CN105114562A - Multi-gear transmission with planet gear structure mode - Google Patents
Multi-gear transmission with planet gear structure mode Download PDFInfo
- Publication number
- CN105114562A CN105114562A CN201510519073.6A CN201510519073A CN105114562A CN 105114562 A CN105114562 A CN 105114562A CN 201510519073 A CN201510519073 A CN 201510519073A CN 105114562 A CN105114562 A CN 105114562A
- Authority
- CN
- China
- Prior art keywords
- clutch
- gear
- axle
- break
- planet
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- 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
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- 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
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/2012—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with four 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
- F16H2306/00—Shifting
Abstract
The invention discloses a multi-gear transmission with a planet gear structure mode, and belongs to the technical field of automatic transmissions. The multi-gear transmission solves the problems that in the prior art of the automatic transmissions, more elements and a complex structure exist, and especially, a slightly progressive well graded transmission ratio series and the good meshing efficiency are difficult to supply. The multi-gear transmission comprises a first planet gear set, a second planet gear set, a third planet gear set and a fourth planet gear set which are sequentially arranged front and back along a main rotation shaft and six gear shifting elements, and the gear shifting elements are allowed to be selectively controlled, so that nine forward gears and one reverse gear are formed between an input shaft and an output shaft of the transmission; the input shaft is separably connected with a fifth shaft through a first clutch, and the fifth shaft is connected with a first sun gear and a second sun gear and connected to a shell through a first brake; the input shaft is separably connected with a fourth shaft connected to a first gear ring through a second clutch and connected with a third shaft through a third clutch; the output shaft is connected with a fourth planet carrier.
Description
Technical field
The invention belongs to automatic transmission technical field, relate to a kind of automatic transmission unit, especially for the Power Train of Motor Vehicle, be specifically related to a kind of multispeed manual transmission of planetary gear construction mode.
Background technique
The dynamical system of Motor Vehicle comprises motor, multispeed manual transmission and differential or main reducing gear composition.Multispeed manual transmission is by allowing that motor is improved the whole operating range of vehicle in its torque range by multi-pass operation.In speed changer, the quantity of available forward velocity ratio (forward gear) determines the number of times that engine torque bands repeats.The negligible amounts of forward gear will limit the whole velocity range of vehicle, and therefore needs relatively large motor, can produce wider speed and torque range.
The automatic transmission of current four speed automatic transmissions particularly planetary gear construction constantly popularizes in China, the operating characteristics of these transmissions improved vehicle and fuel economy.The quantity of forward velocity ratio increases the step-length that will reduce between velocity ratio, and therefore under accelerating in normal vehicle, makes operator substantially discover the shift quality improving speed changer less than speed than replacing.Six gears, seven gears, eight gears, nine speed automatic transmissions have obvious advantage than four gears and five speed automatic transmissions in the fuel economy of vehicle acceleration and improvement, but because the size of these speed changers is large, the complexity of structure and cost high, these automatic transmission universal on be also subject to certain restrictions.
The vehicular automatic transmission of the planetary gear construction mode that generally speaking can automatically switch repeatedly is described in the prior art and is developed further and improve all the time.Such as ZF company CN104114902A, German DaimlerChrysler AG CN102203458A and GM company of U.S. US7695398B2 disclose the multistage automatic transmission of planetary gear construction mode, and this automatic transmission has four planetary gear set and six gearshift control units.
Summary of the invention
Technical problem to be solved by this invention overcomes prior art to there is more the number of components, complicated structure, particularly be difficult to the problem that slightly progressive, that classification is good velocity ratio series and good meshing efficiency are provided, provide a kind of multispeed manual transmission of planetary gear construction mode.
For solving the problems of the technologies described above, the present invention adopts following technological scheme to realize, and accompanying drawings is as follows:
Object of the present invention is especially, provides a kind of compact automatic transmission unit with a large amount of advance gear.According to the present invention, this object is realized by the feature of claim 1.
According to the present invention, propose a kind of automatic transmission unit, especially automatic speed changer for vehicle unit, described gearbox unit has: along main rotating shaft successive ground four planetary gear set arranging and first, second, third and fourth planetary gear set; Six gearshift switching members, described gearshift switching member allows optionally to engage nine advance transmission gears; Input shaft can not be connected in relative rotation with the common outside friction disc support of three clutches, then engages the second sun gear and the first sun gear, the first gear ring, the third line carrier and the 4th gear ring respectively by three clutches; And pto＝power take-off, described pto＝power take-off can not be connected with fourth planet wheel carrier in relative rotation.A kind of automatic transmission unit can be provided thus, this automatic transmission unit has that gear quantity is many, classification is good and transmission range is enough, compact structure.
Two components are interpreted as " can not connect in relative rotation " connected by the form such as spline or rigidity, when two components are rotated, there is equal angular velocity.
" clutch " is especially interpreted as being arranged for the unit that the clutch element selectivity that makes two to arrange rotationally can not connect in relative rotation or separate." break " is especially interpreted as being arranged for and makes rotating brake component and the fixed unit especially case of transmission selectivity unit that can not be connected in relative rotation or separate.
Under this meaning, putting in order of four planetary gears is especially interpreted as " along the first, second, third and fourth planetary gear set speed changer that arranges of main rotating shaft successive ground ", these planetary gear set speed changers put in order along main rotating shaft arrange with these, wherein, first planet wheel speed is advantageously towards input shaft side, and fourth planet wheel speed is advantageously towards output shaft side.In addition, in order to simplify, " first to fourth sun gear ", " first to fourth planetary wheel carrier ", " first to fourth gear ring " are interpreted as configuring respectively to the sun gear of the fast device of first to fourth planet wheel change group or planetary wheel carrier or gear ring, namely such as first planet wheel carrier are interpreted as to the planetary wheel carrier of first planet wheels speed changer.
A multispeed manual transmission for planetary gear construction mode, comprises four planetary gear set be arranged in housing G, eight axles that can rotate and six gearshift switching members;
Described four planetary gear set are respectively first planet wheels P1, the second planetary gear set P2, third planet wheels P3, fourth planet wheels P4;
Described first planet wheels P1 is arranged on input side, and described first planet wheels Pl comprises the first sun gear P11, first planet wheel carrier P12 and the first gear ring P13; Planetary wheel carrier P12 guides planet wheel P14 on circular orbit, planet wheel P14 can on planetary wheel carrier P12 circular-rotation; Planet wheel P14 is with sun gear P11 and be meshed with gear ring P13;
Described second planetary gear set P2, third planet wheels P3 are successively set on centre; Described second planetary gear set P2 comprises the second sun gear P21, the second planetary wheel carrier P22 and the second gear ring P23; Planetary wheel carrier P22 guides planet wheel P24 on circular orbit, planet wheel P24 can on planetary wheel carrier P22 circular-rotation; Planet wheel P24 is with sun gear P21 and be meshed with gear ring P23.
Described third planet wheels P3 comprises the 3rd sun gear P31, third planet wheel carrier P32 and the 3rd gear ring P33; Planetary wheel carrier P32 guides planet wheel P34 on circular orbit, planet wheel P34 can on planetary wheel carrier P32 circular-rotation; Planet wheel P34 is with sun gear P31 and be meshed with gear ring P33;
Described fourth planet wheel speed P4 is arranged on outlet side, and described fourth planet wheels P4 comprises the 4th sun gear P41, fourth planet wheel carrier P42 and the 4th gear ring P43; Planetary wheel carrier P42 guides planet wheel P44 on circular orbit, planet wheel P44 can on planetary wheel carrier P42 circular-rotation; Planet wheel P44 is with sun gear P41 and be meshed with gear ring P43.
Described eight axles that can rotate are respectively input shaft 1, output shaft 2, the 3rd axle 3, the 4th axle 4, the 5th axle 5, the 6th axle 6, the 7th axle 7 and the 8th axle 8;
Described 3rd axle 3 can not be connected in relative rotation with the third line carrier P32, the 4th gear ring P43,
Described 4th axle 4 can not be connected in relative rotation with the first gear ring P13,
Described 5th axle 5 can not be connected in relative rotation with the first sun gear P11, the second sun gear P21,
Described 6th axle 6 can not be connected in relative rotation with the second planet carrier P22,
Described 7th axle 7 can not be connected in relative rotation with the 3rd sun gear P31, the 4th sun gear P41,
Described 8th axle 8 can not be connected in relative rotation with the first row carrier P12, the second gear ring P23, the 3rd gear ring P33
Described output shaft 2 can not be connected in relative rotation with fourth line carrier P42.
Described six gearshift switching members are made up of three breaks and three clutches, described three breaks are respectively the first break B1, second brake B2, the 3rd break B3, and described three clutches are respectively first clutch C1, second clutch C2, the 3rd clutch C3;
Described six gearshift switching members optionally engage and make to obtain different velocity ratios between input shaft 1 and output shaft 2, thus nine forward gears can be realized and one reverse gear;
First clutch C1 is that steerable turning round refuses transfer unit, described input shaft 1 and the 5th axle 5 to be coupled together selectively;
Second clutch C2 is that steerable turning round refuses transfer unit, described input shaft 1 and the 4th axle 4 to be coupled together selectively;
3rd clutch C3 is that steerable turning round refuses transfer unit, described input shaft 1 and the 3rd axle 3 to be coupled together selectively;
First break B1 is that steerable turning round refuses transfer unit, to be coupled together with housing G by described 5th axle 5 selectively;
Second brake B2 is that steerable turning round refuses transfer unit, to be coupled together with housing G by described 6th axle 6 selectively;
3rd break B3 is that steerable turning round refuses transfer unit, to be coupled together with housing G by described 7th axle 7 selectively;
Described first clutch C1 comprises first clutch a element C11 and first clutch b element C12, second clutch C2 comprises second clutch a element C21 and second clutch b element C22, the 3rd clutch C3 comprise the 3rd clutch a element C31 and the 3rd clutch b element C32;
Described first break B1 comprises the first break a element B11, and second brake B2 comprises second brake a element B21, and described 3rd break B3 comprises the 3rd break a element B31.
Be provided with described first clutch C1 when being handled, make the described first clutch a element C11 that can not be connected in relative rotation with described input shaft 1 and couple together with the described first clutch b element C12 that described 5th axle 5 can not be connected in relative rotation; Be provided with described second clutch C2 when being handled, make the described second clutch a element C21 that can not be connected in relative rotation with described input shaft 1 and couple together with the described second clutch b element C22 that described 4th axle 4 can not be connected in relative rotation; Be provided with described 3rd clutch C3 when being handled, make the described 3rd clutch a element C31 that can not be connected in relative rotation with described input shaft 1 and couple together with the described 3rd clutch b element C32 that described 3rd axle 3 can not be connected in relative rotation.
Be provided with described first break B1 when being handled, the described first break a element B11 and housing G that can not be connected in relative rotation with described 5th axle 5 is coupled together; Be provided with described second brake B2 when being handled, the described second brake a element B21 and housing G that can not be connected in relative rotation with described 6th axle 6 is coupled together, be provided with described 3rd break B3 when being handled, the described 3rd break a element B31 and housing G that can not be connected in relative rotation with described 7th axle 7 is coupled together.
Described input shaft 1 can not be connected in relative rotation with first clutch a element C11, second clutch a element C21, the 3rd clutch a element C31.
By closed second and the 3rd break B2, B3 and second clutch C2 obtains the first forward gear, by closed first and the 3rd break B1, B3 and second clutch C2 obtains the second forward gear, by closed 3rd break B3 and first and second clutch C1, C2 obtains the 3rd forward gear, by closed 3rd break B3 and first and the 3rd clutch C1, C3 obtains the 4th forward gear, or by closed 3rd break B3 and second and the 3rd clutch C2, C3 obtains the 4th forward gear, by closed first, second and the 3rd clutch C1, C2, C3 obtains the 5th forward gear, by closed first break B1 and second and the 3rd clutch C2, C3 obtains the 6th forward gear, by closed second brake B2 and second and the 3rd clutch C2, C3 obtains the 7th forward gear, by closed first and second break B1, B2 and the 3rd clutch C3 obtains the 8th forward gear, by closed second brake B2 and first and the 3rd clutch C1, C3 obtains the 9th forward gear, and by closed second and the 3rd break B2, B3 and first clutch C1 is reversed gear.
Described first, second, third and fourth planetary gear set Pl, P2, P3, P4 are configured to negative ratio epicyclic gear group;
Described planetary gear set is observed vertically and is arranged by the order of first planet gear train Pl, the second planetary gear set P2, third planet gear train P3, fourth planet gear train P4.
Described first, second, and third clutch C1, C2, C3 observe vertically and are arranged side by side and have a common outside friction disc support as chip gearshift switching member;
Each gearshift switching member C1 of described speed changer, C2, C3, B1, B2, B3 are constructed to be permeable to the gearshift switching member switched as required, especially the gearshift switching member of electromechanics and/or electric liquid
Compared with prior art the invention has the beneficial effects as follows:
The present invention can provide nine forward gears and one to reverse gear, have that gear quantity is many, classification be good and transmission range is enough, advantage that load that is high, each element of compact structure, transmission efficiency is little, reduce the number of components simultaneously and its weight and cost of production minimized.
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the present invention is further illustrated:
Fig. 1 is the explanatory view of automatic transmission unit according to first embodiment of the invention;
In figure:
G housing
1 input shaft;
2 output shafts;
3 the 3rd axles;
4 the 4th axles;
5 the 5th axles;
6 the 6th axles;
7 the 7th axles;
8 the 8th axles;
C1 first clutch;
C2 second clutch;
C3 the 3rd clutch;
B1 first break;
B2 second brake;
B3 the 3rd break;
P1 first planet gear train;
P2 second planetary gear set;
P3 third planet gear train;
P4 fourth planet gear train;
P11 first sun gear;
P12 the first row carrier;
P13 first gear ring;
P14 the first row star-wheel;
P21 second sun gear;
P22 second planet carrier;
P23 second gear ring;
P24 second planet wheel;
P31 the 3rd sun gear;
P32 the third line carrier;
P33 the 3rd gear ring;
P34 the third line star-wheel;
P41 the 4th sun gear;
P42 fourth line carrier;
P43 the 4th gear ring;
P44 fourth line star-wheel;
C11 first clutch a element;
C21 second clutch a element;
C31 the 3rd clutch a element;
C12 first clutch b element;
C22 second clutch b element;
C32 the 3rd clutch b element;
B11 first break a element;
B21 second brake a element;
B31 the 3rd break a element.
Embodiment
Below in conjunction with accompanying drawing, the present invention is explained in detail:
Fig. 1 shows an embodiment of an automatic transmission unit, and this automatic transmission unit is configured to automatic speed changer for vehicle unit.Automatic transmission unit has four planetary gear set Pl, P2, P3, P4.First planet wheels Pl, the second planetary gear set P2, third planet wheels P3 and fourth planet wheels P4 successive ground are arranged along main rotating shaft.Whole planetary gear set Pl, P2, P3, P4 of automatic transmission unit have single-stage planetary wheels.Gearbox unit has six gearshift switching members C1, C2, C3, B1, B2, B3.These gearshift switching members be arranged for conversion just in time nine advance automatic transmission gear Vl, V2, V3, V4, V5, V6, V7, V8, V9 and to reverse gear VR.But automatic transmission unit also can carry out work with only eight advance transmission gears, such as, by not changing the first advance transmission gear Vl or the 9th advance transmission gear V9.
Automatic transmission unit is arranged for and the driving machine be not shown specifically of Motor Vehicle is connected with the driving wheel be not shown specifically of Motor Vehicle.By means of the gear ratio between the adjustable driving machine of gearbox unit and driving wheel.Gearbox unit can with combination drive model calling, can driving moment be changed by means of this combination drive module.In addition, can CVT be realized by means of combination drive module and gearbox unit, can realize thus a gear ratio at least can in regional area the gearbox unit of step-less adjustment.
Automatic transmission unit has input shaft 1, and this input shaft is arranged for and driving moment is incorporated in gearbox unit.Can connect a module be not shown specifically at input shaft 1, this module especially should be arranged for and provide starting function.Torque-converters or wet type start clutch such as can be considered as the module be connected to above.But in principle also can by the module integration being arranged for starting in gearbox unit or such as use clutch unit one of C1, C2, C3, B1, B2, B3 to start to walk.
In addition, automatic transmission unit has pto＝power take-off 2, and this pto＝power take-off is arranged for draws driving moment from gearbox unit.Pto＝power take-off 2 is arranged for and is connected with the driving wheel of Motor Vehicle.A module be not shown specifically can be connected below at pto＝power take-off 2---the moment of drawing from automatic transmission unit can by means of this module assignment to driving wheel, such as be arranged for the planetary gear of the speed discrepancy compensated between driving wheel, or driving moment distributed to the a11wheel drive unit of two different input shafts.Power input shaft 1 and pto＝power take-off 2 can be arranged arbitrarily in principle toward each other.At this, be especially advantageously arranged on the both sides opposite each other of automatic transmission unit coaxially, but also can consider the same side being arranged on gearbox unit.
First planet wheels P1 is arranged on input side.First planet wheels Pl has single-stage planetary wheels.Single-stage planetary wheels comprise the first sun gear P11, first planet wheel carrier P12 and the first gear ring P13.Planetary wheel carrier P12 guides planet wheel P14 on circular orbit.Planet wheel P14 is with sun gear P11 and be meshed with gear ring P13.Planet wheel P14 can on planetary wheel carrier P12 circular-rotation.Characteristic coefficient (planetary gear set fixed drive ratio) K1=-2.021 of first planet wheels Pl.
Second planetary gear set P2 is arranged on input side in centre.Second planetary gear set P2 has single-stage planetary wheels.Single-stage planetary wheels comprise the second sun gear P21, the second planetary wheel carrier P22 and the second gear ring P23.Planetary wheel carrier P22 guides planet wheel P24 on circular orbit.Planet wheel P24 is with sun gear P21 and be meshed with gear ring P23.Planet wheel P24 can on planetary wheel carrier P22 circular-rotation.Characteristic coefficient (planetary gear set fixed drive ratio) K2=-1.979 of the second planetary gear set P2.
Third planet wheels P3 is arranged on outlet side in centre.Third planet wheels P3 has single-stage planetary wheels.Single-stage planetary wheels comprise the 3rd sun gear P31, third planet wheel carrier P32 and the 3rd gear ring P33.Planetary wheel carrier P32 guides planet wheel P34 on circular orbit.Planet wheel P34 is with sun gear P31 and be meshed with gear ring P33.Planet wheel P34 can on planetary wheel carrier P32 circular-rotation.Characteristic coefficient (planetary gear set fixed drive ratio) K3=-2.654 of third planet wheels P3.
Fourth planet wheel speed P4 is arranged on outlet side.Fourth planet wheels P4 has single-stage planetary wheels.Single-stage planetary wheels comprise the 4th sun gear P41, fourth planet wheel carrier P42 and the 4th gear ring P43.Planetary wheel carrier P42 guides planet wheel P44 on circular orbit.Planet wheel P44 is with sun gear P41 and be meshed with gear ring P43.Planet wheel P44 can on planetary wheel carrier P42 circular-rotation.Characteristic coefficient (planetary gear set fixed drive ratio) K4=-2.632 of fourth planet wheels P4.
Three clutches C1, C2, C3 are configured to clutch unit.These clutches have rotating clutch a element C11, C21, a C31 and rotating clutch b element C12, C22, a C32 respectively.Three clutch a elements C11, C21, C31 can not connect each other in relative rotation, common composition outside friction disc support.When clutch C1, C2, C3 are handled, clutch a element C11, C21, C31 and second clutch b element C12, C22, C32 couple together, and two elements has equal angular velocity of rotation.
Three brake units B1, B2, B3 are configured to brake unit and only have break a element B11, B21, a B31 respectively.When break B1, B2, B3 are handled, break a element B11, B21, B31 are connected with case of transmission, and the angular velocity that break a element is rotated is zero.
Consult the multi-speed automatic transmission of the present invention shown in Fig. 1, comprise the input shaft 1 be arranged in a housing G, an output shaft 2, four planetary gear set Pl, P2, P3, P4 and comprise eight axles 1 that can rotate altogether, 2, 3, 4, 5, 6, 7, 8 and six gearshift switching member C1, C2, C3, B1, B2, B3, gearshift switching member comprises multiple break B1, B2, B3 and multiple clutch C1, C2, C3, gearshift switching member optionally engages and makes to obtain different velocity ratios between input shaft 1 and output shaft 2, thus nine forward gears can be realized and one reverse gear, wherein, input shaft 1 is releasably connected with the 5th axle 5 via first clutch C1, 5th axle 5 is connected with the first sun gear P11 and the second sun gear P21 and is connected on housing G via the first break B1, input shaft 1 to be releasably connected with the 4th axle 4 being connected to the first gear ring P13 via second clutch C2 and to be connected with the 3rd axle 3 via the 3rd clutch C3, and the 3rd axle 3 is connected with the third line carrier P32 and the 4th gear ring P43, 6th axle 6 is connected with the second planet carrier P22 and is connected on housing G via second brake B2, 7th axle 7 is connected with the 3rd sun gear P31 and the 4th sun gear P41 and is connected on housing G via the 3rd break B3, 8th axle 8 is connected with the first row carrier P12, the second gear ring P23 and the 3rd gear ring P33, output shaft 2 is connected with fourth line carrier P42.
As shown in Figure 1, 3rd axle 3 and the third line carrier P32, 4th gear ring P43, 3rd clutch b element C32 can not connect in relative rotation, 4th axle 4 and the first gear ring P13, second clutch b element C22 can not connect in relative rotation, 5th axle 5 and the first sun gear P11, second sun gear P21, first break a element B11, first clutch b element C12 can not connect in relative rotation, 6th axle 6 and the second planet carrier P22, second brake a element B21 can not connect in relative rotation, 7th axle 7 and the 3rd sun gear P31, 4th sun gear P41, 3rd break a element B31 can not connect in relative rotation, 8th axle 8 and the first row carrier P12, second gear ring P23, 3rd gear ring P33 can not connect in relative rotation.
Exemplary gearshift logic, each gear velocity ratio and the ratio step of the multi-speed automatic transmission according to Fig. 1 are shown in Table 1.Closed three gearshift switching members are only needed for each gear.The respective velocity ratio that exemplarily can draw each gear from this gearshift schematic diagram and the gearshift of a higher downwards gear that can determine thus are jumped ratio step (the velocity ratio ratio between gear) in other words, and its numerical value is total up to the ratio coverage that 9.79 are speed changer.
Table 1
In table 1, "×" represents that clutch, break are handled, and " (×) " represents that clutch can be handled, and also can not be handled, does not all affect the velocity ratio of speed changer at this gear.
From table 1, when order gearshift mode, two adjacent gears only must be connected a gearshift switching member respectively and disconnect a switching member, and it is constant that two other gearshift switching member connects situation, share two gearshift switching members when namely changing to adjacent gear.In addition visible, less gearshift can be realized during gearshift and jump and larger gear range.
By closed second and the 3rd break B2, B3 and second clutch C2 obtains the first forward gear, by closed first and the 3rd break B1, B3 and second clutch C2 obtains the second forward gear, by closed 3rd break B3 and first and second clutch C1, C2 obtains the 3rd forward gear, by closed 3rd break B3 and first and the 3rd clutch C1, C3 obtains the 4th forward gear, or by closed 3rd break B3 and second and the 3rd clutch C2, C3 obtains the 4th forward gear, by closed first, second and the 3rd clutch C1, C2, C3 obtains the 5th forward gear, by closed first break B1 and second and the 3rd clutch C2, C3 obtains the 6th forward gear, by closed second brake B2 and second and the 3rd clutch C2, C3 obtains the 7th forward gear, by closed first and second break B1, B2 and the 3rd clutch C3 obtains the 8th forward gear, by closed second brake B2 and first and the 3rd clutch C1, C3 obtains the 9th forward gear, and by closed second and the 3rd break B2, B3 and first clutch C1 is reversed gear.
According to the present invention, even if also different ratio step can be obtained depending on the difference of logic of shifting gears in identical speed changer schematic diagram, thus can realize being applied to the specific or specific flexible program of vehicle.
In addition, specify alternatively according to the present invention, each suitable position of multi-speed automatic transmission arranges additional overrunning clutch, such as, in order to connect between axle and housing at one or connect two axles alternatively.
In input shaft side or output shaft side, axle differential and/or distributor differential mechanism can be set.
In the scope of a kind of favourable improvement project of the present invention, input shaft 1 can separate with drive motor as desired by a clutching member, can use fluid torque converter, hydraulic clutch, dry launch clutch, wet starting clutch, magnetic powder clutch or centrifugal clutch as clutching member.Also can be arranged on below speed changer along direction of power flows by this initiating element, input shaft 1 is fixedly connected with the bent axle of drive motor in this case.
In addition, allow torsion vibration absorber to be arranged between drive motor and speed changer according to multi-speed automatic transmission of the present invention.
In the scope of the unshowned mode of execution of another kind of the present invention, can on each axle, preferably arrange on input shaft 1 or output shaft 2 without the break worn and torn, such as hydraulic type or electrodynamic retarder or analog, this is particularly significant for being used in commercial car.In addition, in order to drive additional unit at each axle, preferably can arrange auxiliary drive on input shaft 1 or output shaft 2.
The friction type gearshift switching member used can be constructed to be permeable to clutch or the break of powershift.Particularly can use clutch or break, such as lamella clutch, band brake and/or the cone clutch of force closure.
Another advantage of multi-speed automatic transmission advised here is, can install on each axle as generator and/or the motor as additional drive system.
Claims (6)
1. a multispeed manual transmission for planetary gear construction mode, is characterized in that: comprise four planetary gear set be arranged in housing (G), eight axles that can rotate and six gearshift switching members;
Described four planetary gear set are respectively first planet wheels (P1), the second planetary gear set (P2), third planet wheels (P3), fourth planet wheels (P4);
Described first planet wheels (P1) are arranged on input side, and described first planet wheels (P1) comprise the first sun gear (P11), first planet wheel carrier (P12) and the first gear ring (P13); Planetary wheel carrier (P12) guides planet wheel (P14) on circular orbit, and planet wheel (P14) can at the upper circular-rotation of planetary wheel carrier (P12); Planet wheel (P14) is with sun gear (P11) and be meshed with gear ring (P13);
Described second planetary gear set (P2), third planet wheels (P3) are successively set on centre; Described second planetary gear set (P2) comprises the second sun gear (P21), the second planetary wheel carrier (P22) and the second gear ring (P23); Planetary wheel carrier (P22) guides planet wheel (P24) on circular orbit, and planet wheel (P24) can at the upper circular-rotation of planetary wheel carrier (P22); Planet wheel (P24) is with sun gear (P21) and be meshed with gear ring (P23);
Described third planet wheels (P3) comprise the 3rd sun gear (P31), third planet wheel carrier (P32) and the 3rd gear ring (P33); Planetary wheel carrier (P32) guides planet wheel (P34) on circular orbit, and planet wheel (P34) can at the upper circular-rotation of planetary wheel carrier (P32); Planet wheel (P34) is with sun gear (P31) and be meshed with gear ring (P33);
Described fourth planet wheel speed (P4) is arranged on outlet side, and described fourth planet wheels (P4) comprise the 4th sun gear (P41), fourth planet wheel carrier (P42) and the 4th gear ring (P43); Planetary wheel carrier (P42) guides planet wheel (P44) on circular orbit, and planet wheel (P44) can at the upper circular-rotation of planetary wheel carrier (P42); Planet wheel (P44) is with sun gear (P41) and be meshed with gear ring (P43);
Described eight axles that can rotate are respectively input shaft (1), output shaft (2), the 3rd axle (3), the 4th axle (4), the 5th axle (5), the 6th axle (6), the 7th axle (7) and the 8th axle (8);
Described 3rd axle (3) can not be connected in relative rotation with the third line carrier (P32), the 4th gear ring (P43),
Described 4th axle (4) can not be connected in relative rotation with the first gear ring (P13),
Described 5th axle (5) can not be connected in relative rotation with the first sun gear (P11), the second sun gear (P21),
Described 6th axle (6) can not be connected in relative rotation with the second planet carrier (P22),
Described 7th axle (7) can not be connected in relative rotation with the 3rd sun gear (P31), the 4th sun gear (P41),
Described 8th axle (8) can not be connected in relative rotation with the first row carrier (P12), the second gear ring (P23), the 3rd gear ring (P33)
Described output shaft (2) can not be connected in relative rotation with fourth line carrier (P42).
Described six gearshift switching members are made up of three breaks and three clutches, described three breaks are respectively the first break (B1), second brake (B2), the 3rd break (B3), and described three clutches are respectively first clutch (C1), second clutch (C2), the 3rd clutch (C3);
Described six gearshift switching members optionally engage and make to obtain different velocity ratios between input shaft (1) and output shaft (2), thus nine forward gears can be realized and one reverse gear;
First clutch (C1) is that steerable turning round refuses transfer unit, described input shaft (1) and the 5th axle (5) to be coupled together selectively;
Second clutch (C2) is that steerable turning round refuses transfer unit, described input shaft (1) and the 4th axle (4) to be coupled together selectively;
3rd clutch (C3) is that steerable turning round refuses transfer unit, described input shaft (1) and the 3rd axle (3) to be coupled together selectively;
First break (B1) is that steerable turning round refuses transfer unit, described 5th axle (5) and housing (G) to be coupled together selectively;
Second brake (B2) is that steerable turning round refuses transfer unit, described 6th axle (6) and housing (G) to be coupled together selectively;
3rd break (B3) is that steerable turning round refuses transfer unit, described 7th axle (7) and housing (G) to be coupled together selectively.
2. the multispeed manual transmission of a kind of planetary gear construction mode according to claim 1, is characterized in that:
Described first clutch (C1) comprises first clutch a element (C11) and first clutch b element (C12), second clutch (C2) comprises second clutch a element (C21) and second clutch b element (C22), and the 3rd clutch (C3) comprises the 3rd clutch a element (C31) and the 3rd clutch b element (C32);
Described first break (B1) comprises the first break a element (B11), second brake (B2) comprises second brake a element (B21), and described 3rd break (B3) comprises the 3rd break a element (B31).
When being provided with described first clutch (C1) by manipulation, making the described first clutch a element (C11) that can not be connected in relative rotation with described input shaft (1) and couple together with the described first clutch b element (C12) that described 5th axle (5) can not be connected in relative rotation; When being provided with described second clutch (C2) by manipulation, making the described second clutch a element (C21) that can not be connected in relative rotation with described input shaft (1) and couple together with the described second clutch b element (C22) that described 4th axle (4) can not be connected in relative rotation; When being provided with described 3rd clutch (C3) by manipulation, making the described 3rd clutch a element (C31) that can not be connected in relative rotation with described input shaft (1) and couple together with the described 3rd clutch b element (C32) that described 3rd axle (3) can not be connected in relative rotation.
When being provided with described first break (B1) by manipulation, the described first break a element (B11) that can not be connected in relative rotation with described 5th axle (5) and housing (G) are coupled together; When being provided with described second brake (B2) by manipulation, the described second brake a element (B21) that can not be connected in relative rotation with described 6th axle (6) and housing (G) are coupled together, when being provided with described 3rd break (B3) by manipulation, the described 3rd break a element (B31) that can not be connected in relative rotation with described 7th axle (7) and housing (G) are coupled together.
3. the multispeed manual transmission of a kind of planetary gear construction mode according to claim 1, is characterized in that: described input shaft (1) can not be connected in relative rotation with first clutch a element (C11), second clutch a element (C21), the 3rd clutch a element (C31).
4. the multispeed manual transmission of a kind of planetary gear construction mode according to claim 1 and 2, is characterized in that:
By closed second and the 3rd break (B2, B3) and second clutch (C2) obtain the first forward gear, by closed first and the 3rd break (B1, B3) and second clutch (C2) obtain the second forward gear, by closed 3rd break (B3) and first and second clutch (C1, C2) the 3rd forward gear is obtained, by closed 3rd break (B3) and first and the 3rd clutch (C1, C3) the 4th forward gear is obtained, or by closed 3rd break (B3) and second and the 3rd clutch (C2, C3) the 4th forward gear is obtained, by closed first, second and the 3rd clutch (C1, C2, C3) the 5th forward gear is obtained, by closed first break (B1) and second and the 3rd clutch (C2, C3) the 6th forward gear is obtained, by closed second brake (B2) and second and the 3rd clutch (C2, C3) the 7th forward gear is obtained, by closed first and second break (B1, B2) and the 3rd clutch (C3) obtain the 8th forward gear, by closed second brake (B2) and first and the 3rd clutch (C1, C3) the 9th forward gear is obtained, and by closed second and the 3rd break (B2, B3) and first clutch (C1) reversed gear.
5. the multispeed manual transmission of a kind of planetary gear construction mode according to claim 1, is characterized in that:
Described first, second, third and fourth planetary gear set (P1, P2, P3, P4) is configured to negative ratio epicyclic gear group;
Described planetary gear set is observed vertically and is arranged by the order of first planet gear train (P1), the second planetary gear set (P2), third planet gear train (P3), fourth planet gear train (P4).
6. the multispeed manual transmission of a kind of planetary gear construction mode according to claim 1, is characterized in that:
Described first, second, and third clutch (C1, C2, C3) is observed vertically and is arranged side by side and has a common outside friction disc support as chip gearshift switching member;
Each gearshift switching member (C1, C2, C3, B1, B2, B3) of described speed changer is constructed to be permeable to the gearshift switching member switched as required, especially the gearshift switching member of electromechanics and/or electric liquid.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510519073.6A CN105114562A (en) | 2015-08-20 | 2015-08-20 | Multi-gear transmission with planet gear structure mode |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201510519073.6A CN105114562A (en) | 2015-08-20 | 2015-08-20 | Multi-gear transmission with planet gear structure mode |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN105114562A true CN105114562A (en) | 2015-12-02 |
Family
ID=54662618
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201510519073.6A Pending CN105114562A (en) | 2015-08-20 | 2015-08-20 | Multi-gear transmission with planet gear structure mode |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN105114562A (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106917849A (en) * | 2017-04-27 | 2017-07-04 | 广州汽车集团股份有限公司 | Eight speed automatic transmissions |
| CN111998044A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
| CN111998043A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
| CN112013088A (en) * | 2020-09-16 | 2020-12-01 | 山东科技大学 | Novel 10-speed automatic transmission device |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN114001132A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| CN103912641A (en) * | 2013-01-03 | 2014-07-09 | 福特全球技术公司 | Multi-speed transmission |
| CN104204612A (en) * | 2012-04-27 | 2014-12-10 | Zf腓德烈斯哈芬股份公司 | Multi-speed gearbox |
| CN104254710A (en) * | 2012-04-25 | 2014-12-31 | Zf腓德烈斯哈芬股份公司 | Multi-speed gearbox |
| CN205064720U (en) * | 2015-08-20 | 2016-03-02 | 肇庆学院 | Multi -step automatic gearbox |
-
2015
- 2015-08-20 CN CN201510519073.6A patent/CN105114562A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102009020442A1 (en) * | 2009-05-08 | 2010-11-11 | Iav Gmbh Ingenieurgesellschaft Auto Und Verkehr | Transmission for internal combustion engine, has four planetary gears sets with sun wheels, planet wheel carriers, hollow wheels and six switching elements, where hollow wheel of third set is constantly connected to carrier of fourth set |
| CN104254710A (en) * | 2012-04-25 | 2014-12-31 | Zf腓德烈斯哈芬股份公司 | Multi-speed gearbox |
| CN104204612A (en) * | 2012-04-27 | 2014-12-10 | Zf腓德烈斯哈芬股份公司 | Multi-speed gearbox |
| CN103912641A (en) * | 2013-01-03 | 2014-07-09 | 福特全球技术公司 | Multi-speed transmission |
| CN205064720U (en) * | 2015-08-20 | 2016-03-02 | 肇庆学院 | Multi -step automatic gearbox |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106917849A (en) * | 2017-04-27 | 2017-07-04 | 广州汽车集团股份有限公司 | Eight speed automatic transmissions |
| CN112013088A (en) * | 2020-09-16 | 2020-12-01 | 山东科技大学 | Novel 10-speed automatic transmission device |
| CN112013088B (en) * | 2020-09-16 | 2023-06-09 | 山东科技大学 | Novel 10-speed automatic transmission device |
| CN111998044A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
| CN111998043A (en) * | 2020-09-30 | 2020-11-27 | 宝能(西安)汽车研究院有限公司 | Multi-gear automatic transmission and vehicle with same |
| CN112324877A (en) * | 2020-11-19 | 2021-02-05 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN112324877B (en) * | 2020-11-19 | 2023-04-18 | 中国地质大学（武汉） | Nine-gear automatic transmission |
| CN114001132A (en) * | 2021-10-26 | 2022-02-01 | 中国地质大学（武汉） | Nine-gear automatic transmission with small step ratio |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN105114562A (en) | Multi-gear transmission with planet gear structure mode | |
| CN105114561A (en) | Automatic nine-gear transmission | |
| CN105114558A (en) | Multi-gear automatic transmission | |
| CN105114560A (en) | Multi-gear transmission achieved in mode of planetary gear structure | |
| CN101550993B (en) | Gear train of automatic transmission for vehicle | |
| CN102844587B (en) | Double clutch group transmission and the method for operating dual clutch device group transmission | |
| US9458910B2 (en) | Multi-ratio transmission | |
| CN104246298B (en) | Multiple-speed gear-box | |
| CN102466003B (en) | For the train of gearings of the automatic transmission of vehicle | |
| CN104728368B (en) | One kind six keeps off planetary automatic transmission | |
| CN205064722U (en) | Nine grades of automatic gearbox | |
| CN102913597A (en) | Seven-level planet automatic speed changer | |
| CN106195156B (en) | Multistage automatic transmission for vehicle | |
| CN103527732A (en) | Seven-gear planet automatic gearbox | |
| CN105114559A (en) | Automatic nine-speed transmission | |
| CN204985566U (en) | Planetary gear configuration mode's many grades of derailleurs | |
| CN107199875B (en) | Hybrid vehicle transmission system | |
| CN205064721U (en) | Planetary gear configuration mode keeps off derailleur more | |
| CN205064720U (en) | Multi -step automatic gearbox | |
| CN204878554U (en) | Nine fast automatic gearbox | |
| CN106838152A (en) | A kind of multi-shifting speed variator of planetary gear construction mode | |
| CN109340327B (en) | Automatic transmission of a planetary gear design for a motor vehicle | |
| CN111033086A (en) | Group transmission device | |
| US10995826B2 (en) | Transmission for a motor vehicle | |
| CN106907468A (en) | Gearbox and automobile |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| WD01 | Invention patent application deemed withdrawn after publication | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20151202 |