CN113007290B - Variable speed transmission system - Google Patents

Variable speed transmission system Download PDF

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Publication number
CN113007290B
CN113007290B CN202110197653.3A CN202110197653A CN113007290B CN 113007290 B CN113007290 B CN 113007290B CN 202110197653 A CN202110197653 A CN 202110197653A CN 113007290 B CN113007290 B CN 113007290B
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China
Prior art keywords
planetary gear
gear train
transmission
planet
gear
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CN113007290A (en
Inventor
鲍和云
杨星光
李晗
罗志洋
周涛
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Nanjing University of Aeronautics and Astronautics
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Nanjing University of Aeronautics and Astronautics
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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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • 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
    • B64D35/00—Transmitting power from power plants to propellers or rotors; Arrangements of transmissions
    • B64D35/04—Transmitting power from power plants to propellers or rotors; Arrangements of transmissions characterised by the transmission driving a plurality of propellers or rotors
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/082—Planet carriers
    • 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
    • F16H2057/087—Arrangement and support of friction devices in planetary gearings, e.g. support of clutch drums, stacked arrangements of friction devices
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • 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
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

The invention discloses a variable speed transmission system, and relates to the technical field of transmission systems; the planetary gear train comprises a first planetary gear train in transmission connection with an input shaft, wherein the first planetary gear train is connected with a second planetary gear train through a transmission shaft, and the second planetary gear train is connected with an output shaft; the first planetary gear train comprises a first sun gear in transmission connection with a transmission shaft and an input shaft, a first planet gear is externally meshed with the first sun gear, one end of the transmission shaft, far away from the first sun gear, is in transmission connection with a second sun gear of a second planetary gear train, a second planet gear is externally meshed with the second sun gear, and the first planet gear and the second planet gear are in transmission connection through a gear ring; and a brake and a friction clutch are arranged on the transmission shaft. The invention can realize different rotating speeds required by the helicopter in two different modes of hovering and cruising, and realizes stable speed change without idle period.

Description

Variable speed transmission system
Technical Field
The invention relates to the technical field of transmission systems, in particular to a variable-speed transmission system.
Background
The helicopter has the characteristics of vertical landing and landing, hovering in the air, flexible flying in any direction, no need of fixing an airport and a runway and the like, and is widely applied to various fields. The general helicopters and special armed helicopters in China are in the continuous development period, the application prospect is wide, and the demand is continuously increased. Demand traction is always one of the main driving forces for scientific and technical progress, so the latest demand of helicopters will certainly promote the further development of the basic science of related disciplines and the key technology of related industries.
The transmission system, the engine and the rotor system are three key moving parts of the helicopter. The transmission system is used for transmitting the power and the rotating speed of the engine to the rotor wing, the tail rotor and various accessories according to a certain proportion, is an indispensable power transmission component for power output of the turboshaft engine and is also the only power transmission path. Therefore, transmission reliability is more demanding than the engine in helicopters, and helicopter performance is highly dependent on the performance of the transmission.
The typical transmission chain of the helicopter transmission system comprises two parts, namely a transmission chain for driving a main rotor and a transmission chain for driving a tail rotor, wherein the transmission chain for driving the main rotor comprises: the power of the engine passes through an engine output unit and a main speed reducer, and a main rotor is driven by a main rotor shaft; drive chain driving the tail rotor: and power is led out from a transmission chain for driving the main rotor wing, and the tail rotor wing is driven by a tail rotor shaft through a tail transmission horizontal shaft unit, an intermediate speed reducer, a tail transmission inclined shaft unit and a tail speed reducer. In the early stage of helicopter technical development, due to the limitations of design and calculation tools, in order to significantly reduce the workload of helicopter aerodynamic characteristic and dynamic characteristic design, reduce the design difficulty and simplify the design process, the rotating speed of a helicopter rotor is always set to a fixed value, although the aerodynamic characteristic of the rotor cannot be optimal in some states.
However, as the flying speed of the helicopter is gradually increased, the difference between the aerodynamic environment of the rotor in the hovering state and the high-speed forward flying state is increased, the difference between the optimal rotating speeds of the rotor in the hovering state and the high-speed forward flying state is increased, and the mode of fixing the rotating speed is difficult to take into account the aerodynamic performance in the hovering state and the high-speed flying state.
Disclosure of Invention
The invention aims to provide a variable speed transmission system, which solves the problems in the prior art, can realize different rotating speeds required by a helicopter in two different modes of hovering and cruising, and realizes stable speed change without a neutral period.
In order to achieve the purpose, the invention provides the following scheme:
the invention provides a variable speed transmission system, which comprises a first planetary gear train in transmission connection with an input shaft, wherein the first planetary gear train is connected with a second planetary gear train through a transmission shaft, and the second planetary gear train is connected with an output shaft; the first planetary gear train comprises a first sun gear in transmission connection with a transmission shaft and an input shaft, a first planet gear is externally meshed with the first sun gear, one end of the transmission shaft, far away from the first sun gear, is in transmission connection with a second sun gear of a second planetary gear train, a second planet gear is externally meshed with the second sun gear, and the first planet gear and the second planet gear are in transmission connection through a gear ring; and a brake and a friction clutch are arranged on the transmission shaft.
Optionally, the planet carrier of the first planetary gear train is fixedly arranged.
Optionally, the planet carrier of the second planetary gear train is connected with an output shaft.
Optionally, the brake and the friction clutch are disposed between the first planetary gear train and the second planetary gear train, the brake is disposed near the second planetary gear train, and the friction clutch is disposed near the first planetary gear train.
Optionally, the calculation method of the transmission ratio of the variable transmission system of the present invention is as follows:
when the friction clutch is in contact, the brake is released;
since the carrier of the first planetary gear train is fixed, n1HWhen it is equal to 0
Figure BDA0002946351930000021
Figure BDA0002946351930000022
Since n is5＝n1Therefore there are
Figure BDA0002946351930000023
Figure BDA0002946351930000024
Thus, the transmission ratio at low speed is
Figure BDA0002946351930000031
When the friction clutch is disengaged, the brake is closed;
the second planetary gear train takes the gear ring as a driving part, and the second sun gear is fixed, at the moment
Figure BDA0002946351930000032
The second planet wheel is analyzed to know
Figure BDA0002946351930000033
Bringing known conditions, solving to obtain:
Figure BDA0002946351930000034
thus, at high speed the transmission ratio is
Figure BDA0002946351930000035
In summary, the change speed transmission ratio is
Figure BDA0002946351930000036
In the above formula, the input rotation speed is niThe output end has a rotating speed of noThe number of the first sun gear teeth is Z1The first planet gear having a tooth number of Z2The number of teeth of the gear ring is Z3The number of second planetary gear teeth being Z4The number of the second sun gear teeth is Z5The first sun gear has a rotation speed of n1The planet carrier of the first planetary gear train has a rotational speed n1HThe gear ring has a rotational speed of n3The second planetary gear has a rotational speed n4The planet carrier of the second planetary gear train has the rotating speed of n2H。
Compared with the prior art, the invention has the following technical effects:
the invention adopts double planetary gear trains, and is matched with a friction clutch and a brake to be linked to realize two-stage variable speed transmission. Through parameter matching, different rotating speeds required by the helicopter in two different modes of hovering and cruising can be achieved. And secondly, the problem of power interruption during speed change is solved, stable speed change is realized, and no idle period exists. Besides, the double-planetary-gear-train-based aircraft adopts a double-planetary-gear train, has small volume and compact structure, and meets the requirements of an aviation aircraft; the high-speed path does not pass through a friction clutch, so that the risk is reduced to a certain extent; the power loss is small, and the efficiency is high; the transmission is stable, and the shock and vibration resistance is strong.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings needed in the embodiments will be briefly described below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without creative efforts.
FIG. 1 is a diagrammatic view of the drive connection of the variable speed drive system of the present invention;
wherein 100 is a variable speed transmission system, 1 is a first sun gear, 2 is a first planet gear, 3 is a gear ring, 4 is a second planet gear, 5 is a second sun gear, 6 is an input shaft, 7 is a transmission shaft, 8 is a friction clutch, 9 is a brake, and 10 is a planet carrier of a second planetary gear train.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
The invention aims to provide a variable speed transmission system, which solves the problems in the prior art, can realize different rotating speeds required by a helicopter in two different modes of hovering and cruising, and realizes stable speed change without a neutral period.
In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in further detail below.
At present, the variable-speed realization mode of the rotor mainly has three types: firstly, the rotating speed of the piston engine is changed through a control system, so that the output rotating speed of the power shaft is changed. The scheme is currently used by all models, but the working rotating speed of the engine is difficult to change, so that the change range is small, about only 3%, and the application is not wide. And secondly, the output rotating speed of the power turbine is changed without changing the working state of the core machine by adjusting the elevation angle or other geometric parameters of the power turbine of the engine. The scheme needs to install a plurality of different control mechanisms in the engine, and the current technology cannot realize the mode, only stays in a theoretical stage, and cannot be put into practice. And thirdly, changing a speed changing unit in a helicopter transmission system so as to change the transmission ratio.
Based on the above mode, the present invention provides a variable speed transmission system 100, as shown in fig. 1, including a first planetary gear train in transmission connection with an input shaft 6, the first planetary gear train is connected with a second planetary gear train through a transmission shaft 7, the second planetary gear train is connected with an output shaft; the first planetary gear train comprises a first sun gear 1 in transmission connection with a transmission shaft 7 and an input shaft 6, a first planet gear 2 is meshed outside the first sun gear 1, one end, far away from the first sun gear 1, of the transmission shaft 7 is in transmission connection with a second sun gear 5 of the second planetary gear train, a second planet gear 4 is meshed outside the second sun gear 5, and the first planet gear 2 and the second planet gear 4 are in transmission connection through a gear ring 3; the transmission shaft 7 is provided with a brake 9 and a friction clutch 8. The planet carrier of the first planetary gear train is fixedly arranged. The carrier 10 of the second planetary gear train is connected to an output shaft. The brake 9 and the friction clutch 8 are arranged between the first planetary gear train and the second planetary gear train, and the brake 9 is arranged close to the second planetary gear train and the friction clutch 8 is arranged close to the first planetary gear train.
When in the low speed path, the friction clutch 8 is engaged and the brake 9 is not active. On one hand, power is transmitted from the first sun gear 1 to the second sun gear 5 through the friction clutch 8 and then transmitted to the second planet gear 4; meanwhile, on the other hand, power is transmitted from the first sun gear 1 to the right second planetary gear 4 via the first planetary gear 2 and the ring gear 3. The two paths of power transmission processes enable the right planetary gear train to become a differential gear train, and finally power is converged and output by the planet carrier 10 of the second planetary gear train on the right side.
When the planetary gear is in a high-speed path, the friction clutch 8 is disengaged, and power is transmitted to the right second planetary gear 4 from the first sun gear 1 through the first planetary gear 2 and the gear ring 3; at this time, the frictional clutch 8 is disengaged and the brake 9 is engaged due to the interlocking action of the frictional clutch 8 and the brake 9, so that the rotational speed of the second sun gear 5 becomes 0. At this time, the right second planetary gear set is in a state where the ring gear 3 is input, the second sun gear 5 is fixed, and the carrier 10 of the second planetary gear set outputs power, and two transmission processes of power are indicated in the arrow direction in the figure.
Preferably, the transmission ratio of the variable transmission system of the present invention is calculated as follows:
when the friction clutch 8 is in contact, the brake 9 is released;
since the carrier of the first planetary gear train is fixed, n1HWhen it is equal to 0
Figure BDA0002946351930000061
Figure BDA0002946351930000062
Since n is5＝n1Therefore there are
Figure BDA0002946351930000063
Figure BDA0002946351930000064
Thus, the transmission ratio at low speed is
Figure BDA0002946351930000065
When the friction clutch 8 is disengaged, the brake 9 is closed;
the second planetary gear train takes the gear ring as a driving part, and the second sun gear is fixed, at the moment
Figure BDA0002946351930000066
The second planet wheel is analyzed to know
Figure BDA0002946351930000067
Bringing known conditions, solving to obtain:
Figure BDA0002946351930000068
thus, at high speed the transmission ratio is
Figure BDA0002946351930000069
In summary, the change speed transmission ratio is
Figure BDA0002946351930000071
In the above formula, the input shaft 6 has a rotation speed niThe output end has a rotating speed of no. The number of teeth of the first sun gear 1 is Z1The number of teeth of the first planet-gear 2 being Z2The number of teeth of the ring gear 3 is Z3The number of teeth of the second planet wheel 4 is Z4The number of teeth of the second sun gear 5 is Z5. The first sun gear 1 has the rotating speed of n1The planet carrier of the first planetary gear train has a rotational speed n1HTooth, toothRing 3 rotating at n3The second planet wheel 4 has the rotating speed n4The planet carrier 10 of the second planetary gear train has the rotating speed n2H。
According to the above formula, different Z's are selected1、Z5Different gear ratios μ can be obtained. This means that when an appropriate Z is selected1、Z5When the helicopter is used, the speed change between the high speed and the low speed of the helicopter can be realized. Table 1 shows preliminary parameters of the variable speed drive system.
TABLE 1 Primary parameters for variable speed drive systems
Name of component Number of teeth Z
First sun gear 1 29
First planetary gear 2 52
Gear ring 3 134
Second planet wheel 4 61
Second sun gear 5 14
In the description of the present invention, it should be noted that the terms "center", "top", "bottom", "left", "right", "vertical", "horizontal", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed in a particular orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The principle and the implementation mode of the invention are explained by applying a specific example, and the description of the embodiment is only used for helping to understand the method and the core idea of the invention; meanwhile, for a person skilled in the art, according to the idea of the present invention, the specific embodiments and the application range may be changed. In view of the above, the present disclosure should not be construed as limiting the invention.

Claims (3)

1. A variable speed drive system, characterized by: the planetary gear train comprises a first planetary gear train in transmission connection with an input shaft, wherein the first planetary gear train is connected with a second planetary gear train through a transmission shaft, and the second planetary gear train is connected with an output shaft; the first planetary gear train comprises a first sun gear in transmission connection with a transmission shaft and an input shaft, a first planet gear is externally meshed with the first sun gear, one end of the transmission shaft, far away from the first sun gear, is in transmission connection with a second sun gear of a second planetary gear train, a second planet gear is externally meshed with the second sun gear, and the first planet gear and the second planet gear are in transmission connection through a gear ring; the transmission shaft is provided with a brake and a friction clutch; the planet carrier of the second planetary gear train is connected with an output shaft; the brake and the friction clutch are arranged between the first planetary gear train and the second planetary gear train, the brake is arranged close to the second planetary gear train, and the friction clutch is arranged close to the first planetary gear train.
2. A variable speed drive system as claimed in claim 1, wherein: and the planet carrier of the first planetary gear train is fixedly arranged.
3. A variable speed drive system as claimed in claim 1, wherein: the transmission ratio is calculated as follows:
when the friction clutch is in contact, the brake is released;
since the carrier of the first planetary gear train is fixed, n1HWhen it is equal to 0
Figure FDA0003554314320000011
Figure FDA0003554314320000012
Since n is5＝n1Therefore there are
Figure FDA0003554314320000013
Figure FDA0003554314320000014
Thus, the transmission ratio at low speed is
Figure FDA0003554314320000015
When the friction clutch is disengaged, the brake is closed;
the second planetary gear train takes the gear ring as a driving part, and the second sun gear is fixed, at the moment
Figure FDA0003554314320000021
The second planet wheel is analyzed to know
Figure FDA0003554314320000022
Bringing known conditions, solving to obtain:
Figure FDA0003554314320000023
thus, at high speed the transmission ratio is
Figure FDA0003554314320000024
In summary, the change speed transmission ratio is
Figure FDA0003554314320000025
In the above formula, the input rotation speed is niThe output end has a rotating speed of noThe number of the first sun gear teeth is Z1The first planet gear having a tooth number of Z2The number of teeth of the gear ring is Z3The number of second planetary gear teeth being Z4The number of the second sun gear teeth is Z5The first sun gear has a rotation speed of n1The planet carrier of the first planetary gear train has a rotational speed n1HThe gear ring has a rotational speed of n3The second planetary gear has a rotational speed n4The planet carrier of the second planetary gear train has the rotating speed of n2H。
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Publication number Priority date Publication date Assignee Title
DE102014215156B4 (en) * 2014-08-01 2020-11-19 Zf Friedrichshafen Ag Group transmission of a motor vehicle
CN105508526B (en) * 2016-01-26 2017-10-10 吉林大学 A kind of power drive system based on the shift transmission of double planet wheel rows of mixing two
DE102017202337A1 (en) * 2017-02-14 2018-08-16 Zf Friedrichshafen Ag Multi-speed transmission for a vehicle
CN106939929A (en) * 2017-05-19 2017-07-11 福建万润新能源科技有限公司 A kind of shift transmission of mono-tooth ring dry friction external control three
DE102017219111B4 (en) * 2017-10-25 2022-05-25 Zf Friedrichshafen Ag Power-split continuously variable transmission device

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