CN104373534B - A kind of multi-shifting speed variator of planetary gear construction - Google Patents
A kind of multi-shifting speed variator of planetary gear construction Download PDFInfo
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- CN104373534B CN104373534B CN201410418597.1A CN201410418597A CN104373534B CN 104373534 B CN104373534 B CN 104373534B CN 201410418597 A CN201410418597 A CN 201410418597A CN 104373534 B CN104373534 B CN 104373534B
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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
- F16H3/62—Gearings having three or more central gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H57/00—General details of gearing
- F16H57/02—Gearboxes; Mounting gearing therein
- F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
-
- 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
- F16H2200/006—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising eight forward speeds
-
- 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
- F16H2200/0065—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising nine forward speeds
-
- 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
- F16H2200/0082—Transmissions for multiple ratios characterised by the number of reverse speeds
-
- 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
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- 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
- F16H2200/2046—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with six engaging means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
Abstract
A kind of multi-shifting speed variator of planetary gear construction, it contains housing, input link, output link, first, second, third planetary gear set, first, second, third and fourth, five, six, seven interconnecting components and first, second, third and fourth, five, six torque transmitters；First, second, third planetary gear set is arranged in order from input terminal to output terminal；First, second, third and fourthth, five, six torque transmitters include three brakes and three clutches, and first, second, and third torque transmitter is between second and third planet gear set side by side close to housing；Four, the 5th and the 6th torque transmitter is between the first and second planetary gear sets, wherein the 4th torque transmitter closes on pivot, five, the 6th torque transmitters are located above the 4th torque transmitter side by side, and above-mentioned each component is respectively positioned within housing；The present invention is a kind of compact-sized multi-speed transmission.
Description
Technical field
The present invention relates to a kind of multi-shifting speed variator of planetary gear construction, more particularly to a kind of applied to motor vehicles
Fluid drive belongs to motor vehicle transmission technical field.
Background technology
Planetary gear construction because possess it is compact-sized, carrying it is big the advantages of due to be widely used in automatic gearbox neck
Domain.Using planetary gear construction automatic transmission need by with reference to different shifting elements such as brake and clutch come reality
Show different forward gears and reverse gear.
A kind of multivariant automatic transmission is disclosed in addition, on May 30th, 2004, in 6,712,731 B1 of US to move
Power delivery system has seven forward gears and a reverse gear shift.Three planetary gear sets that this serial speed changer includes have
Six power shifting elements and two fixed structure connections.It is contained in dynamical system and is at least connected with a planetary gear
The engine and fluid torque-converter of component, output block are connected with the component of another planetary gear set.Six of which power passes
It passs path and provides multiple gear assemblies, be fixedly connected, input shaft, the interconnection between output shaft and case of transmission is led to
The connection for crossing three clutches establishes the fast ratio of seven forward gears and a reverse gear shift.
It discloses and a kind of is made up of four planetary gear sets on October 15th, 2013,8,556,768 B2 of US
More gear planetary transmission systems realize the variation of eight gears by three brakes and three clutches.First group
Planetary gear exports a rotating speed opposite with steering input shaft, and second group of planetary main function is output from first group
The reverse speed or changeed back forward rotational speed that planetary gear passes over, finally by what is formed by the 3rd group and the 4th group
Combined planetary gear group realizes eight forward gears, one retreating gear.
It is comprehensive although using automatic transmission a large amount of introductions existing in the prior art of planetary gear construction at present
Consider the factors such as gear number, gear range, efficiency, transmission dimensions and weight, it is empty that the prior art still possesses very big improvement
Between.Especially for the gear number for increasing automatic transmission, the quantity of planetary gear set, clutch and brake also increases therewith
It is more, cause the oversized of speed changer, be unfavorable for arrangement of the speed changer in vehicle transmission system.
The content of the invention
(1) purpose
The purpose of the invention is to provide a kind of multi-shifting speed variators of planetary gear construction, it can overcome the prior art
Difficult point, make up the deficiency of existing market, it is proposed that a kind of compact-sized, convenient for motor vehicles multi-shifting speed variator.
(2) technical solution
The present invention is a kind of multi-shifting speed variator of planetary gear construction, it contains housing, input link, output link,
First, second, third planetary gear set, first, second, third and fourth, five, six, seven interconnecting components and first, second, third and fourth, five, six
Torque transmitter.First, second, third planetary gear set is arranged in order from input terminal to output terminal；First, second, third and fourthth,
5th, six torque transmitters include three brakes and three clutches, between position connection relation be：Firstth,
Two and the 3rd torque transmitter is between second and third planet gear set side by side close to housing；Four, the 5th and the 6th
Torque transmitter is between the first and second planetary gear sets, wherein the 4th torque transmitter closes on pivot, the
5th, the 6th torque transmitter is located above the 4th torque transmitter side by side.And above-mentioned each component is respectively positioned within housing.
The housing is the shell of planetary transmission, be it is fixed, for accommodate and support speed changer its
His component, shape and structure is because depending on layout, and there is no general fixed forms.
The input link is the input shaft of planetary transmission, by the input link by the output speed of engine
Planetary transmission transmission is input to torque, in this scenario only there are one input link, positioned at the first planet tooth
In front of wheel group.
The output link is the output shaft of planetary transmission, by the output link by planetary transmission
Rotating speed and torque output are to subsequent transmission shaft, in this scenario only there are one output link, after third planet gear set
Side.
The first planetary gear set is positive sign planetary gear set, by three sun gear, gear ring, planet carrier basic building block groups
Into, sun gear, planet carrier, gear ring are followed successively by between three from inside to outside, a planetary gear and sun gear external toothing, in addition one
A planetary gear and gear ring internal messing.
Second planetary gear set is negative sign planetary gear set, by three sun gear, gear ring, planet carrier basic building block groups
Into sun gear, planet carrier, gear ring being followed successively by between three from inside to outside, the planetary gear and sun gear external toothing, with being nibbled in gear ring
It closes；Similarly, third planet gear set structure composition is identical with the planetary gear set.
The third planet gear set is negative sign planetary gear set, by three sun gear, gear ring, planet carrier basic building block groups
Into sun gear, planet carrier, gear ring being followed successively by between three from inside to outside, the planetary gear and sun gear external toothing, with being nibbled in gear ring
It closes；Similarly, the second planetary gear set structure composition such as the planetary gear set are identical.
First interconnecting component is connecting shaft, and the interconnecting component is by the same input link of the sun gear of first planetary gear set
It is fixedly linked.
Second interconnecting component is connecting shaft, which consolidates the gear ring of third planet gear set with output link
It is fixed to be connected.
3rd interconnecting component is connecting shaft, and the interconnecting component is by first planetary gear set planet carrier with the second planet tooth
Wheel group planet carrier is fixedly linked, and is connected with the first torque transmitter.
4th interconnecting component is connecting shaft, which passes the second planetary gear set sun gear and the second torque
Delivery device is connected.
5th interconnecting component is connecting shaft, and the interconnecting component is by third planet gear set carrier and the three, the 4th
It is connected with the 5th torque transmitter.
6th interconnecting component is connecting shaft, which turns round first planetary gear set gear ring and the five, the 6th
Square transfer device is connected.
7th interconnecting component is connecting shaft, and the interconnecting component is by the second planetary gear set gear ring with third planet gear
Group tooth sun gear is fixedly linked, and is connected with the 6th torque transmitter.
Six torque transmitters, are all wet friction formula binding member, pass through connecing for different torque transmitters
It closes so that corresponding two components link together, there is identical motion state.Six torque transmitters can select
The locking of property is connected corresponding two components are temporary.
First torque transmitter can be selectively latched, by first planetary gear set planet carrier and the second planet tooth
Wheel group planet carrier is connected with housing.
Second torque transmitter can be selectively latched, and the second planetary gear set sun gear has been connected with housing
Come.
3rd torque transmitter can be selectively latched, and third planet gear set carrier has been connected with housing
Come.
4th torque transmitter can be selectively latched, by first planetary gear set sun gear and third planet tooth
Wheel group planet carrier connects.
5th torque transmitter can be selectively latched, by first planetary gear set gear ring and third planet gear
Group planet carrier connects.
6th torque transmitter can be selectively latched, by first planetary gear set gear ring and third planet gear
Group sun gear connects.
Wherein, before transmission scheme involved in the present invention is by controlling the engagement of six torque transmitters to generate eight
It reverses gear into gear and one, realizes speed changing function.
Wherein, above three planetary gear set is followed successively by first planetary gear set, the second planetary gear since input terminal
Group, third planet gear set and output shaft；Involved gear is all helical teeth tooth form in above-mentioned three groups of planetary gear sets.
Wherein, first, second, third torque transmitter is friction disk type wet brake.
Wherein, the four, the five, the 6th torque transmitters are friction disk type wet clutch.
Wherein, the size gear ring of brake and clutch, it is necessary to according to the torsion that is exported of matched power input device
Square is calculated and obtained, and the present invention is not intended to limit specifically used model and specification.
The structure working principle overview of the present invention is as follows：When all torque transmitters are in discrete state, the planet tooth
Set mechanism degree of freedom is 4, does not have power transmission between input link and output link；When second, third, the 5th torque transfer
When device is in blocking, the second planetary gear set sun gear is fixed, and third planet gear set carrier is fixed, and first
Planetary gear set carrier is identical with third planet gear set carrier rotating speed, and the degree of freedom of planetary gear mechanism is reduced to 1, input
There are power transmission, input link rotating speed and the ratios of output link rotating speed between output link to keep off gearratio for one.
When the first, second, the 5th torque transmitter is in blocking, first planetary gear set gear ring and the second row
Star gear set carrier is fixed, and the second planetary gear set sun gear is fixed, first planetary gear set planet carrier and the third line
Star gear set carrier rotating speed is identical, and the degree of freedom of planetary gear mechanism is reduced to 1, and there are power biographies between input and output component
It passs, the ratio of input link rotating speed and output link rotating speed is two gear gearratios.
When second, the five, the 6th torque transmitters are in blocking, the second planetary gear set sun gear is consolidated
Fixed, first planetary gear set planet carrier is identical with third planet gear set carrier rotating speed, first planetary gear set planet carrier and
Second planetary gear set gear ring is identical with third planet gear set gear ring rotating speed, and the degree of freedom of planetary gear mechanism is reduced to 1, input
There are power transmission, input link rotating speed and the ratios of output link rotating speed between output link to keep off gearratios for three.
When second, the four, the 5th torque transmitters are in blocking, the second planetary gear set sun gear is consolidated
Fixed, first planetary gear set sun gear is identical with third planet gear set carrier rotating speed, first planetary gear set planet carrier and
Third planet gear set carrier rotating speed is identical, and the degree of freedom of planetary gear mechanism is reduced to 1, exists between input and output component dynamic
Power is transferred, and the ratio of input link rotating speed and output link rotating speed is four gear gearratios.
When the four, the five, the 6th torque transmitters are in blocking, first planetary gear set sun gear and the 3rd
Planetary gear set carrier rotating speed is identical, and first planetary gear set planet carrier is identical with third planet gear set carrier rotating speed,
First planetary gear set planet carrier is identical with the second planetary gear set gear ring and third planet gear set gear ring rotating speed, planetary gear
The degree of freedom of mechanism is reduced to 1, there are power transmission between input and output component, the ratio of input link rotating speed and output link rotating speed
It is worth for five gear gearratios.
When second, the four, the 6th torque transmitters are in blocking, the second planetary gear set sun gear is consolidated
Fixed, first planetary gear set planet carrier is identical with third planet gear set carrier rotating speed, first planetary gear set planet carrier and
Second planetary gear set gear ring is identical with third planet gear set gear ring rotating speed, and the degree of freedom of planetary gear mechanism is reduced to 1, input
There are power transmission, input link rotating speed and the ratios of output link rotating speed between output link to keep off gearratios for six.
When first, the four, the 6th torque transmitters are in blocking, first planetary gear set gear ring and the second row
Star gear set carrier is fixed, and first planetary gear set planet carrier is identical with third planet gear set carrier rotating speed, and first
Planetary gear set carrier is identical with the second planetary gear set gear ring and third planet gear set gear ring rotating speed, planetary gear mechanism
Degree of freedom be reduced to 1, there are power transmission, input link rotating speed and the ratios of output link rotating speed between input and output component to be
Seven gear gearratios.
When the first, second, the 4th torque transmitter is in blocking, first planetary gear set gear ring and the second row
Star gear set carrier is fixed, and the second planetary gear set sun gear is fixed, first planetary gear set planet carrier and the third line
Star gear set carrier rotating speed is identical, and the degree of freedom of planetary gear mechanism is reduced to 1, and there are power biographies between input and output component
It passs, the ratio of input link rotating speed and output link rotating speed is eight gear gearratios.
When second, third, the 6th torque transmitter be in blocking when, the second planetary gear set sun gear is consolidated
Fixed, third planet gear set carrier is fixed, first planetary gear set planet carrier and the second planetary gear set gear ring and the 3rd
Planetary gear set gear ring rotating speed is identical, and the degree of freedom of planetary gear mechanism is reduced to 1, and there are power biographies between input and output component
It passs, the ratio of input link rotating speed and output link rotating speed is back gear ratio.
(3) advantage
The gearratio of corresponding gear can be obtained by following shift logic sequence while being latched three torque transmitters, described
Dynamical system can realize eight forward gear gearratios and a back gear ratio altogether, and the gearshift between adjacent gear is all full
Only the simple of one torque transmitter of conversion shifts gears requirement to realize smooth shift to foot.
The multi-shifting speed variator can obtain eight forward gear gearratios, after the gear number increase of power train, increase and start
Machine is operated in the probability under efficient routine, is conducive to improve fuel consumption rate；More gears are also reduced between adjacent gear
The saltus step of gearratio advantageously reduces shift shock and improves riding comfort.
In addition, the basic building block and torque transmitter of the planetary gear set of the multi-shifting speed variator possess relatively low rotating speed and
Torque is conducive to reduce the abrasion between mesh component, reduces the design size of component and device so as to further lower manufacture
Cost.
Description of the drawings
Fig. 1 is the specific embodiment structure diagram of nine speed transmission according to the present invention.
Reference numeral
0 housing
1 first interconnecting component
2 second interconnecting components
3 the 3rd interconnecting components
4 the 4th interconnecting components
5 the 5th interconnecting components
6 the 6th interconnecting components
7 the 7th interconnecting components
03 first torque transmitter
04 second torque transmitter
05 the 3rd torque transmitter
15 the 4th torque transmitters
56 the 5th torque transmitters
67 the 6th torque transmitters
IN input shafts
OUT output shafts
P1 first planetary gear sets
The second planetary gear sets of P2
P3 third planet gear sets
S1 first planetary gear set sun gears
S2 the second planetary gear set sun gears
S3 third planet gear set sun gears
A1 first planetary gear set planet carriers
The second planetary gear set carriers of A2
A3 third planet gear set carriers
The first planetary gear of G1 first planetary gear sets
The second planetary gear of G10 first planetary gear sets
The planetary gear that the second planetary gear sets of G2 are engaged with sun gear
G3 third planet gear set planetary gears
R1 first planetary gear set gear rings
R2 the second planetary gear set gear rings
R3 third planet gear set gear rings
Specific embodiment
In following illustrative in nature be only it is exemplary and be not intended to limit the present invention, using or use.
A kind of multi-shifting speed variator of planetary gear construction of the present invention, it includes housing；Input link；Output link；Firstth,
Second, third planetary gear set；First interconnecting component；Second interconnecting component；3rd interconnecting component；4th interconnecting component；5th
Interconnecting component；6th interconnecting component；7th interconnecting component and first, second, third and fourth, five, six totally six torque transmitter groups
Into the position connection relation between them is：First, second, third planetary gear set is arranged in order from input terminal to output terminal；
Six torque transmitters include three brakes, three clutches, and the first and second torque transmitters are located at the second He
Side by side close to housing between third planet gear set；3rd torque transmitter is located on the right side of third planet gear set and output structure
Part homonymy；Four, the 5th and the 6th torque transmitter is between the first and second planetary gear sets, wherein the 4th torque passes
Delivery device closes on pivot, and the five, the 6th torque transmitters are located above the 4th torque transmitter side by side.It is above-mentioned each
Component is respectively positioned in housing.
First, the embodiment of multi-speed automatic transmission of the invention has forever between the element of three planetary gear sets
The mechanical connection of long property is set.For example, it is solid between the gear ring of first planetary gear set and the planet carrier of the second planetary gear set
Fixed connection；It is to be fixedly connected between the gear ring of second planetary gear set and the sun gear of third planet gear set...
With reference to figure 1, the speed changer scheme include input link IN, first planetary gear set P1, the second planetary gear set P2,
Third planet gear set P3, housing 0, output link OUT, the first torque transmitter 03, the second torque transmitter the 04, the 3rd
Torque transmitter 05, the 4th torque transmitter 15, the 5th torque transmitter 56 and the 6th torque transmitter 67.At this
In the embodiment of invention, three planetary gear sets P1, P2, P3 are simple planetary groups, as described below.
First planetary gear set P1 includes first planetary gear set sun gear S1, first planetary gear set planet carrier A1,
First planetary gear set gear ring R1 and first planetary gear set planetary gear G1 and G10 (only represent one in this group of planetary gear
Group).First planetary gear set sun gear S1 is fixedly connected by the first interconnecting component 1 with input link IN；First planetary gear
Group gear ring R1 is fixedly connected with the 6th interconnecting component 6；First planetary gear set planet carrier A1 passes through the 3rd interconnecting component 3 and second
Planetary gear set P2 planet carriers A2 is fixedly connected.
Second planetary gear set P2 includes the second planetary gear set sun gear S2, the second planetary gear set carrier A2,
Second planetary gear set R2, the second planetary gear set gear ring R2 and the second planetary gear set planetary gear G2 (only represent each group row
One group in star-wheel).Second planetary gear set P2 sun gears S2 is fixedly connected with the 4th interconnecting component 4；Second planetary gear set
P2 planet carriers A2 is fixedly linked by the 3rd interconnecting component 3 and first planetary gear set P1 planet carriers A1；Second planetary gear set
P2 gear rings R2 is fixedly linked by the 7th interconnecting component 7 and third planet gear set P3 sun gears S3.
Third planet gear set P3 include third planet gear set sun gear S3, third planet gear set carrier A3 and
Third planet gear set planetary gear G3 (only represents one in this group of planetary gear).Third planet gear set P3 gear rings R3 passes through
Second interconnecting component 2 is fixedly linked with output link OUT；Third planet gear set P3 planet carriers A3 and 5 phase of the 5th interconnecting component
Even；Third planet gear set P3 sun gears S3 is fixedly linked by the 7th interconnecting component 7 and the second planetary gear set P2 gear rings R2.
Input shaft IN by fluid torque-converter (not shown) it is lasting be connected to engine (not shown).Output shaft OUT is held
Continuous is connected to final gear unit or transfer gear (not shown).
First planetary gear set P1 is adjacent to fluid torque-converter (not shown), and the second planetary gear set P2 is adjacent to the first planet tooth
Wheel group P1, third planet gear set P3 are adjacent to the second planetary gear set P2.
Illustrate the gear shift operation of the embodiment with reference to rank rear shift logic figure as shown in table 1 and each gear gearratio.
The speed changer can be reversed gear with eight forward gear speed ratios or torque ratio and one speed ratio or torque ratio by torque from input shaft
IN is transferred to output shaft OUT.By three in torque-transmitting mechanisms (shifting element) engagements, can obtain each forward gear with
And the gearratio or torque ratio to reverse gear.As shown in table 1, it is activated or engages to realize that the torque of various shifting states transfers machine
The various combination truth tables of structure.As shown in table 1, "×" represents the specific torque transmitter (shifting element) and is engaged to
It realizes and it is expected shifting state.When first planetary gear set P1, the second planetary gear set P2, the fixed of third planet gear set P3 pass
When dynamic ratio is respectively 4.0000, -2.0000, -2.2663, the gear ratio value of each gear of speed changer as shown in table 1 is acquired.Example
Such as, change can be realized by engaging the second torque transmitter 04, the 3rd torque transmitter 05, the 6th torque transmitter 67
Fast device gear reversing function.Similar, the various combination engaged by shifting element realizes eight forward gear ratios, as shown in table 1
Like that.
The preceding description of operation and shifting state to six shift transmissions is assumed：First, it is specific in given shifting state
All shifting elements referred to depart from；Secondly, during the gearshift (changing shifting state) between adjacent shifting state,
The shifting element engaged under two shifting states will remain engaged with state.
The present invention's says what face was substantially merely exemplary, and the deformation being allowed to without departing from the present invention is intended to be included in this
In the range of invention.This modification is considered without departing from the spirit and scope of the present invention.
Transmission scheme gear ratio calculation method is as follows：
The kinematical equation group of 1 planetary gear mechanism is as follows：
2 calculate each rotating speed, and kinematics formula is considered as M × N=A, and computational methods are as follows：
N=(MT×M)-1×MT×A
Symbol description is as follows in formula：
N is vectorial to solve
M coefficient matrixes
A constant terms
The 3rd interconnecting component rotating speeds of n1
The 4th interconnecting component rotating speeds of n2
The 5th interconnecting component rotating speeds of n3
The 6th interconnecting component rotating speeds of n4
The 7th interconnecting component rotating speeds of n5
N6 the first interconnecting component rotating speeds
N7 the second interconnecting component rotating speeds
I1 first planetary gear set fixed drive ratios
I2 the second planetary gear set fixed drive ratios
I3 third planet gear set fixed drive ratios
A the first torque transmitter joint efficiencies
B the second torque transmitter joint efficiencies
The 3rd torque transmitter joint efficiencies of c
The 4th torque transmitter joint efficiencies of d
The 5th torque transmitter joint efficiencies of e
The 6th torque transmitter joint efficiencies of f
3 gear ratio calculations：
Symbol description in formula：
I gearratios
The 3rd interconnecting component rotating speeds of n1
The 4th interconnecting component rotating speeds of n2
Wherein, it is 1 for the ease of calculating another input shaft IN rotating speeds, other rotating speeds change with input speed and changed.It is logical
Above three formula is crossed, it can (engagement be disconnected for 1 by being closed the assignment of coefficient (a, b, c, d, e, f) to torque transmitter
0), to calculate each rotating speed of different gears and gear gearratio.
The shift logic matrix of 1 scheme 1 of table
"×" represents the specific torque transmitter (shifting element) and is engaged.
Claims (5)
1. a kind of multi-shifting speed variator of planetary gear construction, it is characterised in that：It contains housing, input link, output link,
First, second, third planetary gear set, first, second, third and fourth, five, six, seven interconnecting components and first, second, third and fourth, five, six
Torque transmitter；First, second, third planetary gear set is arranged in order from input terminal to output terminal；First, second, third and fourthth,
5th, six torque transmitters include three brakes and three clutches, and first, second, and third torque transmitter is located at
Side by side close to housing between second and third planet gear set；4th, the 5th and the 6th torque transmitter is located at first and the
Between two planetary gear sets, wherein the 4th torque transmitter closes on pivot, the five, the 6th torque transmitter positions arranged side by side
Above the 4th torque transmitter, and above-mentioned each component is respectively positioned within housing；
The housing is the shell of planetary transmission, is fixed, for accommodating and supporting other structures of speed changer
Part, shape and structure is because depending on layout；
The input link is the input shaft of planetary transmission, by the output speed of engine and is turned by the input link
Square is input to planetary transmission transmission, only there are one input link in the speed changer, positioned at the first planetary gear
Group front；
The output link is the output shaft of planetary transmission, by the output link by the rotating speed of planetary transmission
With torque output to subsequent transmission shaft, only there are one output link in the speed changer, in third planet gear set rear；
The first planetary gear set is positive sign planetary gear set, is made of three sun gear, gear ring, planet carrier basic building blocks,
Be followed successively by sun gear, planet carrier, gear ring between three from inside to outside, a planetary gear of the first planetary gear set with too
Sun wheel external toothing, another planetary gear and gear ring internal messing；
Second planetary gear set is negative sign planetary gear set, is made of three sun gear, gear ring, planet carrier basic building blocks,
Sun gear, planet carrier, gear ring, the planetary gear and sun gear of second planetary gear set are followed successively by between three from inside to outside
External toothing, with gear ring internal messing；
The third planet gear set is negative sign planetary gear set, is made of three sun gear, gear ring, planet carrier basic building blocks,
Sun gear, planet carrier, gear ring, the planetary gear and sun gear of the third planet gear set are followed successively by between three from inside to outside
External toothing, with gear ring internal messing；
First interconnecting component is connecting shaft, which fixes the sun gear of first planetary gear set with input link
It is connected；
Second interconnecting component is connecting shaft, and the interconnecting component is by the gear ring of third planet gear set with output link stationary phase
Even；
3rd interconnecting component is connecting shaft, and the interconnecting component is by first planetary gear set planet carrier with the second planetary gear set
Planet carrier is fixedly linked, and is connected with the first torque transmitter；
4th interconnecting component is connecting shaft, which transfers the second planetary gear set sun gear and the second torque and fill
It puts connected；
5th interconnecting component is connecting shaft, and the interconnecting component is by third planet gear set carrier and the the 3rd, the 4th and the
Five torque transmitters are connected；
6th interconnecting component is connecting shaft, which passes first planetary gear set gear ring and the five, the 6th torques
Delivery device is connected；
7th interconnecting component is connecting shaft, and the interconnecting component is by the second planetary gear set gear ring with third planet gear set tooth
Sun gear is fixedly linked, and is connected with the 6th torque transmitter；
Six torque transmitters, are all wet friction formula binding member, are made by the engagement of different torque transmitters
It obtains corresponding two components to link together, there is identical motion state；Six torque transmitters selective can close
Lock is connected corresponding two components are temporary；
First torque transmitter can be selectively latched, by first planetary gear set planet carrier and the second planetary gear set
Planet carrier is connected with housing；
Second torque transmitter can be selectively latched, and the second planetary gear set sun gear is connected with housing；
3rd torque transmitter can be selectively latched, and third planet gear set carrier is connected with housing；
4th torque transmitter can be selectively latched, by first planetary gear set sun gear and third planet gear set
Planet carrier connects；
5th torque transmitter can be selectively latched, by first planetary gear set gear ring and third planet gear set row
Carrier connects；
6th torque transmitter can be selectively latched, by first planetary gear set gear ring with third planet gear set too
Sun wheel connects.
2. a kind of multi-shifting speed variator of planetary gear construction according to claim 1, it is characterised in that：The speed changer leads to
The engagement for crossing six torque transmitters of control generates eight forward gears and one reverses gear, and realizes speed changing function.
3. a kind of multi-shifting speed variator of planetary gear construction according to claim 1, it is characterised in that：Three groups of planetary gears
Involved gear is all helical teeth tooth form in group.
4. a kind of multi-shifting speed variator of planetary gear construction according to claim 1, it is characterised in that：First, secondth,
Three torque transmitters be friction disk type wet brake, the four, the five, the 6th torque transmitters for friction disk type wet type from
Clutch.
5. a kind of multi-shifting speed variator of planetary gear construction according to claim 1, it is characterised in that：Brake and clutch
The size gear ring of device, it is necessary to according to the torque arithmetic that is exported of matched power input device and obtain, being not intended to limit specifically makes
With model and specification.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201410418597.1A CN104373534B (en) | 2014-08-22 | 2014-08-22 | A kind of multi-shifting speed variator of planetary gear construction |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201410418597.1A CN104373534B (en) | 2014-08-22 | 2014-08-22 | A kind of multi-shifting speed variator of planetary gear construction |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN104373534A CN104373534A (en) | 2015-02-25 |
| CN104373534B true CN104373534B (en) | 2018-06-05 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201410418597.1A Active CN104373534B (en) | 2014-08-22 | 2014-08-22 | A kind of multi-shifting speed variator of planetary gear construction |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN116379112B (en) * | 2023-06-05 | 2023-07-28 | 北京航空航天大学 | Multi-gear planetary gear speed change mechanism and automatic speed changer thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0757189A2 (en) * | 1995-07-31 | 1997-02-05 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN1531634A (en) * | 2001-03-30 | 2004-09-22 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage transmission |
| DE102006001760A1 (en) * | 2006-01-13 | 2007-08-09 | Zf Friedrichshafen Ag | Multistep gear for use in motor vehicle automatic transmission, has planetary sets arranged in axial direction, brake coupled at housing, and output shaft connected with internal gear of one planatery set |
| CN101021247A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN101021257A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5884248A (en) * | 1981-11-11 | 1983-05-20 | Toyota Motor Corp | Driving equipment for automobile |
| JP2614217B2 (en) * | 1986-12-09 | 1997-05-28 | アイシン・エィ・ダブリュ株式会社 | Automatic transmission |
-
2014
- 2014-08-22 CN CN201410418597.1A patent/CN104373534B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0757189A2 (en) * | 1995-07-31 | 1997-02-05 | Aisin Aw Co., Ltd. | Automatic transmission |
| CN1531634A (en) * | 2001-03-30 | 2004-09-22 | 腓特烈斯港齿轮工厂股份公司 | Multi-stage transmission |
| DE102006001760A1 (en) * | 2006-01-13 | 2007-08-09 | Zf Friedrichshafen Ag | Multistep gear for use in motor vehicle automatic transmission, has planetary sets arranged in axial direction, brake coupled at housing, and output shaft connected with internal gear of one planatery set |
| CN101021247A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
| CN101021257A (en) * | 2006-02-14 | 2007-08-22 | Zf腓德烈斯哈芬股份公司 | Multi-gear transmission |
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| Publication number | Publication date |
|---|---|
| CN104373534A (en) | 2015-02-25 |
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