holes of the planetary gear I7 and the planetary gear II 8. 3 sets of said double planetary gears are arranged around the sun gear I2. Wherein the planet gear I7 is externally meshed with the sun gear I2. The duplex planetary gear is of an integral part structure. Wherein the planetary gear I7 and the planetary gear II8 form a planetary gear train with small tooth difference.
The stationary ring gear I3 is in internal mesh with the planet gear I7. The fixed gear ring I3 is fixedly connected with the machine base I6, and the fixed gear ring I3 and the machine base I6 form an integrated structure.
The output gear ring I4 is internally meshed with the planetary gear II8, and an internal spline is machined on the base of the output gear ring I4. The sun gear I2, the 3 groups of duplex planet gears, the fixed gear ring I3, the output gear ring I4 and the planet carrier 5 are all positioned in the engine base I6. The fixed gear ring I3 and the output gear ring I4 are both of an integrally formed structure.
Referring to fig. 5, the planet carrier 5 is provided with 3 flexible pins 51. Each flexible pin shaft 51 penetrates through a group of duplex planetary gears and is connected with rolling bearings of inner holes of the planetary gear I7 and the planetary gear II8 to play a supporting role.
The middle part of the planet carrier 5 is connected with a rotating shaft 9 through a rolling bearing. One end of the rotating shaft 9 is rotatably connected to the sun gear I2 through a bearing, and the other end of the rotating shaft is rotatably connected to the output gear ring I4 through a bearing.
Referring to fig. 4, the two-stage ngwn (III) drive train includes a sun gear shaft 10, sun gear II11, 6 sets of triple planetary gears, output ring gear II12, fixed ring gear II13, fixed ring gear III14, and frame II 15.
An involute external spline is processed at one end of the sun gear shaft 10, the external spline of the sun gear shaft 10 is in fit connection with an internal spline of the base of the output gear ring I4, and the other end of the sun gear shaft 10 and the sun gear II11 are integrally formed.
The triple planetary gear comprises a gear shaft, and a planetary gear III16, a planetary gear IV17 and a planetary gear V18 which are arranged on the gear shaft at intervals. 6 sets of the triple planetary gears are arranged around the sun gear II 11. Wherein the planet gear IV17 is externally meshed with the sun gear II 11. The gear shaft is radially supported in a floating mode through two groups of radial support rings 19, the two groups of radial support rings 19 are respectively located on two sides of the sun gear II11, and the two groups of radial support rings have the same effect as the sliding sleeve by means of self rigidity and are not in contact with the sun gear shaft 10. The triple planetary gear is of an integral part structure. Wherein the planet gear III16 and the planet gear V18 have the same gear parameters, and the planet gear IV17, the planet gear III16 and the planet gear V18 form a planetary gear train with small tooth difference. The output gear ring II12, the fixed gear ring II13 and the fixed gear ring III14 are all of an integrally formed structure.
The fixed ring gear II13 is in internal mesh with the planet gear III 16. The fixed gear ring II13 is fixedly connected with the machine base I6 and is of an integrated structure.
The fixed ring gear III14 is in internal mesh with the planetary gear V18. The outer side of the fixed gear ring III14 is fixedly connected with the machine base II15, and the fixed gear ring III14 and the machine base II15 are of an integrated structure.
Referring to fig. 6, the outer walls of the fixed gear ring II13 and the fixed gear ring III14 are both formed with fixed earrings 20. The fixed earrings 20 are connected with fixed end wings in the wing electric turnover folding system.
The output ring gear II12 is located between the fixed ring gear II13 and the fixed ring gear III 14. And the two sides of the output gear ring II12 are provided with the Glare rings 22, and the output gear ring II12 is respectively contacted with the fixed gear ring II13 and the fixed gear ring III14 through sliding sleeves. The output ring gear II12 is in internal mesh with the planet gear IV 17.
Referring to fig. 7, the output ring gear II12 has an output ear ring 21 formed on the outer wall thereof. The output ear ring 21 is connected with the movable end wing in the wing electric turnover folding system.
During transmission, the rotary transmission mechanism for electrically turning and folding the wings is fixedly connected with the fixed ends of the wings through the fixed ring gears II13 and the fixed earrings 20 of the fixed ring gears III14, and meanwhile, power is transmitted to the sun gear I2 through the motor. The sun gear I2 rotates to drive the planet gear I7 and the planet gear II8 to rotate, the output gear ring I4 rotates, power is connected through a spline and transmitted to the sun gear II11, the planet gear III16, the planet gear IV17 and the planet gear V18 rotate, the output gear ring II12 (the output gear ring II12 and the output earring 21 are integrated) rotates, and the movable end of the wing connected with the output earring 21 is driven to rotate, so that the functions of overturning, folding and unfolding of the wing are achieved.
The heavy-load high-speed-ratio rotating mechanism for electric wing turnover folding disclosed by the embodiment adopts a sun gear I2 of a first-stage NGWN (I) type transmission system as a power input gear, an output gear ring II12 of a second-stage NGWN (III) type transmission system as a power output gear, two planetary gear trains are connected in series, so that the transmission ratio range of the whole transmission system is 8000-10000, and the maximum theoretical transmission ratio of a single-stage NGWN (I) planetary reducer and a single-stage NGWN (III) planetary reducer is less than 500; the serial connection of the NGWN (I) planetary gear train and the NGWN (III) planetary gear train can realize higher transmission ratio range and larger output bearing, and has the characteristics of small volume and light weight.
The output gear ring II12 of the two-stage NGWN (III) type transmission system is a power output gear, the fixed ring gear II13 and the fixed ring gear III14 are fixed with the fixed end wing in the wing electric turnover folding system, the gear ring and the fixed ring gear are of an integral structure, the volume and the mass of the system can be effectively reduced, meanwhile, the fixed ring gears on the two sides provide stronger supporting effect for the system, and the maximum rotation angle of the output gear ring can reach 145 degrees.
Example 2:
the embodiment provides a basic implementation manner, and a heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings, which is shown in fig. 1 and fig. 2, includes a primary transmission system and a secondary transmission system.
Referring to fig. 3, the primary type transmission system comprises an input shaft 1, a sun gear I2, 3 sets of duplex planet gears, a fixed ring gear I3, an output ring gear I4, a planet carrier 5 and a machine base I6.
The input shaft 1 and the sun gear I2 are of an integrated structure.
The double planetary gear comprises a planetary gear comprising a hollow gear shaft, and a planetary gear I7 and a planetary gear II8 which are arranged on the hollow gear shaft at intervals. Rolling bearings are mounted in inner holes of the planetary gear I7 and the planetary gear II 8. 3 sets of said double planetary gears are arranged around the sun gear I2. Wherein the planet gear I7 is externally meshed with the sun gear I2.
The stationary ring gear I3 is in internal mesh with the planet gear I7. The fixed gear ring I3 is fixedly connected with the machine base I6, and the fixed gear ring I3 and the machine base I6 form an integrated structure.
The output gear ring I4 is internally meshed with the planetary gear II8, and an internal spline is machined on the base of the output gear ring I4. The sun gear I2, the 3 groups of duplex planet gears, the fixed gear ring I3, the output gear ring I4 and the planet carrier 5 are all positioned in the engine base I6.
Referring to fig. 5, the planet carrier 5 is provided with 3 flexible pins 51. Each flexible pin shaft 51 penetrates through a group of duplex planetary gears and is connected with rolling bearings of inner holes of the planetary gear I7 and the planetary gear II8 to play a supporting role.
The middle part of the planet carrier 5 is connected with a rotating shaft 9 through a rolling bearing. One end of the rotating shaft 9 is rotatably connected to the sun gear I2 through a bearing, and the other end of the rotating shaft is rotatably connected to the output gear ring I4 through a bearing.
Referring to fig. 4, the two-stage transmission system includes a sun gear shaft 10, a sun gear II11, 6 sets of triple planetary gears, an output ring gear II12, a fixed ring gear II13, a fixed ring gear III14, and a base II 15.
An involute external spline is processed at one end of the sun gear shaft 10, the external spline of the sun gear shaft 10 is in fit connection with an internal spline of the base of the output gear ring I4, and the other end of the sun gear shaft 10 and the sun gear II11 are integrally formed.
The triple planetary gear comprises a gear shaft, and a planetary gear III16, a planetary gear IV17 and a planetary gear V18 which are arranged on the gear shaft at intervals. 6 sets of the triple planetary gears are arranged around the sun gear II 11. Wherein the planet gear IV17 is externally meshed with the sun gear II 11. The gear shaft is radially supported in a floating mode through two groups of radial support rings 19, the two groups of radial support rings 19 are respectively located on two sides of the sun gear II11, and the two groups of radial support rings have the same effect as the sliding sleeve by means of self rigidity and are not in contact with the sun gear shaft 10.
The fixed ring gear II13 is in internal mesh with the planet gear III 16. The fixed gear ring II13 is fixedly connected with the machine base I6 and is of an integrated structure.
The fixed ring gear III14 is in internal mesh with the planetary gear V18. The outer side of the fixed gear ring III14 is fixedly connected with the machine base II15, and the fixed gear ring III14 and the machine base II15 are of an integrated structure.
Referring to fig. 6, the outer walls of the fixed gear ring II13 and the fixed gear ring III14 are both formed with fixed earrings 20. The fixed earrings 20 are connected with fixed end wings in the wing electric turnover folding system.
The output ring gear II12 is located between the fixed ring gear II13 and the fixed ring gear III 14. The output ring gear II12 is in internal mesh with the planet gear IV 17.
Referring to fig. 7, the output ring gear II12 has an output ear ring 21 formed on the outer wall thereof. The output ear ring 21 is connected with the movable end wing in the wing electric turnover folding system.
During transmission, the rotary transmission mechanism for electrically turning and folding the wings is fixedly connected with the fixed ends of the wings through the fixed ring gears II13 and the fixed earrings 20 of the fixed ring gears III14, and meanwhile, power is transmitted to the sun gear I2 through the motor. The sun gear I2 rotates to drive the planet gear I7 and the planet gear II8 to rotate, the output gear ring I4 rotates, power is connected through a spline and transmitted to the sun gear II11, the planet gear III16, the planet gear IV17 and the planet gear V18 rotate, the output gear ring II12 (the output gear ring II12 and the output earring 21 are integrated) rotates, and the movable end of the wing connected with the output earring 21 is driven to rotate, so that the functions of overturning, folding and unfolding of the wing are achieved.
The heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding the wings, disclosed by the embodiment, adopts the sun gear I2 of the primary transmission system as a power input gear and the output gear ring II12 of the secondary transmission system as a power output gear, so that a higher transmission ratio range and a larger output bearing can be realized, and meanwhile, the heavy-load high-speed-ratio rotating mechanism has the characteristics of small size and light weight.
The output gear ring II12 of the two-stage transmission system is a power output gear, the fixed ring gear II13 and the fixed ring gear III14 are fixed on the fixed end wing in the wing electric turnover folding system, the ring gear and the ring gear are of an integral structure, the volume and the mass of the system can be effectively reduced, meanwhile, the fixed ring gears on the two sides provide stronger supporting effect for the system, and the maximum rotation angle of the output ring gear can reach 145 degrees.
Example 3:
the main structure of the present embodiment is the same as embodiment 2, and further, the duplex planetary gear is an integral part structure. Wherein the planetary gear I7 and the planetary gear II8 form a planetary gear train with small tooth difference.
Example 4:
the main structure of this embodiment is the same as that of embodiment 2, and further, the fixed gear I3 and the output gear I4 are both integrally formed.
Example 5:
the main structure of the present embodiment is the same as that of embodiment 2, and further, the triple planetary gear is an integral part structure. Wherein the planet gear III16 and the planet gear V18 have the same gear parameters, and the planet gear IV17, the planet gear III16 and the planet gear V18 form a planetary gear train with small tooth difference.
Example 6:
the main structure of this embodiment is the same as that of embodiment 2, and further, the output gear ring II12, the fixed gear ring II13, and the fixed gear ring III14 are all integrally formed structures.
Example 7:
the main structure of this embodiment is the same as that of embodiment 2, further, glary rings 22 are installed on both sides of the output gear ring II12, and the output gear ring II12 is respectively in contact with the fixed gear ring II13 and the fixed gear ring III14 through sliding sleeves.

Claims (6)

1. The utility model provides a big velocity ratio rotary mechanism of heavy load for wing electronic upset is folding which characterized in that: the device comprises a primary transmission system and a secondary transmission system;
the primary transmission system comprises the input shaft (1), a sun gear I (2), a plurality of groups of duplex planetary gears, a fixed gear ring I (3), an output gear ring I (4), a planet carrier (5) and a machine base I (6);
the input shaft (1) and the sun gear I (2) are of an integrated structure;
the duplex planetary gear comprises a planet, a hollow gear shaft, and a planetary gear I (7) and a planetary gear II (8) which are arranged on the hollow gear shaft at intervals; rolling bearings are arranged in inner holes of the planetary gear I (7) and the planetary gear II (8); a plurality of groups of duplex planetary gears are arranged around the sun gear I (2); wherein the planet gear I (7) is externally meshed with the sun gear I (2);
the fixed gear ring I (3) is internally meshed with the planetary gear I (7); the fixed gear ring I (3) is fixedly connected with the base I (6) and is of an integrated structure;
the output gear ring I (4) is internally meshed with the planetary gear II (8), and an internal spline is processed on a base of the output gear ring I (4);
a plurality of flexible pin shafts (51) are arranged on the planet carrier (5); each flexible pin shaft (51) penetrates through a group of duplex planetary gears and is connected with rolling bearings of inner holes of the planetary gears I (7) and the planetary gears II (8);
the middle part of the planet carrier (5) is connected with a rotating shaft (9) through a rolling bearing. One end of the rotating shaft (9) is rotatably connected to the sun gear I (2), and the other end of the rotating shaft is rotatably connected to the output gear ring I (4);
the secondary transmission system comprises a sun gear shaft (10), a sun gear II (11), a plurality of groups of triple planetary gears, an output gear ring II (12), a fixed gear ring II (13), a fixed gear ring III (14) and a machine base II (15);
one end of the sun wheel shaft (10) is connected with the base of the output gear ring I (4) through a spline, and the other end of the sun wheel shaft is connected with the sun wheel II (11);
the triple planetary gear comprises a gear shaft, and a planetary gear III (16), a planetary gear IV (17) and a planetary gear V (18) which are arranged on the gear shaft at intervals; a plurality of groups of the triple planetary gears are arranged around a sun gear II (11); wherein the planet gear IV (17) is externally meshed with the sun gear II (11); the triple planetary gear is radially and floatingly supported by two groups of radial support rings (19);
the fixed gear ring II (13) is internally meshed with a planetary gear III (16); the fixed gear ring II (13) is fixedly connected with the base I (6) and is of an integrated structure;
the fixed gear ring III (14) is internally meshed with a planetary gear V (18); the fixed gear ring III (14) is fixedly connected with the base II (15) and is of an integrated structure;
the outer walls of the fixed gear ring II (13) and the fixed gear ring III (14) are provided with fixed earrings (20); the fixed earrings (20) are connected with fixed end wings in the wing electric turnover folding system;
the output gear ring II (12) is positioned between the fixed gear ring II (13) and the fixed gear ring III (14); the output gear ring II (12) is internally meshed with a planetary gear IV (17);
an output earring (21) is arranged on the outer wall of the output gear ring II (12); the output earrings (21) are connected with movable end wings in the wing electric turnover folding system.
2. The heavy-duty large-speed-ratio rotating mechanism for the electric wing overturning and folding is characterized in that: the duplex planetary gear has 3 groups; the duplex planetary gear is of an integral structure; the planetary gear I (7) and the planetary gear II (8) form a planetary gear train with small tooth difference.
3. The heavy-duty high-speed-ratio rotating mechanism for the electric wing overturning and folding is characterized in that: the fixed gear ring I (3) and the output gear ring I (4) are both of an integrally formed structure.
4. The heavy-duty large-speed-ratio rotating mechanism for the electric wing overturning and folding is characterized in that: the triple planetary gear has 6 sets; the triple planetary gear is of an integral structure; the planetary gear III (16) and the planetary gear V (18) have the same gear parameters, and the planetary gear IV (17), the planetary gear III (16) and the planetary gear V (18) form a planetary gear train with small tooth difference.
5. The heavy-duty large-speed-ratio rotating mechanism for the electric wing overturning and folding is characterized in that: the output gear ring II (12), the fixed gear ring II (13) and the fixed gear ring III (14) are all of an integrally formed structure.
6. The heavy-duty large-speed-ratio rotating mechanism for the electric wing overturning and folding is characterized in that: the output gear ring II (12) is respectively contacted with the fixed gear ring II (13) and the fixed gear ring III (14) through sliding sleeves.
CN202110265231.5A 2021-03-11 2021-03-11 Heavy-load high-speed-ratio rotating mechanism for electrically overturning and folding wings Active CN113120221B (en)

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Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT8420305A0 (en) * 1983-03-31 1984-03-29 Mc Graw Edison Co GEAR TRANSMISSIONS, PARTICULARLY TRANSMISSIONS WHICH INCLUDE A PLURALITY OF COMPOUND SATELLITE GEARS TO DRIVE AN OUTPUT SHAFT
CN1030817A (en) * 1987-07-18 1989-02-01 湖南省机械研究所 Mixed few-differential involute gear epicyclic transmission mechanism and device
CN1067299A (en) * 1991-05-25 1992-12-23 王文贵 Manually and automatic slepless power variable speed case
CN1380503A (en) * 2002-05-23 2002-11-20 王文贵 Manual and automatic stepless power transmission-gear box
CN102022484A (en) * 2010-12-06 2011-04-20 上海锦珠减速器制造有限公司 Three-stage combined planetary speed reducer and realization method thereof
CN201836308U (en) * 2010-10-22 2011-05-18 青岛海力达齿轮箱有限公司 Novel duplex-gear slewing mechanism
CN102265029A (en) * 2008-12-23 2011-11-30 爱罗丁工程有限公司 Planetary gear
CN102518552A (en) * 2011-12-29 2012-06-27 大连华锐重工集团股份有限公司 Yaw drive for wind generating set
CN102817967A (en) * 2011-06-07 2012-12-12 华锐风电科技(集团)股份有限公司 Speed-changing gear device
WO2014082781A1 (en) * 2012-11-29 2014-06-05 Zf Friedrichshafen Ag Gearing unit having a plus gear set
US20190176616A1 (en) * 2016-08-15 2019-06-13 Auburn Gear, Llc Wheel drive transmission
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
CN110626232A (en) * 2018-06-22 2019-12-31 广东肇庆爱龙威机电有限公司 Drive for adjusting the lifting of a vehicle seat and vehicle seat with such a drive
CN111252234A (en) * 2018-12-02 2020-06-09 罗灿 Oblique double-acting wing
CN111486224A (en) * 2020-05-27 2020-08-04 成都飞亚航空设备应用研究所有限公司 Transmission mechanism of wing electric folding system
CN111828551A (en) * 2020-07-09 2020-10-27 成都飞亚航空设备应用研究所有限公司 Electric driving mechanism suitable for wing folding system
US20210047022A1 (en) * 2019-08-13 2021-02-18 Bell Textron, Inc. Tilting wing rotorcrafts and wing rotation systems

Patent Citations (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT8420305A0 (en) * 1983-03-31 1984-03-29 Mc Graw Edison Co GEAR TRANSMISSIONS, PARTICULARLY TRANSMISSIONS WHICH INCLUDE A PLURALITY OF COMPOUND SATELLITE GEARS TO DRIVE AN OUTPUT SHAFT
CN1030817A (en) * 1987-07-18 1989-02-01 湖南省机械研究所 Mixed few-differential involute gear epicyclic transmission mechanism and device
CN1067299A (en) * 1991-05-25 1992-12-23 王文贵 Manually and automatic slepless power variable speed case
CN1380503A (en) * 2002-05-23 2002-11-20 王文贵 Manual and automatic stepless power transmission-gear box
CN102265029A (en) * 2008-12-23 2011-11-30 爱罗丁工程有限公司 Planetary gear
CN201836308U (en) * 2010-10-22 2011-05-18 青岛海力达齿轮箱有限公司 Novel duplex-gear slewing mechanism
CN102022484A (en) * 2010-12-06 2011-04-20 上海锦珠减速器制造有限公司 Three-stage combined planetary speed reducer and realization method thereof
CN102817967A (en) * 2011-06-07 2012-12-12 华锐风电科技(集团)股份有限公司 Speed-changing gear device
CN102518552A (en) * 2011-12-29 2012-06-27 大连华锐重工集团股份有限公司 Yaw drive for wind generating set
WO2014082781A1 (en) * 2012-11-29 2014-06-05 Zf Friedrichshafen Ag Gearing unit having a plus gear set
US20190176616A1 (en) * 2016-08-15 2019-06-13 Auburn Gear, Llc Wheel drive transmission
CN110626232A (en) * 2018-06-22 2019-12-31 广东肇庆爱龙威机电有限公司 Drive for adjusting the lifting of a vehicle seat and vehicle seat with such a drive
CN111252234A (en) * 2018-12-02 2020-06-09 罗灿 Oblique double-acting wing
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
US20210047022A1 (en) * 2019-08-13 2021-02-18 Bell Textron, Inc. Tilting wing rotorcrafts and wing rotation systems
CN111486224A (en) * 2020-05-27 2020-08-04 成都飞亚航空设备应用研究所有限公司 Transmission mechanism of wing electric folding system
CN111828551A (en) * 2020-07-09 2020-10-27 成都飞亚航空设备应用研究所有限公司 Electric driving mechanism suitable for wing folding system

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
严子焜等: "一种用于折叠翼飞机的行星齿轮机构动力学分析", 《机械设计》 *
陈涛等: "机翼折叠机构的设计研究与动力学分析", 《机械设计》 *

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