CN202186277U - Hybrid drive system and vehicle comprising same - Google Patents
Hybrid drive system and vehicle comprising same Download PDFInfo
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- CN202186277U CN202186277U CN2010201225175U CN201020122517U CN202186277U CN 202186277 U CN202186277 U CN 202186277U CN 2010201225175 U CN2010201225175 U CN 2010201225175U CN 201020122517 U CN201020122517 U CN 201020122517U CN 202186277 U CN202186277 U CN 202186277U
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Abstract
A hybrid drive system comprises an internal combustion engine, a first motor, a first planet coupling mechanism and a first retarding mechanism, wherein the internal combustion engine is connected with the first motor through a first clutch. An output shaft of the first motor is connected with one of a sun wheel and a gear ring of the first planet coupling mechanism at a position in the axial direction of the output shaft; the output shaft of the first motor is connected with the other of the sun wheel and the gear ring through a second clutch at another position in the axial direction of the output shaft; and a first brake is arranged on the other of the sun wheel and the gear ring. A planet carrier of the first planet coupling mechanism is connected with an input gear of the first retarding mechanism. The utility model further provides a vehicle. The hybrid drive system can form two gear grades of a vehicle forward gear by adjusting the first planet coupling mechanism, thereby flexibly choosing an operation mode and a corresponding gear according to different running conditions of the vehicle.
Description
Technical field
The utility model relates to a kind of hybrid electric drive system and comprises the vehicle of this drive system.
Background technology
At present, the requirement of automobile aspect environmental protection is strict day by day.Pure electric automobile (EV) can't satisfy under the different operating modes demand to vehicle dynamic quality technically, and hybrid vehicle (HEV) has then obtained development faster with the advantage of its dynamic property and the feature of environmental protection two aspects.
Prior art discloses a kind of automobile hybrid power drive system; As shown in Figure 4; This drive system comprises combustion engine 100, electrical motor 200 and as the sun and planet gear of power coupling mechanism; This sun and planet gear comprises gear ring 400, planetary pinion carrier 500 and sun wheel 600 is installed, and wherein, electrical motor 200 is given gear ring 400 through gear 300 with transmission of power; Combustion engine 100 is given sun wheel 600 with transmission of power, then the two power is coupled through pinion carrier and is transferred to the running device of automobile.
Known ground, the combustion engine of automobile or the rotating speed of electrical motor are higher, are delivered to before the drive wheel of automobile by the rotation of combustion engine or electrical motor output, must slow down increase through speed reduction gearing and turn round to drive automobile, and this is same like this on hybrid vehicle.Speed reduction gearing mainly is made up of reduction gear train, and its reduction ratio is changeless after the reducing gearbox manufacturing is accomplished.Car deceleration increases the needs of turning round under the different operating modes in order to adapt to; Orthodox car drive system (promptly only by internal combustion engine drive) is equipped with change speed gear box to carry out the gear position operation of automobile; But, for hybrid vehicle, because the arrangement form of its actuating unit (being combustion engine and motor) and the restriction of power coupling mechanism; Change speed gear box is installed is not only made driving system structure too complicated, and on mounting structure, also be difficult to realize.Therefore; The main rotating through the control motor of reversing gear of hybrid vehicle realizes; Speed change then mainly realizes through the rotating speed of adjustment electrical motor; This is equivalent to a kind of stepless change, and this gear shift mode is actual to be the output speed that changes electrical motor through the horsepower output that changes electrical motor.
But; This gear shift mode of hybrid vehicle can not adapt to the needs under the different operating modes of automobile; For example, for above-mentioned hybrid electric drive system, when automobile is in climbing (supposing that the gradient is fully loaded following the possible slope that can go of this automobile) situation following time; Horsepower output after need making combustion engine 100 and electrical motor 200 be coupled reaches maximum; This moment, the output speed of electrical motor 200 should reach maximum in this case, but this output speed must pass through speed reduction gearing slow down could the driving automobile climbing to increase moment of torsion (when especially fully loaded the and quality of automobile is big), for the reduction ratio that adapts to this kind operating mode speed reduction gearing must design greatlyyer.But; If the reduction ratio that is used as this hybrid electric drive system speed reduction gearing with this bigger reduction ratio but can not adapt to the needs of this other operating mode of automobile; For example, unloaded and when going on flat road surface when this automobile, require this moment the automobile can be to exercise than higher speed; Yet because the reduction ratio of speed reduction gearing has designed greatlyyer; Even this moment electrical motor 200 with combustion engine 100 couplings after rotating speed reach maximum, but through the deceleration of the bigger reduction ratio of speed reduction gearing, the moving velocity of automobile is still not ideal enough.
Can be known that by last analysis the gear shift mode of traditional automobile hybrid power drive system can not satisfy the needs that go under the different operating modes of automobile, this is a more insoluble problem on the automobile hybrid power Design of Driving System always.
The utility model content
The utility model provides a kind of vehicle that can satisfy the hybrid electric drive system of the needs that go under the different operating modes of automobile and comprise this drive system for solving the technical matters that the gear shift mode that has hybrid electric drive system now can not satisfy the needs that go under the different operating modes of automobile.
The utility model provides a kind of hybrid electric drive system on the one hand; Comprise combustion engine, first motor, the first planet coupling mechanism and first speed reduction gearing; It is characterized in that; The output shaft of said combustion engine is connected with the output shaft of said first motor through first clutch; The output shaft of said first motor on a position of its axial direction with the sun wheel of the said first planet coupling mechanism and gear ring in one be connected; And the output shaft of said first motor also is connected with another person in the gear ring through second clutch and said sun wheel on another position of its axial direction, and another person in this sun wheel and the gear ring is provided with first drg, and the pinion carrier of the said first planet coupling mechanism is connected with the input gear of said first speed reduction gearing.
Further, said first clutch, second clutch and first drg power-transfer clutch and the drg that separately hydraulic control mechanism is handled of serving as reasons.
The output shaft of the line of centers of the output shaft of said combustion engine, the said first planet coupling mechanism and said first motor is on the same axis.
Said combustion engine is positioned at a side of the said first planet coupling mechanism, and said first motor is positioned at the opposite side of the said first planet coupling mechanism.
Said pinion carrier is connected on the input gear of said first speed reduction gearing through the adapter shaft of hollow, and the output shaft of said first motor passes in the adapter shaft of this hollow.
Said first planet coupling mechanism and said first speed reduction gearing are encapsulated in the housing.
The utility model also provides a kind of vehicle on the other hand, and wherein, one in the forerunner of said vehicle and the rear-guard is above-mentioned hybrid electric drive system.
Further; Another person in said forerunner and the rear-guard comprises: second motor, the second planet coupling mechanism and second speed reduction gearing; The output shaft of said second motor is connected with the sun wheel of the said second planet coupling mechanism; And the output shaft of said second motor also is connected with the gear ring of the said second planet coupling mechanism through three-clutch, and said gear ring is provided with second drg, and the pinion carrier of the said second planet coupling mechanism is connected with the input gear of said second speed reduction gearing.
The said three-clutch and second drg power-transfer clutch and the drg that separately hydraulic control mechanism is handled of serving as reasons.
Said second planet coupling mechanism and said second speed reduction gearing are encapsulated in the housing.
Above-mentioned hybrid electric drive system and the vehicle that comprises this hybrid electric drive system through the utility model; Owing to can make this first planet coupling mechanism participate in slowing down through adjusting the first planet coupling mechanism; And form two shelves levels of vehicle D Drive thus; Therefore can reduce the reduction ratio of first speed reduction gearing, to coordinate the needs that go under the different operating modes of vehicle.Simultaneously, owing to reduced the reduction ratio of first speed reduction gearing, therefore can reduce the gear quantity and the size of first speed reduction gearing, thereby reduce cost.Therefore, the hybrid electric drive system of the utility model can be selected various mode of operations and each respective notch flexibly according to the different driving cycles of vehicle.In addition; The hybrid electric drive system with adjustable two D Drive levels of the utility model can make that the car load low speed torque increases, starting is faster; And under at a high speed, can give play to the best efficiency point of first motor and combustion engine biglyyer; Improve energy conversion efficiency, reduced exhaust emissions and waste of power, finally reached effects such as the anti-emission carburetor of car load, low oil consumption and kinetic energy.
Description of drawings
Fig. 1 is the scheme drawing of a kind of embodiment of the hybrid electric drive system that provides of the utility model;
Fig. 2 is the scheme drawing of the another kind of embodiment of the hybrid electric drive system that provides of the utility model;
Fig. 3 is a kind of scheme drawing of embodiment of forerunner or the rear-guard of the vehicle that provides of the utility model;
Fig. 4 is the scheme drawing of the automobile hybrid power drive system that provides of prior art.
The specific embodiment
Clearer for technical matters, technical scheme and beneficial effect that the utility model is solved, below in conjunction with accompanying drawing and embodiment, the utility model is further elaborated.Should be appreciated that specific embodiment described herein only in order to explanation the utility model, and be not used in qualification the utility model.Need to prove; The major technique design of the utility model is to provide a kind of connection arrangement form of hybrid power system; And the concrete structure of associated components is known in automotive field, and those skilled in the art can select to realize through the parts of multiple concrete structure the connection arrangement form of the utility model hybrid power system.Therefore; The type of attachment of the utility model hybrid power system in following detailed description emphasis is described; Certainly for to make the technical scheme of the utility model be more readily understood; Typical structure that also can some parts of additional disclosure, but the explanation of this concrete structure should not thought the restriction to the utility model protection domain.
A kind of embodiment according to the utility model; A kind of hybrid electric drive system; Comprise combustion engine 1, first motor 2, the first planet coupling mechanism and first speed reduction gearing; Wherein, The output shaft of combustion engine 1 is connected with the output shaft of first motor 2 through first clutch 3, the output shaft of first motor 2 on a position of its axial direction with the sun wheel 8 of the first planet coupling mechanism and gear ring 6 in one be connected, and the output shaft of first motor 2 also passes through second clutch 4 and sun wheel 8 and is connected with another person in the gear ring 6 on another position of its axial direction; The pinion carrier 7 that another person in this sun wheel 8 and the gear ring 6 is provided with first drg, 5, the first planet coupling mechanisms is connected with the input gear 9 of first speed reduction gearing.
Further, above-mentioned hybrid electric drive system also comprises first diff 13, and the output gear 10 of this first speed reduction gearing is connected with the housing of first diff 13.
Known ground, the first planet coupling mechanism comprises gear ring 6, the pinion carrier 7 and the sun wheel 8 of a plurality of satellite gears is installed, and its matching relationship is known as satellite gear and is engaged between sun wheel 8 and the gear ring 6.
As shown in Figure 1; The output shaft of combustion engine 1 is connected on the output shaft of first motor 2 through first clutch 3; Wherein, first clutch 3 can adopt power-transfer clutch commonly used, for example friction-disc clutch; Its steering unit (not shown) can be hydraulic control mechanism, air operated control mechanism, mechanical control mechanism etc.; For example when first clutch 3 adopted diaphragm-spring clutch, its steering unit can adopt the mechanical control mechanism that comprises driving lever and release thrust bearing, and these concrete structures can be selected according to the car load type.
As shown in Figure 1; On the different axial locations of the output shaft of first motor 2; On the sun wheel 8 that the output shaft of this first motor 2 also is connected respectively to the first planet coupling mechanism and the gear ring 6, wherein, and can adopt being connected of sun wheel 8 such as the connection of key alligator groove, spline connection etc.; Connects indirectly with being connected through second clutch 4 of gear ring 6, thereby can pass through joint or the separation of second clutch 4 and optionally be connected or break off with gear ring 6.Second clutch 4 can adopt the power-transfer clutch of multiple concrete structure, and for example, second clutch 4 adopts friction-disc clutch; This friction-disc clutch comprises members such as clutch cover back plate, active friction disc and driven friction disk; Wherein, the output shaft of first motor 2 passes the clutch cover back plate of hollow and is fixedly attached to the end of this clutch cover back plate, and this active friction disc is arranged on the clutch cover back plate; Driven friction disk then relatively is arranged on the gear ring 6 with the active friction disc; Under the manipulation of clutch operating mechanism (not shown), initiatively friction disc can move axially in the clutch cover back plate upper edge, thereby optionally engages with driven friction disk or separate.Concrete structure those skilled in the art of this power-transfer clutch can expect multiple modification, but its principle that engages separation basically all is similar.
The first planet coupling mechanism is mainly used in the power of the coupling combustion engine 1 and first motor 2; But the first planet coupling mechanism of the utility model is relatively unique; It can also be used as adjusting the adjusting mechanism of vehicle D Drive reduction ratio through above-mentioned second clutch 4 and the first following drg 5 not only as power coupling mechanism.As shown in Figure 1; Gear ring 6 is provided with first drg 5; This first drg 5 is similar with the structure of commonly used car brake with principle, can be on the partial-length of the outer peripheral face of gear ring 6, brake shoe brake cheek or slipper to be set, and handle this brake shoe brake cheek or slipper through fluid pressure type brake operating mechanism (not shown); Selectively engaging or to separate, thereby make that gear ring 6 is fixing or can freely rotate with the outer peripheral face of gear ring 6.
It is how right that speed reducing gear pair in first speed reduction gearing can be installed as according to actual needs, and it mainly is that engagement through multistage big or small gear pair realizes slowing down.As shown in Figure 1, first speed reduction gearing comprises input gear 9 and output gear 10, can directly mesh between input gear 9 and the output gear 10, also can connect through the multiple sets of teeth wheel set, thereby realize slowing down.
As shown in Figure 1, pinion carrier 7 is connected with the input gear 9 of first speed reduction gearing as the output shaft of the first planet coupling mechanism.Pinion carrier 7 can form as one with input gear 9; Certainly in practical situation; On the pinion carrier 7 multi-link gear wheel shafts (being input shaft or the pinion carrier 7 of first speed reduction gearing and the adapter shaft of input gear 9), drive the first speed reduction gearing in-to-in gear pair through this gear wheel shaft and slow down to increase and turn round, in the structure shown in Fig. 1 to this input gear 9; Adapter shaft between pinion carrier 7 and the input gear 9 is a hollow; So that the output shaft of first motor 2 can therefrom pass, this is a kind of concrete structure certainly, in the technical conceive scope of the utility model, can have multiple other modified arrangement structure.
The output gear 10 of first speed reduction gearing is fixedly attached on the housing of first diff 13, this first diff 13 and then be connected on first drive wheels 12 through semiaxis.
The output shaft of the line of centers of the output shaft of combustion engine 1, the first planet coupling mechanism and first motor 2 is on the same axis.Can effectively practice thrift the radially installing space of drive system like this, the mounting structure of simplified system.
Usually; The planet coupling mechanism all is that the center of the parts in the planet coupling mechanism is connected with other parts when being connected use with other parts; For example the output shaft of first motor 2 is connected with gear ring 6 with the sun wheel 8 of the first planet coupling mechanism respectively, promptly refer to first motor 2 output shaft line of centers all with the line of centers of the sun wheel 8 of the first planet coupling mechanism and the centerline collineation of gear ring 6.
Combustion engine 1 is positioned at a side of the first planet coupling mechanism; First motor 2 is positioned at the opposite side of the first planet coupling mechanism; And pinion carrier 7 is connected on the input gear 9 of first speed reduction gearing through the adapter shaft of hollow, and the output shaft of first motor 2 passes in the adapter shaft of this hollow.Can effectively arrange drive system like this, avoid the weight of drive system too concentrated, thereby help the driving of vehicle.
The first planet coupling mechanism and first speed reduction gearing can for two independently mechanism install respectively; Also can be encapsulated in the housing, thereby can improve degree of integration, help reducing production costs.
Need to prove at this; Because Fig. 1 (and Fig. 2) only is a scheme drawing; For making the succinctly clear members such as backup bearing wherein that omitted of figure, but these all to be those skilled in the art can expect easily, in the actual installation process, can support as the case may be.
The principle that realizes two shelves levels of automobile D Drive through the arrangement structure among Fig. 1 below will be described.
Known ground, there is following equality (1) in the drive connection of the first planet coupling mechanism:
n1+n3·K1＝(1+K1)·n2
Wherein n1 is the rotating speed of sun wheel 8, and n2 is the rotating speed of pinion carrier 7, and n3 is the rotating speed of gear ring 6, and K1 is the gear ring number of teeth/sun wheel number of teeth.
In Fig. 1, when handling that first drg 5 engages so that gear ring 6 is fixing and when keeping second clutch 4 to be in released state, the rotation speed n 3 of gear ring 6 is zero in the above-mentioned equality (1), thereby has following equality (2):
n1＝(1+K1)·n2
Thereby, this moment the first planet coupling mechanism reduction ratio i
1=n1/n2=1+K1 is because the reduction ratio of first speed reduction gearing is definite value i
2(be two reduction gear among Fig. 1, this first speed reduction gearing can also be first class reducer structure or multi-stage speed-reducing mechanism certainly), therefore the reduction ratio of whole hybrid electric drive system is I=i under this serviceability
1I
2=(1+K1) i
2, this is the reduction ratio of first D Drive of hybrid electric drive system among Fig. 1, and this integral body reduction ratio is bigger, and this is specially adapted to low speed climbing etc. needs significantly rev down to increase the operating mode of moment of torsion.
In addition; In Fig. 1, when keeping first drg 5 to be in released state, because the output shaft and the sun wheel 8 of gear ring 6 through first motor 2 is connected to integral body when making second clutch 4 engage; So the n1=n3 in the above-mentioned equality (1), thereby there is following equality (3):
n1+n1·K1＝(1+K1)·n2
Promptly this moment n1=n2, that is to say that the first planet coupling mechanism is under this serviceability, the rotating speed of sun wheel 8, pinion carrier 7 and gear ring 6 all equates, realizes through-coupling, the reduction ratio i of the first planet coupling mechanism this moment
1=1, therefore the reduction ratio of whole hybrid electric drive system is I=i under this serviceability
1I
2=i
2, this is the reduction ratio of second D Drive of the utility model hybrid electric drive system among Fig. 1, less (the reduction ratio i that only depends on first speed reduction gearing of this reduction ratio
2), this operating mode such as be specially adapted to run at high speed.
Can know by last analysis; Above-mentioned hybrid electric drive system through the utility model preferred implementation; Owing to can make this first planet coupling mechanism participate in slowing down through adjusting the first planet coupling mechanism; And form two shelves levels of vehicle D Drive thus, therefore can reduce the reduction ratio of first speed reduction gearing, to coordinate the needs that go under the different operating modes of automobile.For example; When the fully loaded climbing of vehicle; Adopt the reduction ratio of first D Drive, thereby the output speed of the motor 2 of winning (or combustion engine 1 and first motor 2) is significantly reduced via the common deceleration of the first planet coupling mechanism and first speed reduction gearing, increase the purpose of turning round thereby reach to slow down; When vehicle when flat road surface is gone, can adopt the reduction ratio of second D Drive so that first motor 2 (or combustion engine 1 and first motor 2) rotating speed is only slowed down by first speed reduction gearing, thereby make that vehicle still can be with desirable speed after deceleration.Simultaneously,, therefore can reduce the gear quantity and the size of first speed reduction gearing, thereby practice thrift the required installing space of first speed reduction gearing, reduced cost owing to reduced the reduction ratio of first speed reduction gearing.
Shown in Figure 2 is a kind of variant of the utility model hybrid electric drive system; Its basic structure and embodiment shown in Figure 1 are similar; The output shaft of different is first motor 2 directly is fixed on the gear ring 6; The output shaft of this first motor 2 connects on the sun wheel 8 through second clutch 4 simultaneously; Be connected with sun wheel 8 with the operation through second clutch 4 or break off, the structure of the first clutch 3 among this second clutch 4 and Fig. 1 is similar basically, only is on the inner peripheral surface of the driven friction disk central through hole that is connected to sun wheel 8; Initiatively friction disc then is set directly on the output shaft of first motor 2, and this active friction disc can move to engage with driven friction disk or to separate through the operation of clutch operating mechanism (not shown).In addition; First drg 5 is arranged on the sun wheel 8; Sun wheel 8 is formed with the face of joint that engages with first drg 5 specially in Fig. 2, and the concrete structure of this sun wheel 8 also has multiple variations certainly, for example first drg 5 is set directly on the end face of sun wheel 8.
Arrangement structure among Fig. 2 can be realized two shelves levels of automobile D Drive equally, and is specific as follows:
Be in operating mode such as climbing when automobile and when needing to increase moment of torsion, the drg 5 of winning engaged so that sun wheel 8 is fixing, make second clutch 4 keep released states simultaneously.At this moment, the rotation speed n 1 of sun wheel is zero in the above-mentioned equality (1), and obtains following equality (4):
n3·K1＝(1+K1)·n2
This moment the first planet coupling mechanism reduction ratio i
1=n3/n2=(1+K1)/K1 is because the reduction ratio of first speed reduction gearing is definite value i
2(also be two reduction gear among Fig. 2, certain first this speed reduction gearing can also be first class reducer structure or multi-stage speed-reducing mechanism), therefore the reduction ratio of whole hybrid electric drive system is I=i under this serviceability
1I
2=(1+K1) i
2/ K1; This is the reduction ratio of first D Drive of the utility model hybrid electric drive system among Fig. 2; Though the reduction ratio of this first D Drive is less than the reduction ratio of first D Drive of embodiment shown in Fig. 1; But still the deceleration that can satisfy automobile increases and turns round needs, and the another kind of selection scheme in the utility model technical conceive scope is provided.
In addition; In Fig. 2, when keeping first drg 5 to be in released state, because the output shaft and the sun wheel 8 of gear ring 6 through first motor 2 is connected to integral body when making second clutch 4 engage; So the n1=n3 in the above-mentioned equality (1), thereby there is following equality (5):
n3+n3·K1＝(1+K1)·n2
Promptly this moment n3=n2, that is to say that the first planet coupling mechanism is under this serviceability, the rotating speed of sun wheel 8, pinion carrier 7 and gear ring 6 all equates, realizes through-coupling, the reduction ratio i of the first planet coupling mechanism this moment
1=1, therefore the reduction ratio of whole hybrid electric drive system is I=i under this serviceability
1I
2=i
2, this is the reduction ratio of second D Drive of the utility model hybrid electric drive system among Fig. 2, less (the reduction ratio i that only depends on first speed reduction gearing of this reduction ratio
2), the same with embodiment shown in Fig. 1, the reduction ratio of this second D Drive operating mode such as be specially adapted to run at high speed.
Can know by last analysis; The automobile hybrid power drive system of the utility model is through be provided with the first planet coupling mechanism dexterously; The planet coupling mechanism of winning is played a role as power coupling mechanism; But also make this first planet coupling mechanism participate in deceleration, thus realized two machinery shelves levels of automobile D Drive on first motor, the 2 infinite variable speed bases in addition, satisfied the go needs of automobile under different operating modes better.
The utility model also provides a kind of vehicle on the other hand; This vehicle comprises forerunner and/or rear-guard; Promptly this vehicle can be precursor vehicle, rear-guard vehicle or 4 wheel driven vehicle etc., and wherein one in the forerunner of this vehicle and the rear-guard is above-mentioned hybrid electric drive system.
A kind of embodiment according to the utility model; As shown in Figure 3; The forerunner of this vehicle and another person in the rear-guard comprise: second motor 14, the second planet coupling mechanism and second speed reduction gearing; The output shaft of second motor 14 is connected with the sun wheel 19 of the second planet coupling mechanism; And the output shaft of second motor 14 also is connected with the gear ring 17 of the second planet coupling mechanism through three-clutch 15, and the pinion carrier 18 that gear ring 17 is provided with second drg, 16, the second planet coupling mechanisms is connected with the input gear 20 of second speed reduction gearing.
Further, this drive system also comprises second diff 24, and the output gear 21 of this second speed reduction gearing is connected with the housing of second diff 24.
Known ground, the second planet coupling mechanism comprises gear ring 17, the pinion carrier 18 and the sun wheel 19 of a plurality of satellite gears is installed, and its matching relationship is known as satellite gear and is engaged between sun wheel 19 and the gear ring 17.
On the different axial locations of the output shaft of second motor 14; The output shaft of this second motor 14 also is connected respectively on the sun wheel 19 and gear ring 17 of the second planet coupling mechanism; Wherein, With can adopt being connected of sun wheel 19 such as the connection of key alligator groove, spline connection etc., connects indirectly with being connected through three-clutch 15 of gear ring 17, thereby can pass through joint or the separation of three-clutch 15 and optionally be connected or break off with gear ring 17.Three-clutch 15 can adopt the power-transfer clutch of multiple concrete structure; For example, three-clutch 15 adopts friction-disc clutch, and this friction-disc clutch comprises members such as clutch cover back plate, active friction disc and driven friction disk; Its steering unit (not shown) can be hydraulic control mechanism, air operated control mechanism, mechanical control mechanism etc.; Wherein, the output shaft of second motor 14 passes the clutch cover back plate of hollow and is fixedly attached to the end of this clutch cover back plate, and this active friction disc is arranged on the clutch cover back plate; Driven friction disk then relatively is arranged on the gear ring 17 with the active friction disc; Under the manipulation of clutch operating mechanism (not shown), initiatively friction disc can move axially in the clutch cover back plate upper edge, thereby optionally engages with driven friction disk or separate.Concrete structure those skilled in the art of this power-transfer clutch can expect multiple modification, but its principle that engages separation basically all is similar.
The second planet coupling mechanism can be used as adjusting the adjusting mechanism of vehicle D Drive reduction ratio through above-mentioned three-clutch 15 and the second following drg 16.As shown in Figure 3; Gear ring 17 is provided with second drg 16; This second drg 16 is similar with the structure of commonly used car brake with principle, can be on the partial-length of the outer peripheral face of gear ring 17, brake shoe brake cheek or slipper to be set, and handle this brake shoe brake cheek or slipper through fluid pressure type brake operating mechanism (not shown); Selectively engaging or to separate, thereby make that gear ring 17 is fixing or can freely rotate with the outer peripheral face of gear ring 17.
It is how right that speed reducing gear pair in second speed reduction gearing can be installed as according to actual needs, and it mainly is that engagement through multistage big or small gear pair realizes slowing down.As shown in Figure 3, second speed reduction gearing comprises input gear 20 and output gear 21, can directly mesh between input gear 20 and the output gear 21, also can connect through the multiple sets of teeth wheel set, thereby realize slowing down.
As shown in Figure 3, pinion carrier 18 is connected with the input gear 20 of second speed reduction gearing as the output shaft of the second planet coupling mechanism.Pinion carrier 18 can form as one with input gear 20; Certainly in practical situation; On the pinion carrier 18 multi-link gear wheel shafts (being input shaft or the pinion carrier 18 of second speed reduction gearing and the adapter shaft of input gear 9), drive the second speed reduction gearing in-to-in gear pair through this gear wheel shaft and slow down to increase and turn round, in the structure shown in Fig. 3 to this input gear 20; Adapter shaft between pinion carrier 18 and the input gear 20 is a hollow; So that semiaxis can therefrom pass, this is a kind of concrete structure certainly, in the technical conceive scope of the utility model, can have multiple other modified arrangement structure.
The output gear 21 of second speed reduction gearing is fixedly attached on the housing of second diff 24, this second diff 24 and then be connected on second drive wheels 23 through semiaxis.
The second planet coupling mechanism and second speed reduction gearing can for two independently mechanism install respectively; Also can be encapsulated in the housing, thereby can improve degree of integration, help reducing production costs.
The size of the first planet coupling mechanism and the second planet coupling mechanism can be the same, also can be different, and those skilled in the art can make a choice as required.
The transmitting ratio of first speed reduction gearing and second speed reduction gearing can be the same, also can be different, and those skilled in the art can make a choice as required.
Need to prove at this; Because Fig. 3 only is a scheme drawing; For making the succinctly clear members such as backup bearing wherein that omitted of figure, but these all to be those skilled in the art can expect easily, in the actual installation process, can support as the case may be.
The principle that realizes two shelves levels of automobile D Drive through the arrangement structure among Fig. 3 below will be described.
There is following equality (6) in the drive connection of the second planet coupling mechanism:
n1+n3·K2＝(1+K2)·n2
Wherein n1 is the rotating speed of sun wheel 19, and n2 is the rotating speed of pinion carrier 18, and n3 is the rotating speed of gear ring 17, and K2 is the gear ring number of teeth/sun wheel number of teeth.
In Fig. 3, when handling that second drg 16 engages so that gear ring 17 is fixing and when keeping three-clutch 15 to be in released state, the rotation speed n 3 of gear ring 17 is zero in the above-mentioned equality (6), thereby has following equality (7):
n1＝(1+K2)·n2
Thereby, this moment the second planet coupling mechanism reduction ratio i
3=n1/n2=1+K2 is because the reduction ratio of second speed reduction gearing is definite value i
4(be two reduction gear among Fig. 1, this first speed reduction gearing can also be first class reducer structure or multi-stage speed-reducing mechanism certainly), therefore the reduction ratio of whole hybrid electric drive system is I=i under this serviceability
3I
4=(1+K2) i
4, this is the reduction ratio of first D Drive of the drive system among Fig. 3, and this reduction ratio is bigger, and this is specially adapted to low speed climbing etc. needs significantly rev down to increase the operating mode of moment of torsion.
In addition; In Fig. 3, when keeping second drg 16 to be in released state, because the output shaft and the sun wheel 19 of gear ring 17 through second motor 14 is connected to integral body when making three-clutch 15 engage; So the n1=n3 in the above-mentioned equality (1), thereby there is following equality (7):
n1+n1·K2＝(1+K2)·n2
Promptly this moment n1=n2, that is to say that the second planet coupling mechanism is under this serviceability, the rotating speed of sun wheel 19, pinion carrier 18 and gear ring 17 all equates, realizes through-coupling, the reduction ratio i of the second planet coupling mechanism this moment
3=1, therefore the reduction ratio of this drive system is I=i under this serviceability
3I
4=i
4, this is the reduction ratio of second D Drive of this drive system among Fig. 3, less (the reduction ratio i that only depends on first speed reduction gearing of this reduction ratio
4), this operating mode such as be specially adapted to run at high speed.
For the ease of describing; With hybrid electric drive system shown in Figure 1 as the forerunner; As rear-guard, explain that below in conjunction with Fig. 1 and Fig. 3 the vehicle of the utility model is in the gear position operation method under different operating modes and the dynamic mode, specifically sees table 1 with the described drive system of Fig. 3:
Table 1:
Annotate: ●: expression power-transfer clutch, brake engages state; Zero: expression power-transfer clutch, drg released state; Zero/●: expression power-transfer clutch, brake engages or released state; ▲: expression combustion engine, machine operation are at driving condition;
expression machine operation is at generating state; △: expression combustion engine, motor are not worked.
Below will describe the concrete control method under the various mode of operations of this vehicle in detail:
The firstth, reverse, for forerunner's independent drive, this moment, first clutch 3 was in released state; Vehicle is driven by first motor 2, and in reverse, first motor 2 reverses under the control of control setup; And make second clutch 4 separate; First drg 5 engages, and as stated, the reduction ratio of the hybrid electric drive system that this moment is shown in Figure 1 is respectively (1+K1) i
2, this reduction ratio is bigger, and adds the speed change of first motor 2 itself, thus vehicle can move backward with speed slowly, guaranteed safety.For the rear-guard independent drive, motor 14 counter-rotating this moment second, second drg 16 engages, and three-clutch 15 separates, thereby also makes vehicle to move backward with speed slowly.Work simultaneously for forerunner and rear-guard; This moment, first motor 2 and second motor 14 all reversed; Second clutch 4 separates, and first drg 5 engages, and second drg 16 engages; Three-clutch 15 separates, the rotating speed through controlling first motor 2 and second motor 14 also can so that vehicle can move backward with speed slowly.
Second is neutral gear; In the process of moving temporary transient Parking state just, this moment, second clutch 4, first drg 5, three-clutch 15 and second drg 16 all remained on released state, because sun wheel 8, pinion carrier 7 and the gear ring 6 of the first planet coupling mechanism are all fixing; Known ground; First planet coupling mechanism this moment carry-over moment not, promptly the output speed of the first planet coupling mechanism is zero, thereby even this moment first motor 2 be in operative condition; Can powered vehicle not advance yet, thereby realized the neutral gear running.The second same planet coupling mechanism is carry-over moment not also, no matter whether second motor 14 moves and can powered vehicle not advance.
The 3rd is the D Drive under the electric-only mode, and when accumulator electric-quantity was sufficient, if vehicle is at a high speed or the low speed driving operating mode, the utility model mainly adopted electric-only mode, controls first motor 2 and/or second motor just changes through control setup.Forward gear under the electric-only mode has two shelves levels at least, and is specific as follows:
For the forerunner: first forward gear of electric-only mode: this moment, first clutch 3 all separated with second clutch 4; Operate first drg 5 and be in the engage brake state; As stated, the reduction ratio of hybrid electric drive system at this moment shown in Figure 1 is respectively (1+K1) i
2, this reduction ratio is bigger, thereby can be so that vehicle remains on relatively low at the uniform velocity motoring condition.Certainly under this electric-only mode, vehicle can also be realized acceleration mode slowly through increasing the 2 power outputs of first motor own.
Second forward gear of electric-only mode: first clutch 3 separation this moment, second clutch 4 engages, and 5 of first drgs are in released state, and as stated, the reduction ratio of the hybrid electric drive system that this moment is shown in Figure 1 is i
2, so vehicle can remain on higher relatively at the uniform velocity motoring condition.
For rear-guard: first forward gear of electric-only mode: this moment, three-clutch 15 separated, and operated second drg 16 and was in the engage brake state, and as stated, the reduction ratio of the drive system that this moment is shown in Figure 3 is respectively (1+K2) i
4, this reduction ratio is bigger, thereby can be so that vehicle remains on relatively low at the uniform velocity motoring condition.Certainly under this electric-only mode, vehicle can also be realized acceleration mode slowly through increasing the 14 power outputs of second motor own.
Second forward gear of electric-only mode: three-clutch 15 engages at this moment, and 16 of second drgs are in released state, and as stated, the reduction ratio of the drive system that this moment is shown in Figure 3 is i
4, so vehicle can remain on higher relatively at the uniform velocity motoring condition.
For 4 wheel driven: first forward gear of electric-only mode: this moment, first clutch 3, second clutch 4 all separated with three-clutch 15; Operate first drg 5 and second drg 16 is in the engage brake state; As stated, the reduction ratio of hybrid electric drive system at this moment shown in Figure 1 is respectively (1+K1) i
2, the reduction ratio of drive system shown in Figure 3 is respectively (1+K2) i
4, this reduction ratio is bigger, thereby can be so that vehicle remains on relatively low at the uniform velocity motoring condition.Certainly under this electric-only mode, vehicle can also be realized acceleration mode slowly through the power output that increases first motor 2 and second motor 14 itself.
Second forward gear of electric-only mode: first clutch 3 separation this moment; Second clutch 4 and three-clutch 15 engage; First drg 5 and 16 of second drgs are in released state, and as stated, the reduction ratio of the hybrid electric drive system that this moment is shown in Figure 1 is i
2, the reduction ratio of drive system shown in Figure 3 is i
4, so vehicle can remain on higher relatively at the uniform velocity motoring condition.
For the control method of its forward gear of 4 wheel driven can also for: control first clutch 3 all separates with second clutch 4, operates first drg 5 and is in the engage brake state; Control three-clutch 15 simultaneously and engage, second drg 16 is in released state.Perhaps control first clutch 3 and separate, second clutch 4 engages, and first drg 5 is in released state; Control three-clutch 15 simultaneously and separate, operate second drg 16 and be in the engage brake state.
The 4th is the D Drive under the hybrid power series model; The series model of hybrid power mainly is to drive 2 generatings of first motor through combustion engine 1; And be re-supplied to second motor 14 after directly supplying with second motor 14 or be stored into storage battery through the electric power that said control setup produces first motor 2, so that second motor 14 advances as direct driving force source powered vehicle.This hybrid power series model is applicable to that mainly accumulator electric-quantity is not enough, and needs to keep the operating mode of uniform high speed of automobile or low speed driving.
First forward gear under the series model: at this moment, first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 separates, and second drg 16 engages, and combustion engine 1 drives 2 generatings of first motor, and second motor, 14 powered vehicle are advanced.
Second forward gear under the series model: at this moment, first clutch 3 and three-clutch 15 engage, and second clutch 4 separates, and first drg, 5 second drgs 16 all separate, and combustion engine 1 drives 2 generatings of first motor, and second motor, 14 powered vehicle are advanced.
The 5th is the forward gear under the hybrid power paralleling model; The paralleling model of hybrid power mainly is combustion engine and motor driven in common vehicle; Combustion engine and motor adhere to two cover systems separately; Can to vehicle transmission system moment of torsion be provided independently respectively, not only can driven in common on different road but also can the independent drive automobile.
Parallelly connected for the forerunner: first forward gear: first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 engages, and second drg 16 separates, and combustion engine 1 and first motor, 2 driven in common vehicles advance.
Second forward gear: first clutch 3 all engages with second clutch 4, and three-clutch 5 separates, and first drg 5 all separates with second drg 16, and combustion engine 1 and first motor, 2 driven in common vehicles advance.
For 4 wheel driven parallel connection I: first forward gear: first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 and second drg 16 all engage, and combustion engine 1, first motor 2 and second motor, 14 driven in common vehicles advance.
Second forward gear: first clutch 3, second clutch 4 and three-clutch 5 all engage, and first drg 5 all separates with second drg 16, and combustion engine 1, first motor 2 and second motor, 14 driven in common vehicles advance.
For 4 wheel driven parallel connection II: first forward gear: first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 and second drg 16 all engage, and combustion engine 1 and second motor, 14 driven in common vehicles advance.
Second forward gear: first clutch 3, second clutch 4 and three-clutch 5 all engage, and first drg 5 all separates with second drg 16, and combustion engine 1 and second motor, 14 driven in common vehicles advance.
The 6th is the D Drive under the hybrid power series-parallel connection pattern.The series-parallel connection pattern of hybrid power system mainly is applicable to the situation of automobile climbing or brish acceleration, and this moment, vehicle needed bigger power output, under this series-parallel connection pattern, existed multiple power transmission line to adapt to the different needs that go.Specific as follows:
First D Drive of hybrid power series-parallel connection pattern: first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 and second drg 16 all are in the engage brake state.At this moment, the power part of combustion engine 1 is used for driving 2 generatings of first motor so that supply with second motor, 14 outputting powers; Another part is used for exporting first drive wheels 12 to through the first planet coupling mechanism, because the output of mixed power is bigger, the moment of torsion that therefore increases can guarantee driving cycles such as vehicle implementation climbing.
Second forward gear of hybrid power series-parallel connection pattern: first clutch 3, second clutch 4 and three-clutch 15 all engage, and first drg 5 and second drg 16 all are in released state.At this moment, the power part of combustion engine 1 is used for driving 2 generatings of first motor so that supply with second motor, 14 outputting powers; Another part is used for exporting first drive wheels 12 to through the first planet coupling mechanism, and this moment, vehicle can be realized brish acceleration through powerful power output, and can remain on the highest at the uniform velocity motoring condition through above-mentioned electric-only mode subsequently.
The 7th is the internal combustion engine drive pattern, and first forward gear of this pattern is: first clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 engages, and second drg 16 separates.At this moment, combustion engine 1 independent drive vehicle advances.
Second forward gear of this pattern is: first clutch 3 all engages with second clutch 4, and three-clutch 15 separates, and first drg 5 all separates with second drg 16.At this moment, combustion engine 1 independent drive vehicle advances.
Under the internal combustion engine drive pattern, can also control first motor 2 as generator operation, thereby utilize a part of dynamic power of combustion engine 1 and be stored in the storage battery of wheel.
The 8th is the parking power generation mode; At this moment; First clutch 3 engages, and second clutch 4 all separates with three-clutch 15, and first drg 5 also all separates with second drg 16; The equal outputting power not of this moment first planet coupling mechanism and second planet coupling mechanism, combustion engine 1 drives 2 generatings of first motor.
Can find out by last analysis; The hybrid electric drive system of the utility model is according to the different driving cycles of vehicle; Selecting various mode of operations and respective notch flexibly, can be main with motor-driven, and combustion engine 1 almost be operated in its maximal efficiency district always under hybrid power series-parallel connection pattern; Avoid combustion engine 1 to be in idling and low-speed running operating mode, thereby improved fuel utilization ratio; Secondly, first motor 2 still can be used as the starter motor of traditional combustion engine 1, and therefore first motor 2 is actual has a triple functions: starter motor, electrical generator and drive motor.In addition; Hybrid electric drive system with adjustable two D Drive levels can make that the effective deceleration of car load is faster with increase moment of torsion, starting; And under at a high speed, can give play to the peak efficiency of motor and combustion engine biglyyer; Improve energy conversion efficiency, reduce exhaust emissions and reduce waste of power, finally reach effects such as the anti-emission carburetor of car load, low oil consumption and kinetic energy.
The vehicle that provides of the utility model can adopt above-mentioned hybrid electric drive system as forerunner or rear-guard in addition, and drive system shown in Figure 3 also can be used as forerunner or rear-guard simultaneously.When vehicle adopts above-mentioned hybrid electric drive system and drive system shown in Figure 3 simultaneously; Because two kinds of drive systems all can realize two grades; Therefore those skilled in the art can be combined into various suitable gears as required, thereby have improved the working ability of vehicle under different operating modes greatly.
The above is merely the preferred embodiment of the utility model; Not in order to restriction the utility model; Any modification of being done within all spirit and principles at the utility model, be equal to replacement and improvement etc., all should be included within the protection domain of the utility model.
Claims (10)
1. hybrid electric drive system; Comprise combustion engine, first motor, the first planet coupling mechanism and first speed reduction gearing; It is characterized in that; The output shaft of said combustion engine is connected with the output shaft of said first motor through first clutch; The output shaft of said first motor on a position of its axial direction with the sun wheel of the said first planet coupling mechanism and gear ring in one be connected; And the output shaft of said first motor also is connected with another person in the gear ring through second clutch and said sun wheel on another position of its axial direction, and another person in this sun wheel and the gear ring is provided with first drg, and the pinion carrier of the said first planet coupling mechanism is connected with the input gear of said first speed reduction gearing.
2. hybrid electric drive system as claimed in claim 1 is characterized in that, said first clutch, second clutch and first drg power-transfer clutch and the drg that separately hydraulic control mechanism is handled of serving as reasons.
3. hybrid electric drive system as claimed in claim 1 is characterized in that, the line of centers of the output shaft of said combustion engine, the said first planet coupling mechanism and the output shaft of said first motor are on the same axis.
4. hybrid electric drive system as claimed in claim 1 is characterized in that, said combustion engine is positioned at a side of the said first planet coupling mechanism, and said first motor is positioned at the opposite side of the said first planet coupling mechanism.
5. hybrid electric drive system as claimed in claim 4 is characterized in that, said pinion carrier is connected on the input gear of said first speed reduction gearing through the adapter shaft of hollow, and the output shaft of said first motor passes in the adapter shaft of this hollow.
6. hybrid electric drive system as claimed in claim 1 is characterized in that, said first planet coupling mechanism and said first speed reduction gearing are encapsulated in the housing.
7. a vehicle is characterized in that, one in the forerunner of said vehicle and the rear-guard is any described hybrid electric drive system among the claim 1-6.
8. vehicle as claimed in claim 7; It is characterized in that; Another person in said forerunner and the rear-guard comprises: second motor, the second planet coupling mechanism and second speed reduction gearing; The output shaft of said second motor is connected with the sun wheel of the said second planet coupling mechanism; And the output shaft of said second motor also is connected with the gear ring of the said second planet coupling mechanism through three-clutch, and said gear ring is provided with second drg, and the pinion carrier of the said second planet coupling mechanism is connected with the input gear of said second speed reduction gearing.
9. vehicle as claimed in claim 8 is characterized in that, the said three-clutch and second drg power-transfer clutch and the drg that separately hydraulic control mechanism is handled of serving as reasons.
10. vehicle as claimed in claim 8 is characterized in that, said second planet coupling mechanism and said second speed reduction gearing are encapsulated in the housing.
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| CN2010201225175U CN202186277U (en) | 2010-02-27 | 2010-02-27 | Hybrid drive system and vehicle comprising same |
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| CN2010201225175U CN202186277U (en) | 2010-02-27 | 2010-02-27 | Hybrid drive system and vehicle comprising same |
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| CN102705457A (en) * | 2012-06-29 | 2012-10-03 | 成都凯迈科技有限公司 | Variable-speed transmission device for electric automobile |
| CN104494414A (en) * | 2014-11-26 | 2015-04-08 | 天津博信汽车零部件有限公司 | Power transmission system and vehicle with same |
| CN105697693A (en) * | 2014-11-28 | 2016-06-22 | 舍弗勒技术有限两合公司 | Electric continuously variable transmission and vehicle comprising same |
| CN106195170A (en) * | 2016-08-30 | 2016-12-07 | 重庆青山工业有限责任公司 | A kind of hybrid-powered motor speed variator assembly |
| CN106891713A (en) * | 2017-04-14 | 2017-06-27 | 重庆青山工业有限责任公司 | A kind of mixed power automobile driving system |
| CN106931103A (en) * | 2015-12-31 | 2017-07-07 | 重庆硬核派传动科技有限公司 | One kind uses planetary three-speed gear |
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| CN108016267A (en) * | 2017-12-29 | 2018-05-11 | 聊城大学 | A kind of single motor coupler of pure electric vehicle |
| CN108327497A (en) * | 2018-01-25 | 2018-07-27 | 北京长城华冠汽车科技股份有限公司 | Electric drive axle system |
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| CN110920370A (en) * | 2019-12-06 | 2020-03-27 | 无锡康博瑞特电子科技有限公司 | Multi-gear change differential motor |
| CN111194274A (en) * | 2017-08-02 | 2020-05-22 | 罗伯特·博世有限公司 | Transmission for a hybrid drive system, vehicle, method for operating a hybrid drive system, computer program and storage medium |
| CN111301146A (en) * | 2018-12-12 | 2020-06-19 | 广州汽车集团股份有限公司 | Hybrid power coupling system and vehicle |
| CN111591121A (en) * | 2020-04-22 | 2020-08-28 | 合肥工业大学 | Dual-motor electric automobile driving system based on planetary gear |
| CN112519560A (en) * | 2020-12-03 | 2021-03-19 | 格特拉克（江西）传动系统有限公司 | Transmission, range extending type hybrid power system and vehicle |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102705457A (en) * | 2012-06-29 | 2012-10-03 | 成都凯迈科技有限公司 | Variable-speed transmission device for electric automobile |
| CN104494414A (en) * | 2014-11-26 | 2015-04-08 | 天津博信汽车零部件有限公司 | Power transmission system and vehicle with same |
| CN105697693A (en) * | 2014-11-28 | 2016-06-22 | 舍弗勒技术有限两合公司 | Electric continuously variable transmission and vehicle comprising same |
| CN106931103A (en) * | 2015-12-31 | 2017-07-07 | 重庆硬核派传动科技有限公司 | One kind uses planetary three-speed gear |
| CN106195170A (en) * | 2016-08-30 | 2016-12-07 | 重庆青山工业有限责任公司 | A kind of hybrid-powered motor speed variator assembly |
| CN106891713A (en) * | 2017-04-14 | 2017-06-27 | 重庆青山工业有限责任公司 | A kind of mixed power automobile driving system |
| CN106956579A (en) * | 2017-05-08 | 2017-07-18 | 重庆大学 | Hollow motor formula electric automobile driving switching and transmission gear shift system |
| CN106956579B (en) * | 2017-05-08 | 2023-12-01 | 重庆大学 | Hollow motor type electric automobile driving switching and transmission speed changing system |
| CN111194274A (en) * | 2017-08-02 | 2020-05-22 | 罗伯特·博世有限公司 | Transmission for a hybrid drive system, vehicle, method for operating a hybrid drive system, computer program and storage medium |
| CN107542917A (en) * | 2017-08-24 | 2018-01-05 | 江苏大学 | A kind of power failure-free gear shift automatic speed changer for machine hybrid drive train |
| CN107542917B (en) * | 2017-08-24 | 2019-06-28 | 江苏大学 | A kind of power failure-free gear shift automatic speed changer for machine hybrid drive train |
| CN108016267A (en) * | 2017-12-29 | 2018-05-11 | 聊城大学 | A kind of single motor coupler of pure electric vehicle |
| CN108327497A (en) * | 2018-01-25 | 2018-07-27 | 北京长城华冠汽车科技股份有限公司 | Electric drive axle system |
| CN110549837A (en) * | 2018-05-30 | 2019-12-10 | 广州汽车集团股份有限公司 | Hybrid power drive system |
| CN111301146A (en) * | 2018-12-12 | 2020-06-19 | 广州汽车集团股份有限公司 | Hybrid power coupling system and vehicle |
| CN110920370A (en) * | 2019-12-06 | 2020-03-27 | 无锡康博瑞特电子科技有限公司 | Multi-gear change differential motor |
| CN111591121A (en) * | 2020-04-22 | 2020-08-28 | 合肥工业大学 | Dual-motor electric automobile driving system based on planetary gear |
| CN112519560A (en) * | 2020-12-03 | 2021-03-19 | 格特拉克（江西）传动系统有限公司 | Transmission, range extending type hybrid power system and vehicle |
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