CN201777126U - Hybird power drive system and vehicle comprising same - Google Patents
Hybird power drive system and vehicle comprising same Download PDFInfo
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- CN201777126U CN201777126U CN2010202133880U CN201020213388U CN201777126U CN 201777126 U CN201777126 U CN 201777126U CN 2010202133880 U CN2010202133880 U CN 2010202133880U CN 201020213388 U CN201020213388 U CN 201020213388U CN 201777126 U CN201777126 U CN 201777126U
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Abstract
The utility model relates to a hybird power drive system, which comprises an internal combustion engine, a first motor, a clutch, a second motor, an output shaft for outputting e power, a first input shaft and a second input shaft, wherein a first transmission ratio is formed between the first input shaft and the output shaft through one stage or multiple stages of gear pairs, a second transmission ratio is formed between the second input shaft and the output shaft through one stage or multiple stages of gear pairs, the internal combustion engine is connected with the first motor, the first motor is connected with the first input shaft through the clutch, and the second motor is connected with the second input shaft. The utility model also provides a vehicle comprising the hybird power drive system. Because the hybird power drive system is provided with two input shafts and one output shaft, two gear stages of forwards gears of the vehicle can be formed, each work mode and each corresponding gear can be flexibly selected according to different driving conditions of vehicles, and the driving requirements on the vehicle under different driving conditions can be perfectly met.
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
The mankind of the world today are faced with energy shortage and ecological deterioration two is challenged greatly, and orthodox car is subjected to the serious puzzlement of oil crises day by day, and energy-conserving and environment-protective become the development topic of auto trade gradually.Given this, the appealing of releasing pure electric automobile grows to even greater heights, but is subjected to all multifactor restrictions such as technology, policy, and current pure electric automobile also can't be realized volume production, introducing to the market comprehensively.
Hybrid vehicle was undoubtedly before pure electric automobile is realized industrialization, the most one of Xian Shi technology owing to its outstanding representation aspect energy-conservation and environmental protection.
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, wherein, electrical motor 200 is given gear ring 400 by gear 300 with transmission of power, combustion engine 100 is given sun wheel 600 with transmission of power, then the two power is coupled by 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 of reduction gear train, and its reduction ratio is changeless after the reducing gearbox manufacturing is finished.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 by the control motor of reversing gear of hybrid vehicle realizes that speed change then mainly realizes that by the rotating speed of adjusting electrical motor this is equivalent to a kind of stepless change.
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 travel of this automobile) situation following time, need make the output torque after combustion engine 100 and electrical motor 200 couplings reach maximum, this moment, the output torque of electrical motor 200 should reach maximum in this case, could the driving automobile climbing but this output speed must slow down through speed reduction gearing 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 travelling 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 the rotating speed after this moment electrical motor 200 and combustion engine 100 couplings reaches maximum, but through the deceleration of the bigger reduction ratio of speed reduction gearing, the moving velocity of automobile is still not ideal enough.
By last analysis as can be known, the gear shift mode of traditional automobile hybrid power drive system can not satisfy the needs that travel under the different operating modes of automobile, and 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 travel 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 travel 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 power-transfer clutch and second motor, wherein, described hybrid electric drive system also comprises the output shaft that is used for outputting power and separately to first input shaft and second input shaft of described output shaft transmitting power, form first transmitting ratio by one or more levels gear pair between first input shaft and the output shaft, form second transmitting ratio by one or more levels gear pair between second input shaft and the output shaft, described combustion engine is connected with described first motor, described first motor is connected with described first input shaft by described power-transfer clutch, and described second motor is connected with described second input shaft.
Further, be fixed with first gear on described first input shaft, be fixed with second gear on described second input shaft, be fixed with the 3rd gear and the 4th gear on the described output shaft, described first gear and described the 3rd gear mesh form first transmitting ratio, and described second gear and described the 4th gear mesh form second transmitting ratio.
Described hybrid electric drive system also comprises diff, and described diff is connected with described the 3rd gear or described the 4th gear.
Described hybrid electric drive system also comprises diff, also is fixed with the 5th gear on the described output shaft, and described diff is connected with described the 5th gear.
Further,
Described first transmitting ratio is less than described second transmitting ratio.
The output shaft of the output shaft of the output shaft of described combustion engine, described first motor and described second motor is on the same axis.
One end of described first gear is provided with quill shaft, an end of described second input shaft by bearing installation in described quill shaft.
Described hybrid electric drive system also comprises double mass flywheel, and described combustion engine is connected with described first motor by described double mass flywheel.
Described power-transfer clutch comprises first friction member and second friction member that contacts or separate under the driving of hydraulic pressure release thrust bearing, described first friction member is captiveed joint with the rotor of described first motor, and described second friction member is captiveed joint with described first input shaft.
The utility model also provides a kind of vehicle on the other hand, and wherein, described vehicle comprises above-mentioned hybrid electric drive system.
Hybrid electric drive system of the present utility model and comprise the vehicle of this drive system, owing to be provided with two input shafts and an output shaft, connect by gear pair respectively between two input shafts and the output shaft, the combustion engine and second motor are respectively by two input shaft outputting powers, thereby two shelves levels of vehicle D Drive have been formed, and then can be according to the different driving cycles of vehicle, select various mode of operations and each respective notch flexibly, so well satisfied the travel needs of vehicle under different operating modes.In addition, hybrid electric drive system with two D Drive levels of the present utility model can make that the car load low speed torque increases, starting is faster, and under high speed, can give play to the peak efficiency of combustion engine better, improved energy conversion efficiency, reduce 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 the structural representation of a kind of embodiment of the hydraulic pressure release thrust bearing among Fig. 2;
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 drawings and Examples, 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.
According to a kind of embodiment of the present utility model, as depicted in figs. 1 and 2, a kind of hybrid electric drive system, comprise combustion engine 1, first motor 3, the power-transfer clutch 4 and second motor 10, wherein, this hybrid electric drive system also comprises the output shaft 16 that is used for outputting power and separately to first input shaft 5 and second input shaft 7 of output shaft 16 transmitting powers, form first transmitting ratio by one or more levels gear pair between first input shaft 5 and the output shaft 16, form second transmitting ratio by one or more levels gear pair between second input shaft 7 and the output shaft 16, combustion engine 1 is connected with first motor 3, the output shaft of first motor 3 is connected with first input shaft 5 by power-transfer clutch 4, and second motor 10 is connected with second input shaft 7.
Between input shaft and the output shaft one or more levels gear pair can be set as required,, connect by multi-stage gear is secondary between input shaft and the output shaft in order to pursue bigger transmitting ratio; For common cars of taking such as hybrid vehicles, can satisfy the needs of transmitting ratio between input shaft and the output shaft by the one-level gear pair, so for simplified structure, further, be fixed with first gear 81 on first input shaft 5, be fixed with second gear 91 on second input shaft 7, be fixed with the 3rd gear 82 and the 4th gear 92 on the output shaft 16, first gear 81 and 82 engagements of the 3rd gear form the first transmitting ratio K1, and second gear 91 and 92 engagements of the 4th gear form the second transmitting ratio K2.
Further, according to a kind of embodiment of the present utility model, this hybrid electric drive system also comprises diff 11, and diff 11 is connected with the 3rd gear 82 or the 4th gear 92.
According to another kind of embodiment of the present utility model, also be fixed with the 5th gear (not shown) on the output shaft 16, diff 11 is connected with the 5th gear.
Diff is the main part that drives sedan-chair, the effect of diff is exactly in the semiaxis transferring power of both sides, allow the both sides semiaxis with different rotating speed rotations, satisfy two sidecar wheels and do equidistantly not travel with the form of pure rolling as far as possible, reduce tire and ground-surface friction.Open differential is made up of parts such as satellite gear, planetary wheel carrier (differential gear box), axle side gears.Power enters diff, and the direct drive planetary wheel carrier drives left and right two semiaxis by satellite gear again, drives left and right wheel respectively.
Because meshing respectively, first gear 81 and the 3rd gear 82, second gear 91 and the 4th gear 92 form two transmitting ratio K1 and K2, between output shaft 16 and diff 11, can also form a transmitting ratio K3, so the transmitting ratio of car load has two, be respectively K=K1*K3 and K '=K2*K3.Wherein, K3 can be formed by the planetary wheel carrier engagement of the 3rd gear 82, the 4th gear 92 or the 5th gear and diff 11.Those skilled in the art can select the planetary wheel carrier engagement of the 3rd gear 82, the 4th gear 92 or the 5th gear and diff 11 as required.In order to form broader gear range, K3 can be formed by the planetary wheel carrier engagement of the 5th gear and diff 11.On the other hand, in order to reduce taking up room of part, reduce the quantity of part, cost-cutting, K3 can be formed by the 3rd gear 82 or the 4th gear 92 and planetary wheel carrier engagement with diff 11.
Two grades that it should be noted that two gears of the present utility model (or two transmitting ratios of car load) and general meaning is different, in scheme of the present utility model, the combustion engine 1 and second motor 10 are to pass through two transmitting ratios (or two gears) outputting power respectively, be that combustion engine 1 uses the first transmitting ratio K1 outputting power, second motor 10 uses the second transmitting ratio K2 outputting power.
Further, the first transmitting ratio K1 is different with the second transmitting ratio K2, can make the first transmitting ratio K1 greater than the second transmitting ratio K2 as required, also can make the first transmitting ratio K1 less than the second transmitting ratio K2.Preferably, the first transmitting ratio K1 is less than the second transmitting ratio K2.
In order to improve the fuel economy of combustion engine 1, especially the fuel economy during high speed, meshing two transmitting ratio K1 that form by first gear 81 respectively with the 3rd gear 82, second gear 91 and the 4th gear 92 should be different with K2, further, the transmitting ratio K1 of first gear 81 and the 3rd gear 82 is less than the transmitting ratio K2 of second gear 91 and the 4th gear 92, thereby makes the transmitting ratio K of car load also less than K '.
For the hybrid power scheme of having only a car load transmitting ratio in the prior art, in order to guarantee that vehicle normally starts, it is bigger that this transmitting ratio is provided with usually, thereby make that the moment of torsion of combustion engine and/or motor output is bigger, and vehicle just can have bigger moment of torsion normally to start like this.This vehicle is starting or can well meet requirements during low cruise, but during high-speed cruising, because transmitting ratio is bigger, combustion engine can't guarantee to be operated in the fuel-economy district always, thereby has reduced the degree of utilization of fuel oil, has increased oil consumption, worsen discharging, be unfavorable for environmental protection.Simultaneously, in order to take into account the output performance of combustion engine and motor, and satisfy the output of vehicle, this vehicle may need to be provided with a more high-performance motor, and motor just relatively takes up room like this, has also increased the cost of car load.
Form the hybrid power scheme of two transmitting ratios for the available technology adopting planet circular system, because planet circular system structure more complicated, need to brake certain rotating element such as pinion carrier or gear ring in use, parts such as drg so just need be set realize, control also more complicated; Simultaneously since in the planet circular system rotating element such as rotating speeds such as sun wheel, pinion carrier higher, channel for oiling need be set in planet circular system.The axial dimension of whole like this hybrid electric drive system is bigger, and the structure more complicated is controlled also more complicated, and cost is just than higher.
And hybrid electric drive system of the present utility model and the vehicle that comprises this drive system, owing to be provided with two input shafts and then formed two transmitting ratios, so can be so that vehicle adopts a bigger transmitting ratio when startup and low cruise, when high-speed cruising, adopt a less transmitting ratio, thereby make vehicle when low speed, can export high pulling torque, can export high speed during high speed.The power that is combustion engine 1 output is through a less transmitting ratio K, thereby can better bring into play the performance of combustion engine 1 when high vehicle speeds, and the fuel economy when improving combustion engine 1 high-speed cruising improves fuel utilization ratio, reduces oil consumption, alleviates discharging.And the power of second motor 10 output is through a bigger transmitting ratio K ', thereby can export a big moment of torsion and then start vehicle smoothly and make the vehicle low cruise.
On the other hand, owing to be provided with two transmitting ratios, these two transmitting ratio K and K ' can differ bigger as required simultaneously, so just can reduce the power of second motor 10, the motor that promptly can select a smaller power for use is as second motor 10, thereby reduced taking up room of this hybrid electric drive system, saved integral vehicle cost.
Simultaneously, owing to adopt two groups of gear pairs to form two transmitting ratios, therefore, and whole hybrid electric drive system relatively simple for structure, axial space is also smaller, more helps spatial destribution, especially is fit to the little vehicle of axial space.A change speed gear box can be set in addition, thereby first gear 81, first input shaft 5, second input shaft 7, second gear 91, the 3rd gear 82, the 4th gear 92 and output shaft 16 are installed and fixed in this change speed gear box.Usually, have lubricating oil in the change speed gear box, when vehicle ', the 3rd gear 82, the 4th gear 92 just can stir lubricating oil, thereby realize the lubricated of gear easily and need not to be provided with in addition oil leab.The cost of gear is lower simultaneously, and need not to be provided with synchro and wait to control and switch two transmitting ratios, therefore can effectively reduce the cost of whole hybrid electric drive system, and then reduce the cost of motor vehicle driven by mixed power, more help popularizing of motor vehicle driven by mixed power.
Hybrid electric drive system of the present utility model owing to be provided with two transmitting ratios, makes the combustion engine 1 and second motor 10 can pass through these two transmitting ratio outputting powers respectively; Simultaneously since first transmitting ratio less than second transmitting ratio, can be so that vehicle adopts second motor by the second transmitting ratio outputting power when startup, climbing and low cruise; Vehicle can adopt combustion engine 1 by the first transmitting ratio outputting power when high-speed cruising, thus the fuel economy of combustion engine 1 when having improved the vehicle high-speed cruising.Vehicle can both well be brought into play the performance of each propulsion source under operating modes such as startup, climbing and high-speed cruising like this, has improved the energy utilization of vehicle, helps reducing the consumption of the energy such as electric energy and fuel oil.
Those skilled in the art as required can be so that the output shaft conllinear of the output shaft of second motor 10 and combustion engine 1 or conllinear not.In order to reduce the radially installing space of this hybrid electric drive system, preferably, the output shaft of the output shaft of combustion engine 1, first motor 3 and the output shaft of second motor 10 are on the same axis.
Can captive joint by various suitable manner between the known ground, axle and gear, as connecting by spline.Promptly can be connected by spline between first input shaft 5 and first gear 81, second input shaft 7 and second gear 91, output shaft 16 and the 3rd gear 82 and the 4th gear 92.
Further, for the size that reduces output shaft 16 and simplify being connected and fixed of output shaft 16 and the 3rd gear 82 and the 4th gear 92, the 3rd gear 82 and the 4th gear 92 can be same gear or two gears that are formed in one.
Specifically, be at power-transfer clutch 4 under the situation of engagement state, when combustion engine 1 work, the power of combustion engine 1 can be delivered to first input shaft 5 by power-transfer clutch 4.Because combustion engine 1 links to each other with the rotor of first motor 3, therefore when combustion engine 1 is worked, no matter whether power-transfer clutch 4 engages, the rotor of first motor 3 all will be under the drive of combustion engine 1 and turn round, and when 3 work of first motor, equally also will drive combustion engine 1 running.
Owing to have said structure, thereby first motor 3 can be as the starter motor of combustion engine 1, thereby need not extra starter motor to be set for combustion engine 1, first motor 3 can also be to first input shaft, 5 outputting powers simultaneously, thereby, satisfying under the situation of power demand, saving the part installing space.In addition, when needs vehicle reverse gear, 10 counter-rotatings of second motor can be realized, thereby need not to be provided with extra gear reversing device, thereby further saved the installing space that gear reversing device is installed, made hybrid electric drive system provided by the utility model have comparatively compact integral structure.
The rotor of first motor 3 is a hollow structure, at least a portion of power-transfer clutch 4 is arranged in this hollow structure, preferably, power-transfer clutch 4 all is arranged in this hollow structure, the inwall of the rotor of first motor 3 links to each other with power-transfer clutch 4, power-transfer clutch 4 also links to each other with first input shaft 5, i.e. the power of the rotor of first motor 3 output directly is transported to first input shaft 5 by power-transfer clutch 4, finally is delivered to wheel.Power-transfer clutch 4 is installed in this hollow structure can be effectively saved axial installing space.
Hybrid electric drive system of the present utility model also comprises the closed-center system (not shown), and this closed-center system is electrically connected with first motor 3 and second motor 10 respectively.This closed-center system is used for electrical power storage that first motor 3 and second motor 10 are produced as electrical generator the time, so that in needs, again to first motor 3 and/or 10 power supplies of second motor.This closed-center system is the electric energy unit that can repeatedly discharge and recharge, as lithium rechargeable battery etc.
Further, this closed-center system can also be connected with the electric energy power input device, promptly charges to closed-center system by the electric energy power input device, thereby constitutes " plug-in type " hybrid electric drive system.
Generally speaking, can there be vibration in the power of combustion engine 1 output, in order to reduce this vibration, can be provided with dampings such as torsion vibration absorber on the output shaft of combustion engine 1.According to a kind of embodiment of the present utility model, further, this hybrid electric drive system also comprises double mass flywheel 2, and combustion engine 1 is connected with first motor 3 by double mass flywheel 2.
Double mass flywheel is divided into two parts with an original flywheel exactly, and a part is retained on the position of original combustion engine one side, plays the effect of original flywheel, is used to start and transmit the driving torque of combustion engine, and this part is called elementary quality.Another part then is placed on transmission system gear shift device one side, the rotor inertia that is used to improve change-speed box, and this part is called secondary mass.A ring-like oil pocket is arranged between two parts flywheel, jounce bumper is housed in the chamber, connect two parts flywheel as a whole by jounce bumper.Because secondary mass can improve the moment of inertia of transmission system under the prerequisite of the moment of inertia that does not increase flywheel, make resonance speed drop to below the idling speed.
Double mass flywheel is the best device of vibration isolation and damping effect on the current automobile, therefore this double mass flywheel 2 is provided with the vibration isolation and damping that can realize between the combustion engine 1 and first motor 3, help reducing the adverse effect of 1 pair first motor 3 of combustion engine, thereby improved the real work performance of first motor 3.
Usually, axle needs two bearings fix support, as the two ends of first input shaft 5 two bearings can be set and fix support, and the two ends of second input shaft 7 also can be provided with two bearings and fix support.Because first gear 81 and second gear 91 are respectively at the 3rd gear 82 and 92 engagements of the 4th gear, and the 3rd gear 82 and the 4th gear 92 all are fixed on the output shaft 16, in order to reduce the fixed pedestal difficulty of first input shaft 5 and second input shaft 7, simplify the structure of change speed gear box, according to a kind of embodiment of the present utility model, as shown in Figure 2, end at first gear, 81 close second motors 10 is provided with quill shaft 15, this quill shaft 15 can be one-body molded with first gear 81, also can be installed on first gear 81 in addition, in order better to guarantee build-up tolerance, reduce wearing and tearing, improve service life, preferably, first gear 81 is one-body molded with this quill shaft 15, and the central axis conllinear of the central axis of this quill shaft 15 and first gear 81.One end of second input shaft 7 relies on bearing fixing to support, the other end promptly near an end of first motor 3 by bearing installation in this quill shaft 15.In order to improve the support strength of this end, preferably, an end of second input shaft 7 is installed in this quill shaft 15 by needle bearing 14.
Because the gear pair in the change speed gear box generally all is a helical wheel, and helical wheel can produce axial force, in order to reduce influence to input shaft, therefore also be provided with thrust baring 13 between second input shaft 7 and first gear 81, an end that promptly is installed on second input shaft 7 in the quill shaft 15 also is equipped with thrust baring 13.
Similarly, also can be provided with quill shaft 15 (not shown)s at an end of second gear, 91 close combustion engines 1, this quill shaft 15 can be one-body molded with second gear 91, also can be installed in addition on second gear 91.In order better to guarantee to reduce wearing and tearing by build-up tolerance, improve service life, preferably, second gear 91 is one-body molded with this quill shaft 15, and the central axis conllinear of the central axis of this quill shaft 15 and second gear 91.One end of first input shaft 5 relies on bearing fixing to support, the other end promptly near an end of second motor 10 by bearing installation in this quill shaft 15.In order to improve the support strength of this end, preferably, an end of first input shaft 5 is installed in this quill shaft 15 by needle bearing 14.
Because the gear pair in the change speed gear box generally all is a helical wheel, and helical wheel can produce axial force, in order to reduce influence to input shaft, therefore also be provided with thrust baring 13 between first input shaft 5 and second gear 91, an end that promptly is installed on first input shaft 5 in the quill shaft 15 also is equipped with thrust baring 13.
Such first input shaft 5 and second input shaft 7 both can well satisfy the installation of two input shafts again and support demand separately to output shaft 16 transmitting powers.
Power-transfer clutch 4 can be selected various suitable arrangement of clutch as required, as being liquid clutch.Because liquid clutch is the rotating hydraulic cylinder, the leak tightness of also having relatively high expectations simultaneously when in the hollow structure that liquid clutch is installed to first motor 3, needs to guarantee higher sealing effectiveness, also need to offer oil duct simultaneously, thus the folding of control liquid clutch.
In order to reduce the installation requirement of power-transfer clutch 4, simplify mounting structure, according to a kind of embodiment of the present utility model, power-transfer clutch 4 comprises first friction member and second friction member that can cooperate transmission, first friction member is captiveed joint with the rotor of first motor 3, and second friction member is captiveed joint with first input shaft 5.First friction member and second friction member can be friction lining or friction disc, as long as the transmission or the interruption that can cooperatively interact and realize power.
First friction member and second friction member all can be multi-disc friction sheet or friction disc, those skilled in the art can make choose reasonable as required, as first friction member and second friction member adopt with liquid clutch in friction element similarly be connected arrangement form.
Power-transfer clutch 4 is by 6 controls of hydraulic pressure release thrust bearing, as shown in Figure 3, hydraulic pressure release thrust bearing 6 comprises: hydraulic actuating cylinder and release thrust bearing 61, the inner ring of release thrust bearing 61 is captiveed joint with the piston of hydraulic actuating cylinder 62, hydraulic actuating cylinder comprises cylinder body 64, be plugged in the cylinder body 64 and form the cylinder core 67 of an end osed top annulus 63 with cylinder body 64 and be arranged in this end osed top annulus 63 and can axially movable piston 62, piston 62 and the inwall of cylinder body 64 and the outer wall sealing contact of cylinder core 67, cylinder body 64 is provided with the passage 65 that is communicated with annulus 63, and this passage 65 is connected with hydraulic oil pipe 66.
First friction member or second friction member can contact with release thrust bearing 61 or separate, promptly first friction member contacts transferring power or disconnects and cut off power with second friction member under the effect of release thrust bearing 61, and perhaps second friction member contact transferring power or disconnects cut-out power with first friction member under the effect of release thrust bearing 61.
Further, cylinder core 67 has hollow structure, and the output shaft of first motor 3 passes cylinder core 67 and links to each other with first input shaft 5, has the gap between the output shaft of first motor 3 and the cylinder core 67, i.e. the running of first motor 3 can not be subjected to the influence of cylinder core 67.
If power-transfer clutch 4 adopts traditional power-transfer clutch such as liquid clutch, then need on the adapter shaft between the rotor of box body wall, double mass flywheel 2 and first motor 3 of change speed gear box, offer oil duct, thus adopt traditional power-transfer clutch can make the oil duct design, make more complicated.And the power-transfer clutch 4 by 6 controls of hydraulic pressure release thrust bearing that adopts the utility model to provide then can reduce the difficulty that manufactures and designs of power-transfer clutch oil duct, helps cost-cutting.Simultaneously, hydraulic actuating cylinder can be fixed on the change speed gear box, thereby can not be subjected to the influence of first motor, 3 output shafts, helps mentioning the control accuracy of power-transfer clutch 4.
Further, hydraulic pressure release thrust bearing 6 also comprises cylinder seat 70, and an end of this cylinder seat 70 and cylinder body 64 and cylinder core 67 are tightly connected.The sealing mode can realize by variety of way well known in the art, as between cylinder body 64 and cylinder seat 70, forming concaveconvex structure, one end of cylinder core 67 have flange and be inserted into cylinder body 64 and cylinder seat 70 between, and cylinder body 64 and cylinder seat 70 are fixed together by screw 69.
In addition according to a kind of embodiment of the present utility model, thereby 1 needs of combustion engine outputting power powered vehicle when high-speed cruising, at this moment, power-transfer clutch 4 just needs combination, therefore, the hydraulic power source of hydraulic pressure release thrust bearing 6 such as oil pump can need not direct motor drive is set in addition and be driven by combustion engine 1.Promptly drive oil pump and rotate, and then provide hydraulic coupling for hydraulic pressure release thrust bearing 6 by combustion engine 1.
Known ground, hybrid vehicle is provided with control setup, and as vehicle-mounted ECU, each mechanism operates under the various mode of operations on car load and the automobile thereby can control.
When needs control clutch 4, control setup modulated pressure propulsion source such as electric oil pump work, thus hydraulic oil is input in the annulus 63 by hydraulic oil pipe 66, and then promotion piston 62 moves, under the effect of piston 62, release thrust bearing 61 drives power-transfer clutch 4 closures; When needs cut-off clutch 4, control setup modulated pressure source such as electric oil pump quit work, hydraulic pressure release thrust bearing 6 the oil return loop on electromagnetic valve connect, hydraulic oil in the annulus 63 flows back in hydraulic power source such as the change speed gear box by hydraulic oil pipe 66, at this moment, release thrust bearing 61 and piston 62 be return gradually, and power-transfer clutch 4 disconnects.
Hybrid electric drive system of the present utility model can be provided with different mode of operations and reasonably select according to different operating modes.
Hybrid electric drive system of the present utility model can be operated under pure electronic and two kinds of patterns of hybrid power, and promptly can to drive based on second motor 10 be electric-only mode to this hybrid electric drive system.As long as satisfying the needs of second motor 10, the electric weight in the closed-center system can operate in electric-only mode by control vehicle.
According to a kind of embodiment of the present utility model, this hybrid electric drive system following mode of operation of can working: stop mode, series model, paralleling model, electric-only mode and energy feedback pattern:
Stop mode: this moment, combustion engine 1, first motor 3 and second motor 10 of vehicle all were in run-stopping status.Power-transfer clutch 4 is in released state or bonding state can not exert an influence to vehicle.
Series model: at this moment, power-transfer clutch 4 separates, and vehicle travels under the driving of second motor 10, and combustion engine 1 drives 3 generatings of first motor simultaneously, and first motor, 3 electricity can directly be exported to second motor 10, also can flow to closed-center system.
Paralleling model: at this moment, power-transfer clutch 4 combinations, second motor 10 receives the electric energy running of closed-center systems and power is transported to diff 11 and then drive wheels 12 by output shaft 16 and rotates and travel; Simultaneously, combustion engine 1 starts, and power is transported to diff 11 and then drive wheels 12 by output shaft 16 rotates and travel.
At this moment, first motor 3 also can be used as electrical motor operation, and power is transported to diff 11 and then drive wheels 12 by output shaft 16 rotates and travel.
Electric-only mode: second motor 10 receives the electric energy of closed-center systems and power is transported to diff 11 and then drive wheels 12 by output shaft 16 and rotates and travel.At this moment, power-transfer clutch 4 separates, and the combustion engine 1 and first motor 3 are all out of service.
Energy feedback pattern: when car brakeing, second motor 10 can be accepted the mechanical energy of output shaft 16 conveyings and be converted into electrical power storage in closed-center system.
Certainly, hybrid electric drive system of the present utility model can also be operated in other pattern, and as the parking power generation mode: this moment, power-transfer clutch 4 separated, and combustion engine 1 drives 3 generatings of first motor and powers to closed-center system.
Hybrid electric drive system of the present utility model and comprise the vehicle of this drive system, owing to be provided with two input shafts and an output shaft, connect by gear pair respectively between two input shafts and the output shaft, the combustion engine and second motor are respectively by two input shaft outputting powers, thereby two shelves levels of vehicle D Drive have been formed, and then can be according to the different driving cycles of vehicle, select various mode of operations and each respective notch flexibly, so well satisfied the travel needs of vehicle under different operating modes.In addition, hybrid electric drive system with two D Drive levels of the present utility model can make that the car load low speed torque increases, starting is faster, and under high speed, can give play to the peak efficiency of combustion engine better, improved energy conversion efficiency, reduce exhaust emissions and waste of power, finally reached effects such as the anti-emission carburetor of car load, low oil consumption and kinetic energy.
Hybrid electric drive system of the present utility model and comprise the vehicle of this drive system, owing to formed two transmitting ratios by two gear pairs, only needing control second motor 10 and combustion engine 1 to work just can be so that both utilizes two transmitting ratio outputting powers respectively and need not to be provided with in addition gearshift, therefore effectively reduce the control difficulty of this hybrid electric drive system, simplified control policy, and then reduced the probability that control fault appears in this drive system, effectively improve the control quality, thereby reduced the fault rate of vehicle and car owner's cost of upkeep.
Hybrid electric drive system of the present utility model and comprise the vehicle of this drive system has been given full play to combustion engine and the performance of second motor under different operating modes, has well taken into account performance and cost, thereby has helped popularizing of motor vehicle driven by mixed power.
The above only is preferred embodiment of the present utility model; not in order to restriction the utility model; all any modifications of within spirit of the present utility model and principle, being done, be equal to and replace and improvement etc., all should be included within the protection domain of the present utility model.
Claims (10)
1. hybrid electric drive system, comprise combustion engine, first motor, the power-transfer clutch and second motor, it is characterized in that, described hybrid electric drive system also comprises the output shaft that is used for outputting power and separately to first input shaft and second input shaft of described output shaft transmitting power, form first transmitting ratio by one or more levels gear pair between first input shaft and the output shaft, form second transmitting ratio by one or more levels gear pair between second input shaft and the output shaft, described combustion engine is connected with described first motor, described first motor is connected with described first input shaft by described power-transfer clutch, and described second motor is connected with described second input shaft.
2. hybrid electric drive system as claimed in claim 1, it is characterized in that, be fixed with first gear on described first input shaft, be fixed with second gear on described second input shaft, be fixed with the 3rd gear and the 4th gear on the described output shaft, described first gear and described the 3rd gear mesh form first transmitting ratio, and described second gear and described the 4th gear mesh form second transmitting ratio.
3. hybrid electric drive system as claimed in claim 2 is characterized in that described hybrid electric drive system also comprises diff, and described diff is connected with described the 3rd gear or described the 4th gear.
4. hybrid electric drive system as claimed in claim 2 is characterized in that described hybrid electric drive system also comprises diff, also is fixed with the 5th gear on the described output shaft, and described diff is connected with described the 5th gear.
5. hybrid electric drive system as claimed in claim 1 is characterized in that, described first transmitting ratio is less than described second transmitting ratio.
6. hybrid electric drive system as claimed in claim 1 is characterized in that, the output shaft of the output shaft of described combustion engine, described first motor and the output shaft of described second motor are on the same axis.
7. hybrid electric drive system as claimed in claim 2 is characterized in that, an end of described first gear is provided with quill shaft, an end of described second input shaft by bearing installation in described quill shaft.
8. hybrid electric drive system as claimed in claim 1 is characterized in that described hybrid electric drive system also comprises double mass flywheel, and described combustion engine is connected with described first motor by described double mass flywheel.
9. hybrid electric drive system as claimed in claim 1, it is characterized in that, described power-transfer clutch comprises first friction member and second friction member that contacts or separate under the driving of hydraulic pressure release thrust bearing, described first friction member is captiveed joint with the rotor of described first motor, and described second friction member is captiveed joint with described first input shaft.
10. a vehicle is characterized in that, described vehicle comprises any described hybrid electric drive system among the claim 1-9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202133880U CN201777126U (en) | 2010-05-31 | 2010-05-31 | Hybird power drive system and vehicle comprising same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010202133880U CN201777126U (en) | 2010-05-31 | 2010-05-31 | Hybird power drive system and vehicle comprising same |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201777126U true CN201777126U (en) | 2011-03-30 |
Family
ID=43790352
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010202133880U Expired - Lifetime CN201777126U (en) | 2010-05-31 | 2010-05-31 | Hybird power drive system and vehicle comprising same |
Country Status (1)
| Country | Link |
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| CN (1) | CN201777126U (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN102259581A (en) * | 2010-05-31 | 2011-11-30 | 比亚迪股份有限公司 | Hybrid power drive system and vehicle comprising same |
| CN103072472A (en) * | 2012-12-07 | 2013-05-01 | 常州万安汽车部件科技有限公司 | Multimode dual-motor driving system and driving mode thereof |
| CN103358877A (en) * | 2012-04-10 | 2013-10-23 | 阿尔特汽车技术股份有限公司 | Power system of range extended electromobile and range extended electromobile |
| CN106274464A (en) * | 2015-05-29 | 2017-01-04 | 上海汽车集团股份有限公司 | The double-motor power system of pure electric vehicle and control method |
| CN110949114A (en) * | 2019-11-15 | 2020-04-03 | 华为技术有限公司 | Speed reducer, electric automobile's actuating system and electric automobile |
| WO2020073809A1 (en) * | 2018-10-09 | 2020-04-16 | 北京致行慕远科技有限公司 | Power device, control method for power device, and traveling apparatus |
| CN112356647A (en) * | 2020-11-10 | 2021-02-12 | 浙江吉利控股集团有限公司 | Multi-motor flexible torque centralized driving synthesis box and electric vehicle |
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2010
- 2010-05-31 CN CN2010202133880U patent/CN201777126U/en not_active Expired - Lifetime
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102259581A (en) * | 2010-05-31 | 2011-11-30 | 比亚迪股份有限公司 | Hybrid power drive system and vehicle comprising same |
| CN103358877A (en) * | 2012-04-10 | 2013-10-23 | 阿尔特汽车技术股份有限公司 | Power system of range extended electromobile and range extended electromobile |
| CN103072472A (en) * | 2012-12-07 | 2013-05-01 | 常州万安汽车部件科技有限公司 | Multimode dual-motor driving system and driving mode thereof |
| CN106274464A (en) * | 2015-05-29 | 2017-01-04 | 上海汽车集团股份有限公司 | The double-motor power system of pure electric vehicle and control method |
| WO2020073809A1 (en) * | 2018-10-09 | 2020-04-16 | 北京致行慕远科技有限公司 | Power device, control method for power device, and traveling apparatus |
| US11007858B2 (en) | 2018-10-09 | 2021-05-18 | Nine Intelligent (Changzhou) Tech Co., Ltd. | Power apparatus, control method for power apparatus, and traveling device |
| CN110949114A (en) * | 2019-11-15 | 2020-04-03 | 华为技术有限公司 | Speed reducer, electric automobile's actuating system and electric automobile |
| CN112356647A (en) * | 2020-11-10 | 2021-02-12 | 浙江吉利控股集团有限公司 | Multi-motor flexible torque centralized driving synthesis box and electric vehicle |
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Legal Events
| Date | Code | Title | Description |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CX01 | Expiry of patent term | ||
| CX01 | Expiry of patent term |
Granted publication date: 20110330 |