CN108343716B - The fast modularization transmission device of one kind three - Google Patents
The fast modularization transmission device of one kind three Download PDFInfo
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- CN108343716B CN108343716B CN201810129628.XA CN201810129628A CN108343716B CN 108343716 B CN108343716 B CN 108343716B CN 201810129628 A CN201810129628 A CN 201810129628A CN 108343716 B CN108343716 B CN 108343716B
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- clutch
- friction disk
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- oil
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/04—Features relating to lubrication or cooling or heating
- F16H57/042—Guidance of lubricant
-
- 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
- F16H57/10—Braking arrangements
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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
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
- F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three forward speeds
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
The present invention relates to the fast modularization transmission devices of one kind three, the transmission device uses modularized design, one module is a gear unit, input shaft, two clutches, two brakes and planet row are integrated in module, and the transformation of three fast transmission ratios can be achieved by the control of the various combination of clutch and brake.Planet row is as primary drive component, mainly includes centre wheel, coplanar gear ring, outer gear ring and planet carrier using coplanar double internal-gearing planet gear driving forms.The interior external gear teeth of coplanar gear ring constitutes the gear mesh form of internal messing with centre wheel and outer gear ring respectively.Clutch and brake are the control assembly of module, mainly include clutch oil cylinder, brake cylinder, piston friction disk, intermediate friction disk, clutch fixed friction disk and brake disc etc..Each frictional disk is all made of more cone tank configuration designs, the torque capacity of transmitting is improved, to realize the miniaturization and lightweight of transmission device.
Description
Technical field
The present invention relates to a kind of including clutch, brake and the planet being made of coplanar double internal-gearing planet gears
Row, the transmission device designed using modular method, belongs to Gearbox design field.
Background technique
In the power energy type system of field of new energy applications, such as EHV electric and hybrid vehicle, it is desirable that its power passes
Dynamic system has the characteristics such as transmission efficiency is high, transmitting change in torque range is wide, small in size, light-weight, to meet vehicle not
With the passability and driver comfort demand of road conditions, while reaching the target of energy-saving and emission-reduction.Current most of pure electric automobiles are adopted
With single reduction gear, gear is limited, although its structure is simple, does not play obvious effect to widening for output torque range
Fruit causes current pure electric automobile only to be fitted far from the driving challenge for meeting China's wide geographic area road conditions and proposing to vehicle
It shares in urban traffic road；As for hybrid vehicle, variable ratio drive system be it is essential, be using more at present
Automatic transmission AT, while fluid torque-converter is needed to configure, cause power transmission efficiency lower than 80%, but also transmission transposition body
Long-pending and weight is larger, and structure is complicated, is unfavorable for overhauling.
, output torque variation range few for current pure electric automobile transmission gear be narrow and hybrid vehicle speed change
The problems such as structure is complicated for device, transmission efficiency is low,
Summary of the invention
The technology of the present invention solves the problems, such as: overcoming the deficiencies of the prior art and provide the fast modularization transmission device of one kind three, has
The advantages such as transmission efficiency is high, small in size, light-weight, transmitting load is big；In addition, also can be real by the series connection of multiple transmission modules
The existing purely mechanic nearly variable speed in multi gear position, to meet the drive demand of EHV electric and hybrid vehicle.
The technology of the present invention solution: the fast modularization transmission device of one kind three, the transmission device use modularized design,
One module is a gear unit, and the gear unit includes input shaft, clutch transmission axis, first clutch, the second clutch
Device, the first brake, second brake, planet row, snubbing, oil distribution seat and cabinet, wherein planet row includes centre wheel, is total to
Face gear ring, outer gear ring and planet carrier, planet carrier are bolted and are formed by the first frame and the second frame；Input shaft and planet
Between row by gear drive connect, the first, second brake rank planet row two sides respectively with the first frame of planet carrier and second
Frame connection, the first, second clutch are mounted on clutch transmission axis, and input shaft and clutch transmission axis are co-axially mounted；Each biography
Moving cell realizes three kinds of different drive ratios, i.e., three fast transmission ratios by the control of the various combination of two clutches and two brakes
Transformation, each unit module with different drive ratios, which is together in series, can be realized the nearly variable speed of transmission device.
The outer hub spare interface of each module, for multiple block coupled in series connect, the transmission ratio quantity of entire transmission device with
Module number is in exponential grade relationship, N=3m, wherein N is transmission gear ratio quantity, and m is module number, disparate modules selection
Different transmission ratios, multiple block coupled in series realize nearly variable speed.
Detailed process is as follows for the transformation of the three fast transmission ratios, if three kinds of transmission ratios are respectively k1, k2 and 1, described three
The realization process of kind transmission ratio k1, k2 and 1 is as follows:
(1) first clutch oil cylinder is oil-filled, and the first clutch intermediate friction disk is compacted to clutch by the first clutch piston friction disk
Fixed friction disk, realization planet carrier are indirectly connected with clutch transmission axis；Meanwhile second brake cylinder it is oil-filled, second braking live
Second braking intermediate friction disk is compacted to the second brake disc by plug frictional disk, the fixation of outer gear ring is realized, in this way in planet
In transmission system, there are determining input component, a brake component and an output, it is defeated to form a determining transmission ratio k1
Out；
(2) second clutch oil cylinders are oil-filled, and the second clutch intermediate friction disk is compacted to clutch by the second clutch piston friction disk
Fixed friction disk realizes being indirectly connected with for outer gear ring and clutch transmission axis；Meanwhile first brake cylinder it is oil-filled, first braking
First braking intermediate friction disk is compacted to the first brake disc by piston friction disk, realizes the fixation of planet carrier, at this time shape
At a determining transmission ratio k2 output；
(3) first, second clutch oil cylinders are oil-filled simultaneously, and the first, second brake cylinder is not oil-filled, realize planet carrier and outer
Gear ring is connected, and two driving members, which are connected, in planet row can be such that planet row rotates as a whole, is formed at this time
The output that one determining transmission ratio is 1.
The first clutch is identical with second clutch structure, each clutch include: the first clutch oil cylinder, second from
Close oil cylinder, clutch fixed friction disk, the first clutch piston friction disk, the second clutch piston friction disk, the first clutch intermediate friction
Disk, the second clutch intermediate friction disk and clutch transmission axis and straight pin and cylindrical compression spring；One clutch transmission axis conduct
The power output shaft of gear unit, clutch transmission axis one end are supported on input shaft inner hole and row by two groups of deep groove ball bearings respectively
Carrier the second frame inner hole, the other end are supported among the outer hub inner hole of composition cabinet by one group of deep groove ball bearing, and clutch passes
Inner spline groove, circumferential uniformly distributed hydraulic oil duct and oil leab are provided with along axis among moving axis；
Clutch fixed friction disk, is connected on clutch transmission axis by flat key, and clutch fixed friction disk inner hole two sides
Face is provided with tooth, and the tooth socket opened up with the first clutch oil cylinder and the second clutch oil cylinder side engages, and plays circumferentially fixed clutch oil
The effect of cylinder；First, second clutch oil cylinder is connected by teeth tooth socket and clutch fixed friction disk and is located at clutch fixed friction
Disk two sides are placed on clutch transmission axis, are rotated together with clutch transmission axis；
It can the first clutch piston friction disk be placed in the first clutch oil cylinder in axial sliding along clutch transmission axis；First from
Piston friction disk is closed to be determined in the in-oil cylinder axial position of the first clutch by the in-oil cylinder oil pressure size of the first clutch；
Can along clutch transmission axis the first clutch intermediate friction disk and the second clutch intermediate friction disk in axial sliding, first from
Intermediate friction disk is closed between the first clutch piston friction disk and clutch fixed friction disk, the second clutch intermediate friction disk is located at
Between second clutch piston friction disk and clutch fixed friction disk；Wherein, the first clutch intermediate friction disk and the second frame of planet carrier
The stretching of frame is disconnected along connection, stretches out and breaks along being the part stretched out on matrix, similar to the structure of claw；Second clutch intermediate friction
The stretching of disk and snubbing is disconnected along connection, each clutch intermediate friction disk two sides workspace respectively with piston friction disk and clutch
The working region of fixed friction disk is coupled.
First brake and second brake, two brakes are similar in control mode in mounting structure, each
Brake includes: the first, second brake cylinder, and the first, second brake piston frictional disk, first, second brakes intermediate friction disk,
First, second brake disc and straight pin and cylindrical compression spring；
First brake disc and the outer hub of the first brake cylinder pass through the circumferentially fixed connection of straight pin；
It can the first brake piston frictional disk be placed in the brake cylinder of hub outside the first brake cylinder in axial sliding along straight pin
It is interior, first, brake piston frictional disk determined in the axial position in the first brake cylinder by the oil pressure size in the first brake cylinder
It is fixed；
First, second intermediate friction disk can be braked in axial sliding along transmission device central axis, wherein in the first braking
Between frictional disk and the stretching of the first frame of planet carrier it is disconnected along connect, the disconnected edge of the stretching of the second braking intermediate friction disk and snubbing
Connection；
It is resetted by cylindrical compression spring between the frictional disk respectively coupled.
The planet row uses coplanar double internal-gearing planet gear driving forms, including centre wheel, coplanar gear ring, outer gear ring
And planet carrier；Wherein centre wheel, coplanar gear ring, outer gear ring and planet carrier are located at same mounting plane, and coplanar gear ring is by planet carrier
It supports, external gear teeth constitutes the gear mesh form of internal messing with centre wheel and outer gear ring respectively in coplanar gear ring.
The planet row, the planet carrier for supporting coplanar gear ring for including pass through bolt by the first frame and the second frame
Connection composition, the first frame stretch out disconnected edge and link together with the first braking intermediate friction disk.
The disconnected edge of the stretching for the second frame of planet carrier that planet row includes links together with the first clutch intermediate friction disk.
The stretching of the snubbing for the connection gear ring that the planet row includes is disconnected to brake intermediate friction disk with second along simultaneously
It links together with the second clutch intermediate friction disk.
The oil distribution seat radially opens up the first, second clutch fluid pressure oil injection hole and lubricating oil injection hole, oil distribution seat with
The second outer hub of braking is connected with, and guarantees to seal with sealing ring between clutch transmission axis.
The advantages of the present invention over the prior art are that:
(1) present invention uses modularized design, and a module is a gear unit, clutch, brake and transmission
Gear is encapsulated in a transmission module.There are three available transmission ratio, one transmission modules of every increase for each transmission module tool
Available transmission ratio quantity is just in that exponential grade increases.The transmission ratio for rationally designing each unit, the list with different drive ratios
Element module is together in series, the control of engagement clutch and brake, realizes the more gear speed-changings of transmission device.
(2) each module mainly includes first clutch, second clutch, the first brake, second brake, planet
Row, oil distribution seat and cabinet.The transmission gear of coplanar double inside engaged gear gear units uses coplanar double modulus planetary gear, base
This component includes centre wheel, coplanar gear ring, outer gear ring and planet carrier, and planet carrier is formed by the first frame and the second framework composition.
Coplanar gear ring is arranged off-centre, and support construction is supported using two point form, and such stability of strutting system is good, and transmission power is big.Transmission is single
All gear mesh forms are internal messing in member, multiple planetary gears of conventional planetary row are replaced with a coplanar gear ring, therefore
Reduce number of components, the volume and weight of drive mechanism.In order to improve the bearing capacity of the gear teeth, coplanar double inside engaged gears are used
Novel big registration internal messing tooth form, novel tooth form registration are doubled than traditional involute profile.Clutch and braking
Device is the control assembly of module, is mainly rubbed including clutch oil cylinder, brake cylinder, piston friction disk, intermediate friction disk, clutch fixation
Wipe disk and brake disc etc..Two of them clutch intermediate friction disk is connected with planet carrier and gear ring respectively, is subject to brake
Control be optionally used as the input of clutch power, clutch fixed friction disk and clutch transmission axis are connected as clutch
The output of power.Each frictional disk is all made of the configuration design of more cone tanks, greatly enhances the torque capacity of transmitting, from
And realize miniaturization, light-weight design.
Detailed description of the invention
Fig. 1 is the cross-sectional view of three fast modularization transmission devices of present example；
Fig. 2 is kinematic sketch in the present invention；
Fig. 3 is the first and second clutch cross-sectional views in the present invention；
Fig. 4 is planet row cross-sectional view in the present invention.
Specific embodiment
Embodiment of the present invention is illustrated with reference to the accompanying drawing.
As shown in Figure 1, one module is one for the unit example of of the invention one three fast modularization transmission device
Gear unit, main includes input shaft 1, first clutch, second clutch, the first brake, the second braking of a rotation
Device, planet row, oil distribution seat 22 and cabinet.Input shaft 1 and clutch transmission axis 25 are located on same center line, 1 inner hole of input shaft
It disposes round slider 50 and is sealed with thread plug 51, interior hexagonal spiral shell 52, round slider 50 and interior hexagonal spiral shell are screwed on thread plug 51
The installation of nail is for the ease of the disassembly of input shaft 1 and clutch transmission axis 25, and deep groove ball bearing is installed in 25 one end of clutch transmission axis
49 are supported on the inner hole of input shaft 1；Four groups of sealing rings 24 are installed to be sealed between oil distribution seat 22 and clutch transmission axis 25；It is coplanar
The centre wheel 47 of double inside engaged gear gear units is connect with input shaft 1 by internal spline and is supported with needle bearing 48 coplanar double
The planet carrier of inside engaged gear gear unit completes the input of power；The snubbing of coplanar double inside engaged gear gear units
38 and planet carrier (being connected by the first frame 43 and the second frame 40 by screw 41) optionally as transmission device power
Output.Clutch fixed friction disk 34 is connect by flat key 28 with clutch transmission axis 25, and power is reached clutch transmission axis 25.It is defeated
Enter axis 1 and clutch transmission axis 25 to connect with other modules again by internal spline with spline axis connection, realizes the string of gear unit
Connection meets the requirement of more transforming gears.
The cabinet of each module is the outer hub of five sections of cylindrical types, installs " O " type sealing ring 11 between each outer hub and by multiple
Stay bolt 16 connects, mainly include the first brake cylinder 5, first brake outer hub 12, hub 13 outside unit, the second brake cylinder 14,
The outer hub 15 of second braking, input end cap 2 and oil distribution seat 22.There is sufficiently large space coplanar double to dispose inside the outer hub 13 of unit
Inside engaged gear gear unit.Input end cap 2 and the first brake cylinder 5 are connected to input terminal and can adjust deeply by adjusting gasket
The gap of ditch ball bearing 4, meanwhile, inputting mounting framework oil sealing 3 between end cap 2 and input shaft 1 prevents from revealing.Oil distribution seat 22 and second
The outer hub 15 of braking is connected to output end can adjust the gap of deep groove ball bearing 23 by adjusting gasket.Each brake cylinder and system
Have hydraulic oil injection hole and lubricating oil injection hole on dynamic outer hub, 13 lower end of hub is provided with that drain oil is mountable to drain the oil to unit outside
Valve.
As shown in figure 4, the planet row that coplanar double internal-gearing planet gears of three fast modularization transmission devices are constituted mainly wraps
Include outer gear ring 42, coplanar gear ring 45, centre wheel 47 and planet carrier and snubbing 38；Planet carrier is by the first frame 43 and second
Frame 40 is connected by screw 41；Outer gear ring 42 is supported on the first frame of planet carrier 43 by retainer bearing 44, damper frame
Frame 38 is supported on the second frame of retainer 40 by retainer bearing 39；Centre wheel internal spline is connect with input shaft external splines,
Outer gear ring 42 is linked together with snubbing 38 using cotter way formula, and is fixed by interior snap ring.Coplanar double internal messing rows
The gear-driven all tooth forms of star are all made of big registration tooth.Coplanar gear ring 45 is disposed relative to 47 bias of centre wheel,
And it is supported on planet carrier by two groups of retainer bearings 46.Planet carrier includes the first frame 43 and the second frame 40, the first frame
There is the boss of small one and large one two months shapes between frame and the second frame, the moon shape boss on the first, second frame is corresponding, leads to
The connection of multiple groups screw 41 is crossed, forms an eccentric annular space in centre, this annular space has ladder and annular space
Eccentricity it is identical as the eccentricity that coplanar gear ring 45 is installed, gear ring 45 coplanar so both can be in the annular space of planet carrier
Autobiography can also revolve around centre wheel 47.The meaning of double internal messings refers to: 47 external tooth of centre wheel forms interior with coplanar 45 internal tooth of gear ring
Engagement, coplanar 45 external tooth of gear ring and 42 internal tooth of outer gear ring form internal messing.It can be punched on the first, second frame, by changing
Become counterweight to adjust static balance, the outside of the first frame 43 is stretched out disconnected edge and connect with the first braking intermediate friction disk, the second frame
40 outside is stretched out disconnected edge and is connect with the first clutch intermediate friction disk.Structure above forms the tooth with three degree of freedom
Gear unit is taken turns, centre wheel 47 is used as power input link, and coplanar gear ring 45 is used as intermediate reaction component, passes through clutch and system
Dynamic device collective effect changes the state of planet carrier and outer gear ring, selects a component in planet carrier and outer gear ring defeated as power
Part out, another component is as fixing piece, to change the transmission ratio of gear transmission unit.
As shown in figure 3, clutch and brake mainly include the first clutch oil cylinder 37, the second clutch oil cylinder 31, first from
Close piston friction disk 36, the second clutch piston friction disk 32, the first clutch intermediate friction disk 35, the second clutch intermediate friction disk
33, clutch fixed friction disk 34, clutch transmission axis 25, the first clutch intermediate friction disk 5, the braking of the second brake cylinder 14, first
Outer hub 12, second brakes outer hub 15, the first brake piston frictional disk 7, the second brake piston frictional disk 17, first and brakes intermediate rub
It wipes disk 6, second and brakes intermediate friction disk 18, the first brake disc 8, the second brake disc 19, the first fixed pin 29, second
Fixed pin 9, the first return spring 30, second return spring 10 etc..The working region of frictional disk is tapered frictional groove, can be increased in this way
Big friction surface product, reduces the quantity of frictional metal piece, increases transmitted torque.Fixed friction disk 34 in clutch is logical
It crosses flat key 28 and is connected on clutch transmission axis and can rotate together, the side tooth of the first clutch oil cylinder 37, the second clutch oil cylinder 31
It intermeshes and is fixed together with the side alveolus of fixed friction disk 34, while the second clutch oil cylinder 31 right end locking nut 26
It is fixed together with holding screw 27 and clutch transmission axis 25, the first clutch oil cylinder 37 above-mentioned in this way, is consolidated the second clutch oil cylinder 31
Determining frictional disk 34 and clutch transmission axis 25 can rotate together.First clutch piston friction disk 36, the second clutch piston friction disk
32, the first clutch intermediate friction disk 35, the second clutch intermediate friction disk 33 are co-axially mounted with clutch fixed friction disk 34, and lead to
The connection of fixed pin 29 is crossed, clutch piston friction disk only axially moves；First clutch intermediate friction disk 35 can be with planet carrier one
It plays rotation and can be stretched out in the second frame 40 and broken along interior axial movement, the second clutch intermediate friction disk 33 can be with snubbing 38 1
It plays rotation and can be stretched out at it disconnected along interior axial movement.First brake piston frictional disk 7, the second brake piston frictional disk 17 difference
It is connected to outside the first braking outside the braking of hub 12, second with the first brake disc 8, the second brake disc 19 by fixed pin 9
On hub 15, the first brake piston frictional disk 7 of limitation, the second brake piston frictional disk 17 only axially move；In first braking
Between frictional disk can rotate together and be stretched out in the first frame 43 disconnected along interior axial movement, the second braking intermediate friction disk with planet carrier
It can rotate together and be stretched out at it disconnected along interior axial movement with snubbing 38.Each frictional disk is in brake and clutch
Be co-axially mounted, and between separation return carried out by the return spring 10,30 etc. being mounted on flush end holding screw 20.
The course of work of the fast modularization transmission device of explanation three below.When input shaft 1 rotates, double inside engaged gear transmissions are single
Centre wheel 47 in member rotates with.At the same time, pass through the oil charging-discharging control (control to each clutch oil cylinder and brake cylinder
Sequence is as shown in table 1), realize the power output (kinematic sketch is as shown in Figure 2) of gear unit different drive ratios:
(1) first clutch oil cylinder 37 is oil-filled, and the first clutch piston friction disk 36 compresses the first clutch intermediate friction disk 35
To clutch fixed friction disk 34, being indirectly connected with for planet carrier and clutch transmission axis 25 is realized；Meanwhile second brake cylinder fill
Second braking intermediate friction disk 18 is compacted to the second brake disc 19, realized outer by oil, the second brake piston frictional disk 17
The fixation of gear ring 42 has determining input component, a brake component and an output in this way in planetary transmission system, is formed
One determining transmission ratio k1 output；
(2) second clutch oil cylinders 31 are oil-filled, and the second clutch piston friction disk 32 compresses the second clutch intermediate friction disk 33
To clutch fixed friction disk 34, being indirectly connected with for outer gear ring 42 and clutch transmission axis 25 is realized；Meanwhile first brake cylinder fill
First braking intermediate friction disk 6 is compacted to the first brake disc 8, realizes planet carrier by oil, the first brake piston frictional disk 7
Fixation, form a determining transmission ratio k2 output at this time；
(3) first, second clutch oil cylinders are oil-filled simultaneously, and the first, second brake cylinder is not oil-filled, realizes planet carrier and tooth
Circle is connected, and two driving members, which are connected, in planetary transmission system can be such that planetary transmission system revolves as a whole
Turn, forms the output that a determining transmission ratio is 1 at this time.
1 control sequence of table
(● --- it is oil-filled, zero --- not oil-filled, C1 --- first clutch, C2 --- second clutch, B1 --- first
Brake, B2 --- second brake；K1, k2 are determined by the specific number of teeth of each transmission gear)
Wherein the hydraulic oil in the first, second brake cylinder is external oil pump via the note on hub outside the first, second oil cylinder
Enter hole enter it is in-oil cylinder, the hydraulic oil in the first, second clutch oil cylinder is passed through again by injection hole corresponding on oil distribution seat 22
Oil duct in clutch transmission axis respectively enters in-oil cylinder, the outer hub of 21 installation pipeline of oil circuit pipeline installation site connection and oil distribution seat
22.By the different control combinations of brake and clutch, different driving members is selected to realize as fixing piece and output
Three speed transformation of the fast modularization transmission device of of the invention three.In addition, can also be by the clutch of module according to different usages
Transmission shaft 25 is used as power input shaft, and former input shaft 1 is used as power output shaft, can realize three different gear ratio sets again in this way
It closes.
In conclusion each gear unit can be there are three types of sequence of motion, this depends on which element in all elements
As torque input members, torque output members and fixing piece.
One modular three fast transmission device has as a smallest gear unit there are three types of different transmission ratios,
One modular gear unit of every increase, available numbers of gear steps double.It, can by the series connection of multiple gear units
Realize the bit map of transmission device multi gear.When concatenated module number is more and more, the numbers of gear steps of transmission device also will be more next
More, shift will be more steady, can more make full use of the output power of engine also or expand the output torque model of motor
It encloses.
Above embodiments are provided just for the sake of the description purpose of the present invention, and are not intended to limit the scope of the invention.This
The range of invention is defined by the following claims.It does not depart from spirit and principles of the present invention and the various equivalent replacements made and repairs
Change, should all cover within the scope of the present invention.
Claims (10)
1. the fast modularization transmission device of one kind three, the transmission device uses modularized design, and a module is that a transmission is single
Member, the gear unit include input shaft, clutch transmission axis, first clutch, second clutch, the first brake, the second system
Dynamic device, planet row, snubbing, oil distribution seat and cabinet, it is characterised in that: planet row includes centre wheel, coplanar gear ring, outer gear ring
And planet carrier, planet carrier are bolted and are formed by the first frame and the second frame；Pass through gear between input shaft and planet row
Transmission connection, the first, second brake rank planet row two sides and connect respectively with the first frame of planet carrier and the second frame, the
One, second clutch is mounted on clutch transmission axis, and input shaft and clutch transmission axis are co-axially mounted；Each gear unit passes through two
The various combination of a clutch and two brakes control three kinds of different drive ratios of realization, i.e., the transformation of three fast transmission ratios, each
Unit module with different drive ratios, which is together in series, can be realized the variable speed of transmission device.
2. according to claim 1 three fast modularization transmission devices, it is characterised in that: the outer hub of each module is reserved to be connect
Mouthful, it is connected for multiple block coupled in series, the transmission ratio quantity and module number of entire transmission device are in exponential grade relationship, N=3m,
Middle N is transmission gear ratio quantity, and m is module number, and disparate modules select different transmission ratios, and multiple block coupled in series are realized
Variable speed.
3. according to claim 1 three fast modularization transmission devices, it is characterised in that: the transformation of described three fast transmission ratios
Detailed process is as follows, if three kinds of transmission ratios are respectively k1, k2 and 1, described three kinds of transmission ratios k1, k2 and 1 realization process it is as follows:
(1) first clutch oil cylinder is oil-filled, and the first clutch intermediate friction disk is compacted to clutch and fixed by the first clutch piston friction disk
Frictional disk, realization planet carrier are indirectly connected with clutch transmission axis；Meanwhile second brake cylinder it is oil-filled, the second brake piston rubs
It wipes disk and the second braking intermediate friction disk is compacted to the second brake disc, the fixation of outer gear ring is realized, in this way in Gear Planet Transmission
In system, there are determining input component, a brake component and an output, forms a determining transmission ratio k1 output；
(2) second clutch oil cylinders are oil-filled, and the second clutch intermediate friction disk is compacted to clutch and fixed by the second clutch piston friction disk
Frictional disk realizes being indirectly connected with for outer gear ring and clutch transmission axis；Meanwhile first brake cylinder it is oil-filled, the first brake piston
First braking intermediate friction disk is compacted to the first brake disc by frictional disk, is realized the fixation of planet carrier, is formd at this time
One determining transmission ratio k2 output；
(3) first, second clutch oil cylinders are oil-filled simultaneously, and the first, second brake cylinder is not oil-filled, realizes planet carrier and outer gear ring
Be connected, in planet row by two driving members be connected planet row can be made to rotate as a whole, at this time formed one
The output that determining transmission ratio is 1.
4. three fast modularization transmission devices according to claim 1, it is characterised in that: the first clutch and second from
Clutch structure is identical, and each clutch includes: the first clutch oil cylinder, the second clutch oil cylinder, clutch fixed friction disk, the first clutch
Piston friction disk, the second clutch piston friction disk, the first clutch intermediate friction disk, the second clutch intermediate friction disk and clutch transmission
Axis and straight pin and cylindrical compression spring；Power output shaft of one clutch transmission axis as gear unit, clutch transmission axis
One end is supported on input shaft inner hole and planet carrier the second frame inner hole by two groups of deep groove ball bearings respectively, and the other end passes through one group
Deep groove ball bearing is supported among the outer hub inner hole of composition cabinet, is provided with inner spline groove along axis among clutch transmission axis, circumferential
Uniformly distributed hydraulic oil duct and oil leab；
Clutch fixed friction disk, is connected on clutch transmission axis by flat key, and clutch fixed friction disk inner hole two sides are opened
There is tooth, the tooth socket opened up with the first clutch oil cylinder and the second clutch oil cylinder side engages, and plays circumferentially fixed clutch oil cylinder
Effect；First, second clutch oil cylinder is connected by teeth tooth socket and clutch fixed friction disk and is located at clutch fixed friction disk two
Side is placed on clutch transmission axis, is rotated together with clutch transmission axis；
Along clutch transmission axis, the first clutch piston friction disk is placed in the first clutch oil cylinder in axial sliding；First clutch piston
Frictional disk is determined in the in-oil cylinder axial position of the first clutch by the in-oil cylinder oil pressure size of the first clutch；
Among clutch transmission axis the first clutch intermediate friction disk and the second clutch intermediate friction disk in axial sliding, the first clutch
Frictional disk between the first clutch piston friction disk and clutch fixed friction disk, the second clutch intermediate friction disk be located at second from
It closes between piston friction disk and clutch fixed friction disk；Wherein, the first clutch intermediate friction disk and the second frame of planet carrier are stretched
Break out along connection；The stretching of second clutch intermediate friction disk and snubbing is disconnected along connection, each clutch intermediate friction disk two sides
Working region of the workspace respectively with piston friction disk and clutch fixed friction disk is coupled.
5. according to claim 1 three fast modularization transmission devices, it is characterised in that: first brake and the second system
Dynamic device, two brakes are identical on mounting structure and control mode, and each brake includes: the first, second brake cylinder, the
One, the second brake piston frictional disk, the first, second braking intermediate friction disk, the first, second brake disc and straight pin and
Cylindrical compression spring；
First brake disc and the outer hub of the first brake cylinder pass through the circumferentially fixed connection of straight pin；
Along straight pin, the first brake piston frictional disk is placed in outside the first brake cylinder in the brake cylinder of hub in axial sliding, the
One, brake piston frictional disk is determined in the axial position in the first brake cylinder by the oil pressure size in the first brake cylinder；
First, second intermediate friction disk is braked in axial sliding along transmission device central axis, wherein the first braking intermediate friction
Disk is disconnected along connecting with the stretching of the first frame of planet carrier, and the stretching of the second braking intermediate friction disk and snubbing is disconnected along connection；
It is resetted by cylindrical compression spring between the frictional disk respectively coupled.
6. according to claim 1 three fast modularization transmission devices, it is characterised in that: the planet row is using coplanar double interior
Meshing planetary gear driving form, including centre wheel, coplanar gear ring, outer gear ring and planet carrier；Wherein centre wheel, coplanar gear ring,
Outer gear ring and planet carrier are located at same mounting plane, and coplanar gear ring is supported by planet carrier, and external gear teeth is respectively in coplanar gear ring
Heart wheel and outer gear ring constitute the gear mesh form of internal messing.
7. according to claim 4 three fast modularization transmission devices, it is characterised in that: the planet row, include is used for
The planet carrier for supporting coplanar gear ring is bolted and is formed by the first frame and the second frame, and the first frame stretches out disconnected along with the
One braking intermediate friction disk links together.
8. according to claim 4 three fast modularization transmission devices, it is characterised in that: the planet carrier second that planet row includes
The disconnected edge of the stretching of frame links together with the first clutch intermediate friction disk.
9. according to claim 4 three fast modularization transmission devices, it is characterised in that: the tooth connection that the planet row includes
The stretching of the snubbing of circle is disconnected to link together along simultaneously with the second braking intermediate friction disk and the second clutch intermediate friction disk.
10. three fast modularization transmission devices according to claim 1, it is characterised in that: the oil distribution seat radially opens up the
One, second clutch hydraulic oil injection hole and lubricating oil injection hole, oil distribution seat is connected with the second outer hub of braking, with clutch
Guarantee to seal with sealing ring between transmission shaft.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810129628.XA CN108343716B (en) | 2018-02-08 | 2018-02-08 | The fast modularization transmission device of one kind three |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810129628.XA CN108343716B (en) | 2018-02-08 | 2018-02-08 | The fast modularization transmission device of one kind three |
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| Publication Number | Publication Date |
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| CN108343716A CN108343716A (en) | 2018-07-31 |
| CN108343716B true CN108343716B (en) | 2019-10-11 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201810129628.XA Active CN108343716B (en) | 2018-02-08 | 2018-02-08 | The fast modularization transmission device of one kind three |
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Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN110120722A (en) * | 2019-06-18 | 2019-08-13 | 北京航空航天大学 | A kind of integrated speed-reducing motor |
Family Cites Families (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR100617460B1 (en) * | 2005-03-30 | 2006-09-01 | 우영유압주식회사 | Compact variable transmission installed between bevel and differential gear |
| IT201600072035A1 (en) * | 2016-07-11 | 2018-01-11 | Fabio Marcello Rota | EXCHANGE OF SPEED PARTICULARLY FOR SHREDDERS |
| CN106286727B (en) * | 2016-08-26 | 2018-11-20 | 哈尔滨东安汽车发动机制造有限公司 | A kind of transmission system of eight-speed automatic transmission |
| CN106704499B (en) * | 2017-01-13 | 2018-02-16 | 广州市新域动力技术有限公司 | Star-like dry friction brake type automatic planet arrangement of clutch |
| CN106594192B (en) * | 2016-12-23 | 2023-05-02 | 陕西国力信息技术有限公司 | Modularized combined transmission |
| CN106704495B (en) * | 2016-12-23 | 2023-03-31 | 陕西国力信息技术有限公司 | Modular combined transmission suitable for more gears |
| CN107387682A (en) * | 2017-07-10 | 2017-11-24 | 徐西玲 | A kind of Gear Planet Transmission shifter |
| CN107339379B (en) * | 2017-08-08 | 2023-06-16 | 张家港川梭车业有限公司 | Movable three-gear speed change device of planetary transmission |
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