CN109236970B - Helicopter main reducer based on torque-dividing transmission mechanism - Google Patents
Helicopter main reducer based on torque-dividing transmission mechanism Download PDFInfo
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- CN109236970B CN109236970B CN201811255487.2A CN201811255487A CN109236970B CN 109236970 B CN109236970 B CN 109236970B CN 201811255487 A CN201811255487 A CN 201811255487A CN 109236970 B CN109236970 B CN 109236970B
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- 230000005540 biological transmission Effects 0.000 title claims abstract description 44
- 239000003638 chemical reducing agent Substances 0.000 title claims abstract description 18
- 238000009434 installation Methods 0.000 claims description 3
- 230000000694 effects Effects 0.000 abstract description 2
- 238000010586 diagram Methods 0.000 description 5
- 230000004075 alteration Effects 0.000 description 1
- 238000000354 decomposition reaction Methods 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
- F16H37/0826—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one output shaft
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B64—AIRCRAFT; AVIATION; COSMONAUTICS
- B64D—EQUIPMENT FOR FITTING IN OR TO AIRCRAFT; FLIGHT SUITS; PARACHUTES; ARRANGEMENT OR MOUNTING OF POWER PLANTS OR PROPULSION TRANSMISSIONS IN AIRCRAFT
- B64D31/00—Power plant control systems; Arrangement of power plant control systems in aircraft
- B64D31/14—Transmitting means between initiating means and power plants
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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
- F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
- F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
- F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
- F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
- F16H37/0833—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with arrangements for dividing torque between two or more intermediate shafts, i.e. with two or more internal power paths
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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
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Aviation & Aerospace Engineering (AREA)
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- Gear Transmission (AREA)
Abstract
The invention provides a helicopter main speed reducer based on a torque-dividing transmission mechanism, which relates to the field of helicopter transmission systems.A power is input through two planet carrier shafts, is subjected to torque division through a differential gear train I and a torque-increasing gear train and is transmitted to a bevel gear driving wheel; the bevel gear driving wheel is meshed with a bevel gear driven wheel, and the bevel gear driven wheel is connected with an input sun wheel shaft and inputs power into a differential gear train II; the differential gear train II divides the power to a straight gear lower driving wheel and a straight gear upper driving wheel; the straight gear driving wheel is meshed with a straight gear driven wheel, and the straight gear driven wheel is connected with the upper and lower half herringbone gear driving wheels through an elastic shaft; the herringbone tooth driving wheels input from the left and the right converge power to the herringbone tooth driven wheels, and the power is output through the output shaft. The reducer has strong bearing capacity, large transmission ratio and ideal load balancing effect, and improves the performance of the whole transmission system and the service life of parts.
Description
Technical Field
The invention relates to the field of helicopter transmission systems, in particular to a helicopter main speed reducer based on a torque-dividing transmission mechanism.
Background
Helicopters, as a flexible, versatile, and highly maneuverable vehicle, have been widely used in military, transportation, rescue, and business fields since the past, and have been continuously developed. The traditional helicopter speed reducer is mostly single-path transmission, the mode of using ordinary gear train and planetary gear train combination to decelerate step by step, and this kind of configuration is only applicable to light-duty and small-size helicopter, to large-scale and heavy helicopter, because engine power is big, the transmission system load is big for the speed reducer size and weight increase, vibration noise problem also more outstanding. Therefore, in order to meet the development requirements of the helicopter, a novel speed reducer with strong bearing capacity and large transmission ratio is urgently needed.
The existing speed reducer is easy to lose efficacy due to elastic deformation, manufacturing precision, assembly error and other reasons of components, so that the service life of the speed reducer is greatly reduced.
Disclosure of Invention
The invention aims to provide a helicopter main speed reducer based on a torque-dividing transmission mechanism, which is characterized in that:
the system comprises two sets of branch input systems, four sets of torque-dividing transmission systems, eight sets of torque-dividing input systems and output systems.
Each set of the branch input system comprises an input shaft, a differential gear train I, a shaft sleeve I, a bevel gear II and a bevel gear III
One end of the input shaft is connected with power, and the other end of the input shaft is connected with a differential gear train I. The differential gear train I comprises a planet carrier I, a planet wheel, an inner gear ring and a sun wheel. The input shaft is a rotating shaft of the planet carrier I. The rotating shaft of the sun gear is a shaft I. And a rotating shaft of the inner gear ring is a shaft sleeve I. The input shaft is positioned at one side of the differential gear train I, and the shaft I and the shaft sleeve I are positioned at the other side of the differential gear train I. And the shaft I penetrates through the shaft sleeve I and then is connected with and drives the bevel gear II to rotate. The bevel gear I is arranged on the shaft sleeve I and rotates along with the rotation of the shaft sleeve I. The bevel gear III and the bevel gear I rotate coaxially. The specification and the rotating speed of the bevel gear I and the bevel gear III are the same.
The torque-dividing transmission system comprises a bevel gear, a shaft, a differential gear train II, a shaft sleeve II, a lower gear and an upper gear.
The differential gear train II comprises a lower star wheel, a lower sun wheel, a planet carrier II, an upper star wheel and an upper sun wheel.
The bevel gear is coaxial with the lower sun gear. Planet wheels, namely an upper planet wheel and a lower planet wheel are arranged on the upper portion and the lower portion of the planet carrier II.
The lower sun wheel is meshed with the lower star wheel. The upper star wheel is meshed with the upper sun wheel.
The shaft II is connected with and rotates along with the planet carrier II. And the shaft II penetrates through the shaft sleeve II and is connected with an upper gear. The upper gear rotates with the rotation of the planet carrier II.
And an upper sun gear and a lower gear are arranged on the shaft sleeve II. The shaft sleeve II and the lower gear rotate along with the rotation of the upper sun gear.
The torque-dividing input system comprises a lower bevel gear II, a gear and an upper bevel gear II which are coaxially mounted from bottom to top in sequence. The mounting shafts of the three are elastic shafts. And the lower bevel gear II, the gear and the upper bevel gear II are all connected with the elastic shaft through splines.
The lower helical gear II, the upper helical gear II and the elastic shaft rotate along with the rotation of the gears. After the installation, the rotation directions of the lower bevel gear II and the upper bevel gear II are opposite.
The output system comprises a lower helical gear I and an upper helical gear I which are coaxially arranged. The mounting shafts of the two are output shafts. The output shaft rotates as the lower helical gear I and the upper helical gear I rotate. The rotation directions of the lower helical gear I and the upper helical gear I are opposite.
The two sets of branch input systems are respectively positioned at two sides of the output system.
Each branch input system is provided with two sets of torque-splitting transmission systems. The two sets of torque splitting transmission systems are positioned above the branch input system. One set of bevel gears of the torque-dividing transmission system is meshed with a bevel gear I of the branch input system, and the other set of bevel gears of the torque-dividing transmission system is meshed with a bevel gear III of the branch input system.
Each set of torque-sharing transmission system is provided with two sets of torque-sharing input systems. One set of the torque-dividing input system is meshed with the lower gear, and the other set of the torque-dividing input system is meshed with the upper gear.
Eight sets of torque splitting input systems are arranged around the output system. The lower bevel gear II of each torque-sharing input system is meshed with the lower bevel gear I of the output system. The upper bevel gear II of each torque splitting input system is meshed with the upper bevel gear I of the output system.
Further, the branch input system further comprises a torque increasing gear train.
The torque-increasing gear train comprises a torque-increasing level planet gear I, a planet gear pin shaft, a torque-increasing level planet gear II, a torque-increasing level planet carrier shaft, a torque-increasing level planet carrier, a fixed bevel gear and a shell. The torque-increasing level planet wheel I and the torque-increasing level planet wheel II are the same in size and specification and are respectively arranged at two ends of a planet wheel pin shaft. The fixed bevel gear is fixed on the shell, is concentric with the bevel gear II and has the same size and specification. And the torque-increasing stage planet wheel I and the torque-increasing stage planet wheel II are both meshed with the bevel gear II. And the torque-increasing stage planet wheel I and the torque-increasing stage planet wheel II are both meshed with the fixed bevel gear. The planet wheel pin shaft is connected to a torque-increasing stage planet carrier at one end of a torque-increasing stage planet carrier shaft. The bevel gear II can drive the torque-increasing stage planet carrier shaft to rotate.
The housing has a central through hole. The planet carrier shaft is connected with a bevel gear III after passing through the central through hole. The bevel gear III rotates with the rotation of the carrier shaft.
The bottom of the shell is fixed on the frame.
Further, the lower bevel gear I and the upper bevel gear I of the output system are the upper half and the lower half of a herringbone gear.
The lower gear and the upper gear have the same specification and rotating speed.
Furthermore, the power output by the two sets of power output devices is transmitted to the two sets of branch input systems respectively after passing through the clutch.
The helicopter main reducer based on the torque-dividing transmission mechanism has a large transmission ratio and strong bearing capacity; the power is divided by the branches, the power and the torque on each branch are reduced, and the loads of related parts such as gears are effectively reduced, so that the sizes of the parts are reduced, and the performance of the speed reducer is improved; by utilizing the motion decomposition function of the closed differential gear train and through reasonable design, a single input torque is decomposed into two output torques, and the two output torques are equal, so that the loads between the branches are equal, and the service life of parts is prolonged.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a schematic view of the structure of the present invention shown from another perspective relative to fig. 1.
Fig. 3 is a schematic diagram of the structure of the branch input system.
Fig. 4 is a schematic structural diagram of a torque-splitting transmission system.
Fig. 5 is a schematic structural diagram of the split-twist input system.
Fig. 6 is a schematic diagram of the structure of the output system.
FIG. 7 is a gear train drive diagram of the present invention.
In the figure:
first, branch input system 1:
II, a torque-dividing transmission system 2:
Thirdly, a torque splitting input system 3:
a lower bevel gear II301, an elastic shaft 302, a gear 303 and an upper bevel gear II304
Fourthly, outputting the system 4:
a lower bevel gear I401, an upper bevel gear I402, an output shaft 403.
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:
referring to fig. 1, 2 and 7, a helicopter main reducer based on a torque-splitting transmission mechanism is characterized in that:
the system comprises two sets of branch input systems 1, four sets of torque-dividing transmission systems 2, eight sets of torque-dividing input systems 3 and an output system 4.
Referring to fig. 3, each set of the branched input system 1 includes an input shaft 101, a differential gear train I102, a shaft I103, a sleeve I104, a bevel gear I105, a bevel gear II106, and a bevel gear III 108.
One end of the input shaft 101 is connected with power, and the other end is connected with a differential gear train I102. The differential gear train I102 includes a carrier I1021, a planetary gear 1022, an annular gear 1023, and a sun gear 1024. The input shaft 101 is a rotating shaft of the carrier I1021. The rotating shaft of the sun gear 1024 is the shaft I103. The rotating shaft of the inner gear 1023 is a shaft sleeve I104. The input shaft 101 is located on one side of the differential gear train I102, and the shaft I103 and the sleeve I104 are located on the other side of the differential gear train I102. After the shaft I103 penetrates through the shaft sleeve I104, the bevel gear II106 is connected and driven to rotate. The bevel gear I105 is mounted on the sleeve I104 and rotates with the sleeve I104. The bevel gear III108 rotates coaxially with the bevel gear I105. The specification and the rotating speed of the bevel gear I105 and the bevel gear III108 are the same.
Referring to fig. 4, the torque-splitting transmission system 2 comprises a bevel gear 201, a shaft 202, a differential gear train II203, a shaft II204, a shaft sleeve II205, a lower gear 206 and an upper gear 207.
The differential gear train II203 includes a lower star wheel 2031, a lower sun wheel 2032, a carrier II2033, an upper star wheel 2034, and an upper sun wheel 2035.
The bevel gear 201 is coaxial 202 with the lower sun gear 2032. Planet wheels, namely an upper planet wheel 2034 and a lower planet wheel 2031, are arranged on the upper part and the lower part of the planet carrier II 2033.
The lower sun gear 2032 is engaged with the lower planetary gear 2031. The up-star 2034 is engaged with the upper sun gear 2035.
The shaft II204 is connected to and rotates with the carrier II 2033. After the shaft II204 passes through the shaft sleeve II205, an upper gear 207 is connected. The upper gear 207 rotates as the carrier II2033 rotates.
The sleeve II205 is provided with an upper sun gear 2035 and a lower gear 206. The hub II205 and the lower gear 206 rotate as the upper sun gear 2035 rotates. The shaft sleeve II205 is mounted on the frame through a bearing.
Referring to fig. 5, the torque-splitting input system 3 comprises a lower bevel gear II301, a gear 303 and an upper bevel gear II304 which are coaxially mounted from bottom to top in sequence. The mounting shaft of the three is an elastic shaft 302 (the elastic shaft has elasticity in the circumferential direction, namely, the elastic shaft is of a thin-walled structure, the torsion-resistant section modulus is relatively small, the allowable torsion angle is relatively large, and therefore the gears at the upper end and the lower end are allowed to have a large angle difference in the torsion direction around the axis). The lower bevel gear II301, the gear 303 and the upper bevel gear II304 are all connected with the elastic shaft 302 through splines. The lower bevel gear II301, the gear 303 and the upper bevel gear II304 are mounted on the frame through bearings, and radial force and axial force are borne by the bearings. The elastic shaft 302 is a thin-walled structure, only bears torque, has small torsional rigidity, and can allow a large relative rotation angle between the lower bevel gear II and the upper bevel gear II so as to realize uniform load between the two gears.
The lower helical gear II301, the upper helical gear II304, and the elastic shaft 302 rotate as the gear 303 rotates. After installation, the rotation directions of the lower bevel gear II301 and the upper bevel gear II304 are opposite.
Referring to fig. 6, the output system 4 includes a lower helical gear I401 and an upper helical gear I402, which are coaxially mounted. The mounting shafts of the two are output shafts 403. The output shaft 403 rotates as the lower helical gear I401 and the upper helical gear I402 rotate. The rotation directions of the lower bevel gear I401 and the upper bevel gear I402 are opposite. The output shaft 403 is mounted on the frame by bearings.
The two sets of branch input systems 1 are respectively positioned at two sides of the output system 4.
Each set of branch input system 1 is provided with two sets of torque-splitting transmission systems 2. The two torque splitting transmission systems 2 are arranged above the branch input system 1. One set of bevel gears 201 of the torque-sharing transmission system 2 is meshed with the bevel gears I105 of the branch input system 1, and the other set of bevel gears 201 of the torque-sharing transmission system 2 is meshed with the bevel gears III108 of the branch input system 1.
Each set of torque-sharing transmission system 2 is provided with two sets of torque-sharing input systems 3. One set of the torque-splitting input system 3 has a gear 303 meshed with the lower gear 206, and the other set of the torque-splitting input system 3 has a gear 303 meshed with the upper gear 207.
The output system 4 is surrounded by eight sets of torque splitting input systems 3. The lower bevel gear II301 of each torque splitting input system 3 meshes with the lower bevel gear I401 of the output system 4. The upper bevel gear II304 of each set of torque splitting input system 3 is meshed with the upper bevel gear I402 of the output system 4.
The number of gear teeth of the differential gear train I according to the present embodiment is exemplified:
the number of teeth of the planet gears 1022 is 20, the number of teeth of the sun gear 1024 is 40, and the number of teeth of the inner gear 1023 is 80. Under the condition of the number of teeth, the rotating speed and the torque output by the bevel gear I105 and the bevel gear III108 can be equal.
The number of gear teeth of the differential gear train II according to the present embodiment is exemplified:
the number of teeth of the lower sun gear 2032 is 40, the number of teeth of the lower star gear 2031 is 20, the number of teeth of the upper sun gear 2035 is 30, and the number of teeth of the upper star gear 2034 is 30. Under the condition of the number of teeth, the rotation speed and the torque output by the lower gear 206 and the upper gear 207 can be equalized.
Example 2
The main structure of this embodiment is the same as that of embodiment 1, and further, in order to realize torque increase and speed reduction, i.e. to make the rotation speed and transmission torque of bevel gear I105 and bevel gear III108 equal, the branched input system 1 further comprises a torque increasing gear train 107.
The torque-increasing gear train 107 comprises a torque-increasing stage planet gear I1071, a planet gear pin 1072, a torque-increasing stage planet gear II1073, a torque-increasing stage planet carrier shaft 1074, a torque-increasing stage planet carrier 10741, a fixed bevel gear 1076 and a housing 1075. The torque-increasing level planet wheel I1071 and the torque-increasing level planet wheel II1073 are the same in size and specification and are respectively installed at two ends of a planet wheel pin shaft 1072. The fixed bevel gear 1076 is fixed on the housing 1075, and is concentric with the bevel gear II106 and has the same size and specification. The torque-increasing stage planet gear I1071 and the torque-increasing stage planet gear II1073 are both meshed with the bevel gear II 106. The torque-increasing stage planet gear I1071 and the torque-increasing stage planet gear II1073 are both meshed with a fixed bevel gear 1076. The planet wheel pin shaft 1072 is connected to a torque increasing stage planet carrier 10741 at one end of a torque increasing stage planet carrier shaft 1074. The bevel gear II106 may rotate the torque-increasing stage carrier shaft 1074.
The housing 1075 has a central through hole. The planet carrier shaft 1074, after passing through this central through hole, connects with the bevel gear III 108. The bevel gear III108 rotates as the carrier shaft 1074 rotates.
The bottom of the housing 1075 is fixed to the frame.
Example 3:
the main structure of this embodiment is the same as that of embodiment 2, and further, in order to realize more smooth power transmission, the lower bevel gear I401 and the upper bevel gear I402 of the output system 4 are upper and lower halves of a herringbone gear.
The lower gear 206 and the upper gear 207 have the same specification and rotating speed.
Example 4:
based on the structure of embodiment 3, the load of each branch is reduced, the size of parts is reduced, and the torque of each branch is balanced. Therefore, in the embodiment, the power output by the two helicopter power output devices is transmitted to the two branch input systems 1 and finally to the output shaft 403 respectively after passing through the clutch, so that the reducer has strong bearing capacity, large transmission ratio and ideal load balancing effect, and the performance of the whole transmission system and the service life of parts are improved.
Claims (3)
1. The utility model provides a helicopter main reducer based on divide and turn round drive mechanism which characterized in that:
comprises two sets of branch input systems (1), four sets of torque-sharing transmission systems (2), eight sets of torque-sharing input systems (3) and an output system (4);
each set of the branch input system (1) comprises an input shaft (101), a differential gear train I (102), a shaft I (103), a shaft sleeve I (104), a bevel gear I (105), a bevel gear II (106) and a bevel gear III (108);
one end of the input shaft (101) is connected with power, and the other end of the input shaft is connected with a differential gear train I (102); the differential gear train I (102) comprises a planet carrier I (1021), a planet wheel (1022), an inner gear ring (1023) and a sun wheel (1024); the input shaft (101) is a rotating shaft of a planet carrier I (1021); the rotating shaft of the sun gear (1024) is a shaft I (103); the rotating shaft of the inner gear ring (1023) is a shaft sleeve I (104); the input shaft (101) is positioned at one side of the differential gear train I (102), and the shaft I (103) and the shaft sleeve I (104) are positioned at the other side of the differential gear train I (102); the shaft I (103) penetrates through the shaft sleeve I (104) and then is connected with and drives the bevel gear II (106) to rotate; the bevel gear I (105) is arranged on the shaft sleeve I (104) and rotates along with the rotation of the shaft sleeve I (104); the bevel gear III (108) and the bevel gear I (105) rotate coaxially; the specification and the rotating speed of the bevel gear I (105) and the bevel gear III (108) are the same;
the torque-dividing transmission system (2) comprises a bevel gear (201), a shaft (202), a differential gear train II (203), a shaft II (204), a shaft sleeve II (205), a lower gear (206) and an upper gear (207);
the differential gear train II (203) comprises a lower star wheel (2031), a lower sun wheel (2032), a planet carrier II (2033), an upper star wheel (2034) and an upper sun wheel (2035);
the bevel gear (201) is coaxial (202) with the lower sun gear (2032); planet wheels, namely an upper planet wheel (2034) and a lower planet wheel (2031), are arranged on the upper part and the lower part of the planet carrier II (2033);
the lower sun wheel (2032) is meshed with the lower star wheel (2031); the upper star wheel (2034) is meshed with the upper sun wheel (2035);
the shaft II (204) is connected with and rotates along with the planet carrier II (2033); the shaft II (204) is connected with an upper gear (207) after passing through the shaft sleeve II (205); the upper gear (207) rotates with the rotation of the carrier II (2033);
an upper sun gear (2035) and a lower gear (206) are arranged on the shaft sleeve II (205); the shaft sleeve II (205) and the lower gear (206) rotate along with the rotation of the upper sun gear (2035);
the torque-dividing input system (3) comprises a lower bevel gear II (301), a gear (303) and an upper bevel gear II (304) which are coaxially mounted from bottom to top in sequence; the mounting shafts of the three are elastic shafts (302); the lower bevel gear II (301), the gear (303) and the upper bevel gear II (304) are all connected with the elastic shaft (302) through splines;
the lower bevel gear II (301), the upper bevel gear II (304) and the elastic shaft (302) rotate along with the rotation of the gear (303); after installation, the rotation directions of the lower bevel gear II (301) and the upper bevel gear II (304) are opposite;
the output system (4) comprises a lower helical gear I (401) and an upper helical gear I (402) which are coaxially mounted; the mounting shafts of the two are output shafts (403); an output shaft (403) rotates as the lower helical gear I (401) and the upper helical gear I (402) rotate; the rotation directions of the lower bevel gear I (401) and the upper bevel gear I (402) are opposite;
the two sets of branch input systems (1) are respectively positioned at two sides of the output system (4);
each set of branch input system (1) is provided with two sets of torque-dividing transmission systems (2); the two sets of torque-dividing transmission systems (2) are positioned above the branch input system (1); one set of bevel gears (201) of the torque-sharing transmission system (2) is meshed with a bevel gear I (105) of the branch input system (1), and the other set of bevel gears (201) of the torque-sharing transmission system (2) is meshed with a bevel gear III (108) of the branch input system (1);
each set of torque-sharing transmission system (2) is provided with two sets of torque-sharing input systems (3); one set of the torque-sharing input system (3) is provided with a gear (303) meshed with the lower gear (206), and the other set of the torque-sharing input system (3) is provided with a gear (303) meshed with the upper gear (207);
eight sets of torque splitting input systems (3) are arranged around the output system (4); the lower bevel gear II (301) of each torque-sharing input system (3) is meshed with the lower bevel gear I (401) of the output system (4); the upper bevel gear II (304) of each torque splitting input system (3) is meshed with the upper bevel gear I (402) of the output system (4);
the power output by the two sets of power output devices is transmitted to the two sets of branch input systems (1) after passing through the clutch.
2. The helicopter main reducer based on the torque-splitting transmission mechanism according to claim 1, characterized in that:
the branch input system (1) further comprises a torque increasing gear train (107);
the torque-increasing gear train (107) comprises a torque-increasing stage planet gear I (1071), a planet gear pin shaft (1072), a torque-increasing stage planet gear II (1073), a torque-increasing stage planet carrier shaft (1074), a torque-increasing stage planet carrier (10741), a fixed bevel gear (1076) and a shell (1075); the torque-increasing planetary gear I (1071) and the torque-increasing planetary gear II (1073) are the same in size and specification and are respectively arranged at two ends of a planetary gear pin shaft (1072); the fixed bevel gear (1076) is fixed on the shell (1075) and is concentric with the bevel gear II (106) and has the same size and specification; the torque-increasing stage planet wheel I (1071) and the torque-increasing stage planet wheel II (1073) are both meshed with the bevel gear II (106); the torque-increasing stage planet gear I (1071) and the torque-increasing stage planet gear II (1073) are both meshed with the fixed bevel gear (1076); the planet wheel pin shaft (1072) is connected to a torque-increasing stage planet carrier (10741) at one end of a torque-increasing stage planet carrier shaft (1074); the bevel gear II (106) can drive the torque-increasing stage planet carrier shaft (1074) to rotate;
said housing (1075) having a central through hole; the planet carrier shaft (1074) is connected with a bevel gear III (108) after passing through the central through hole; the bevel gear III (108) rotates as the carrier shaft (1074) rotates;
the bottom of the housing (1075) is fixed to the frame.
3. The helicopter main reducer based on the torque-splitting transmission mechanism according to claim 1, characterized in that: the lower bevel gear I (401) and the upper bevel gear I (402) of the output system (4) are the upper half and the lower half of a herringbone gear;
the lower gear (206) and the upper gear (207) have the same specification and rotating speed.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201811255487.2A CN109236970B (en) | 2018-10-26 | 2018-10-26 | Helicopter main reducer based on torque-dividing transmission mechanism |
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| CN201811255487.2A CN109236970B (en) | 2018-10-26 | 2018-10-26 | Helicopter main reducer based on torque-dividing transmission mechanism |
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| CN111268114B (en) * | 2020-02-27 | 2024-03-01 | 西安工业大学 | Bevel gear coaxial counter-rotating double-rotor transmission mechanism |
| CN111268115B (en) * | 2020-02-27 | 2024-02-27 | 西安工业大学 | Face gear configuration coaxial double-rotor speed-changing transmission mechanism |
| CN113483059A (en) * | 2021-07-07 | 2021-10-08 | 重庆大学 | Torque-dividing transmission speed reducing device for coaxial helicopter |
| CN115432181B (en) * | 2022-10-08 | 2024-04-19 | 重庆大学 | Tilt gyroplane transmission system with input shaft coaxial with rotor shaft |
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| US5813292A (en) * | 1995-12-15 | 1998-09-29 | Sikorsky Aircraft Corporation | Method for fabricating a split path transmission system providing equal torque splitting between the split load paths of each gear train thereof at a predefined operating point |
| US20040211278A1 (en) * | 2003-04-23 | 2004-10-28 | Yuriy Gmirya | Load sharing gear for high torque, split-path transmissions |
| EP1896750A1 (en) * | 2005-06-20 | 2008-03-12 | Tae, Nung Jun | Lever-type gear reducer |
| WO2007135156A1 (en) * | 2006-05-22 | 2007-11-29 | Vestas Wind Systems A/S | A gear system for a wind turbine |
| CN101225870A (en) * | 2008-01-25 | 2008-07-23 | 中国农业大学 | Planetary gear coupling |
| CN103968003B (en) * | 2014-05-20 | 2016-08-24 | 西北工业大学 | An a kind of Helicopter Main Reducer point torsion drive mechanism |
| CN104500655A (en) * | 2014-12-11 | 2015-04-08 | 中国航空动力机械研究所 | Torsion-transmission helicopter reducer |
| CN105383690A (en) * | 2015-11-20 | 2016-03-09 | 西安工业大学 | Face gear and herringbone-tooth cylindrical gear combined four-way branch transmission mechanism |
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