CN205064720U - Multi -step automatic gearbox - Google Patents
Multi -step automatic gearbox Download PDFInfo
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- CN205064720U CN205064720U CN201520636709.0U CN201520636709U CN205064720U CN 205064720 U CN205064720 U CN 205064720U CN 201520636709 U CN201520636709 U CN 201520636709U CN 205064720 U CN205064720 U CN 205064720U
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Abstract
The utility model discloses a multi -step automatic gearbox belongs to automatic gearbox technical field, overcome and had more component quantity, complicated structure in the current automatic gearbox technique, especially be difficult to to provide progressive slightly, hierarchical good drive ratio series and good engagement efficiency's problem, include four planet wheelsets setting up in succession along the main rotation axis around first, second, third and fourth planet wheelset promptly, six gear shift switching device, gear shift switching device permission optionally are handled to make forms nine advance gear and speeds in reverse between transmission input shaft and output shaft, the input shaft can loosen with the fourth axle via first clutch and be connected with taking off, and the fourth axle is connected with first sun gear and second sun gear and can loosen with the third axle via the second clutch and be connected with taking off, and the third axle is connected with first planet carrier and connect on the casing via first stopper, the input shaft can loosen and is connected with taking off with the 5th via the third clutch.
Description
Technical field
The utility model belongs to automatic transmission technical field, relates to a kind of automatic transmission unit, especially for the Power Train of Motor Vehicle, is specifically related to multidrive.
Background technique
The dynamical system of Motor Vehicle comprises motor, multi-speed transmission and differential or main reducing gear composition.Multi-speed 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 gears) determines the number of times that engine torque bands repeats.The negligible amounts of forward gears 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 fourth gear automatic transmission 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 grades, seven grades, eight grades, nine gear automatic speed variators have obvious advantage than fourth gear and five gear automatic speed variators 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 elements.
Summary of the invention
Technical problem to be solved in the utility model 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 multidrive.
For solving the problems of the technologies described above, the utility model adopts following technological scheme to realize, and accompanying drawings is as follows:
The purpose of this utility model is especially, provides a kind of compact automatic transmission unit with a large amount of advance gear.
According to the utility model, 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 gear shift switching members, described gear shift switching member allows optionally to engage nine advance Transmission gear; 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, the first row carrier, 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 numbers of gear steps 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.
Multidrive, comprises four planetary gear set be arranged in housing G, eight axles that can rotate and six gear shift 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 first row carrier P12;
Described 4th axle 4 can not be connected in relative rotation with the first sun gear P11, the second sun gear P21;
Described 5th axle 5 can not be connected in relative rotation with the third line carrier P32, the 4th gear ring P43;
Described 6th axle 6 can not be connected in relative rotation with the 3rd sun gear P31, the 4th sun gear P41;
Described 7th axle 7 can not be connected in relative rotation with the first gear ring P13, the second planet carrier P22, the 3rd gear ring P33;
Described 8th axle 8 can not be connected in relative rotation with the second gear ring P23;
Described output shaft 2 can not be connected in relative rotation with fourth line carrier P42.
Described six gear shift 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 gear shift 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 4th axle 4 to be coupled together selectively;
Second clutch C2 is that steerable turning round refuses transfer unit, described input shaft 1 and the 3rd axle 3 to be coupled together selectively;
3rd clutch C3 is that steerable turning round refuses transfer unit, described input shaft 1 and the 5th axle 5 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 3rd axle 3 selectively;
Second brake B2 is that steerable turning round refuses transfer unit, to be coupled together with housing G by described 8th axle 8 selectively;
3rd break B3 is that steerable turning round refuses transfer unit, to be coupled together with housing G by described 6th axle 6 selectively;
The C1 of first clutch described in technological scheme 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 4th axle 4 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 3rd axle 3 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 5th axle 5 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 3rd axle 3 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 8th axle 8 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 6th axle 6 is coupled together.
Input shaft 1 described in technological scheme 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 first clutch C1 obtains the first forward gear, by closed second and the 3rd break B2, 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 second brake B2 and second and the 3rd clutch C2, C3 obtains the 6th forward gear, by closed second brake B2 and first and the 3rd clutch C1, 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 first break B1 and first and the 3rd clutch C1, C3 obtains the 9th forward gear, and by closed first and the 3rd break B1, B3 and first clutch C1 is reversed gear.
The planetary gear set Pl of first, second, third and fourth described in technological scheme, 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.
First, second, and third clutch C1 described in technological scheme, C2, C3 observe vertically and are arranged side by side and have a common outside friction disc support as chip gear shift switching member;
Each gear shift switching member C1 of described speed changer, C2, C3, B1, B2, B3 are constructed to be permeable to the gear shift switching member switched as required, are gear shift switching members that is dynamo-electric and/or electric liquid.
Compared with prior art the beneficial effects of the utility model are:
The utility model can provide nine forward gearss and a reverse gear, have that numbers of gear steps 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 utility model is further described:
Fig. 1 is the explanatory view according to first embodiment's automatic transmission unit of the present utility model;
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 utility model 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 gear shift switching members C1, C2, C3, B1, B2, B3.These gear shift switching members are arranged for conversion just in time nine advance A/T gear position Vl, V2, V3, V4, V5, V6, V7, V8, V9 and reverse gear VR.But automatic transmission unit also can carry out work by only eight advance Transmission gear, 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=-1.979 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=-1.474 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.
The utility model multidrive as shown in Figure 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 gear shift switching member C1, C2, C3, B1, B2, B3, gear shift switching member comprises multiple break B1, B2, B3 and multiple clutch C1, C2, C3, gear shift 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 4th axle 4 via first clutch C1, 4th axle is connected with the first sun gear P11 and the second sun gear P21 and is releasably connected with the 3rd axle 3 via second clutch C2, 3rd axle is connected with the first row carrier P12 and is coupled on housing G via the first break B1, input shaft 1 is releasably connected with the 5th axle 5 via the 3rd clutch C3, and the 5th axle is connected with the third line carrier P32 and the 4th gear ring P43, 6th axle 6 is connected with the 3rd sun gear P31 and the 4th sun gear P41 and is coupled on housing G via the 3rd break B3, 7th axle 7 is connected with the first gear ring P13, the second planet carrier P22 the 3rd gear ring P33, 8th axle 8 and the second gear ring P23 and be coupled on housing G via second brake B2, output shaft 2 is connected with fourth line carrier P42.
As shown in Figure 1, 3rd axle 3 and the first row carrier P12, second clutch element C22, first break a element B11 can not connect in relative rotation, 4th axle 4 and the first sun gear P11, second sun gear P21, first clutch b element C12 can not connect in relative rotation, 5th axle 5 and the third line carrier P32, 4th gear ring P43, 3rd clutch b element C32 can not connect in relative rotation, 6th axle 6 and the 3rd sun gear P31, 4th sun gear P41, 3rd break a element B31 can not connect in relative rotation, 7th axle 7 and the first gear ring P13, second planet carrier P22, 3rd gear ring P33 can not connect in relative rotation, 8th axle 8 and the second gear ring P23, second brake a element B21 can not connect in relative rotation.
Exemplary shift logic, each shelves velocity ratio and the ratio step of the multidrive according to Fig. 1 are shown in Table 1.Closed three gear shift 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 gear shift switching member respectively and disconnect a switching member, and it is constant that two other gear shift switching member connects situation, share two gear shift switching members when namely changing to adjacent gear.In addition visible, less gearshift can be realized during gear shift and jump and larger gear range.
By closed second and the 3rd break B2, B3 and first clutch C1 obtains the first forward gear, by closed second and the 3rd break B2, 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 second brake B2 and second and the 3rd clutch C2, C3 obtains the 6th forward gear, by closed second brake B2 and first and the 3rd clutch C1, 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 first break B1 and first and the 3rd clutch C1, C3 obtains the 9th forward gear, and by closed first and the 3rd break B1, B3 and first clutch C1 is reversed gear.
According to the utility model, 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 this embodiment, shift logic, each shelves velocity ratio and ratio step are as shown in table 1.
In this implements, especially the 3rd break B3 is applicable to being configured to castellated gear shift switching member, thus significantly can improve energy loss.
In addition, specify alternatively according to the utility model, each suitable position of multidrive 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 utility model, 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 multidrive of the present utility model.
In the scope of the unshowned mode of execution of another kind of the present utility model, 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 shifting 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 multidrive advised here is, can install on each axle as generator and/or the motor as additional drive system.
Claims (6)
1. a multidrive, is characterized in that: comprise four planetary gear set be arranged in housing (G), eight axles that can rotate and six gear shift 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 (Pl) 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 first row carrier (P12);
Described 4th axle (4) can not be connected in relative rotation with the first sun gear (P11), the second sun gear (P21);
Described 5th axle (5) can not be connected in relative rotation with the third line carrier (P32), the 4th gear ring (P43);
Described 6th axle (6) can not be connected in relative rotation with the 3rd sun gear (P31), the 4th sun gear (P41);
Described 7th axle (7) can not be connected in relative rotation with the first gear ring (P13), the second planet carrier (P22), the 3rd gear ring (P33);
Described 8th axle (8) can not be connected in relative rotation with the second gear ring (P23);
Described output shaft (2) can not be connected in relative rotation with fourth line carrier (P42);
Described six gear shift 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 gear shift 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 4th axle (4) to be coupled together selectively;
Second clutch (C2) is that steerable turning round refuses transfer unit, described input shaft (1) and the 3rd axle (3) to be coupled together selectively;
3rd clutch (C3) is that steerable turning round refuses transfer unit, described input shaft (1) and the 5th axle (5) to be coupled together selectively;
First break (B1) is that steerable turning round refuses transfer unit, described 3rd axle (3) and housing (G) to be coupled together selectively;
Second brake (B2) is that steerable turning round refuses transfer unit, described 8th axle (8) and housing (G) to be coupled together selectively;
3rd break (B3) is that steerable turning round refuses transfer unit, described 6th axle (6) and housing (G) to be coupled together selectively.
2. a kind of multidrive 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 4th axle (4) 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 3rd axle (3) 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 5th axle (5) 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 3rd axle (3) 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 8th axle (8) 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 6th axle (6) and housing (G) are coupled together.
3. a kind of multidrive 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. a kind of multidrive according to claim 1 and 2, is characterized in that:
By closed second and the 3rd break (B2, B3) and first clutch (C1) obtain the first forward gear, by closed second and the 3rd break (B2, 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 second brake (B2) and second and the 3rd clutch (C2, C3) the 6th forward gear is obtained, by closed second brake (B2) and first and the 3rd clutch (C1, 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 first break (B1) and first and the 3rd clutch (C1, C3) the 9th forward gear is obtained, and by closed first and the 3rd break (B1, B3) and first clutch (C1) reversed gear.
5. a kind of multidrive according to claim 1, is characterized in that:
Described first, second, third and fourth planetary gear set (Pl, 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 (Pl), the second planetary gear set (P2), third planet gear train (P3), fourth planet gear train (P4).
6. a kind of multidrive 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 gear shift switching member;
Each gear shift switching member (C1, C2, C3, B1, B2, B3) of described speed changer is constructed to be permeable to the gear shift switching member switched as required, is gear shift switching member that is dynamo-electric and/or electric liquid.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201520636709.0U CN205064720U (en) | 2015-08-20 | 2015-08-20 | Multi -step automatic gearbox |
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| CN201520636709.0U CN205064720U (en) | 2015-08-20 | 2015-08-20 | Multi -step automatic gearbox |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114562A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission with planet gear structure mode |
| CN105114558A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear automatic transmission |
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2015
- 2015-08-20 CN CN201520636709.0U patent/CN205064720U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105114562A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear transmission with planet gear structure mode |
| CN105114558A (en) * | 2015-08-20 | 2015-12-02 | 肇庆学院 | Multi-gear automatic transmission |
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