CN205417162U - Bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star - Google Patents
Bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star Download PDFInfo
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- CN205417162U CN205417162U CN201620197733.3U CN201620197733U CN205417162U CN 205417162 U CN205417162 U CN 205417162U CN 201620197733 U CN201620197733 U CN 201620197733U CN 205417162 U CN205417162 U CN 205417162U
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Abstract
The utility model provides a bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star relates to car technical field, including preceding planet row, back planet row, clutch, stopper, motor system, main reducer and box, combination and the separation through control clutch and stopper can realize different mode's switching, climbing capability in the time of can improving vehicle low -speed and go, transmission efficiency when the improvement vehicle is gone at high speed, reduce cost.
Description
Technical field
This utility model relates to automobile technical field, particularly to a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case.
Background technology
Series-Parallel HEV change speed gear box, as dynamical system critical piece, rotational speed regulation to be possessed, basic functions such as increasing torsion of slowing down, also to realize the power dividing of each power source.At present, typical power dividing version is the THS system of Toyota and general AHS system.Wherein, the single mode power dividing form that THS system is single planetary row of Toyota, there is the advantage that simple in construction is easily controllable, but, THS system is bigger to the dependency of motor, the motor that mesh power bigger grade is generally required for meeting the demand of dynamic property, thus there is the problem that hardware utilization is relatively low, and meanwhile, the phenomenon that when THS system there is also low speed, when climbing capacity difference and high speed, transmission efficiency is relatively low, thus it is used for dilly, less for cargo vehicle and passenger car application prospect.The general bimodulus power dividing pattern that AHS system is double planet wheel rows of mixing or three planet rows, it is possible to make transmission efficiency higher in whole rotating speed interval, but AHS system needs the switching of multiple clutch implementation patterns, thus system authority is complicated, controls difficulty.
At present, the existing patent about Series-Parallel HEV dual mode system the most only introduces power dividing path and operation principle, is formed without normalized structure, simultaneously, such patent the most only considers power dividing part, does not put it to be designed in whole transmission system.If Chinese patent publication No. is CN104960407A; date of publication is 2014-10-07; disclose a kind of integrated form planetary gear oil electricity series-parallel connection bimodulus hybrid power system; this system only considers that design power shunting part is carried out in the power dividing path of each power source; not according to each design of part of assembly relation appropriate design, the most do not carry out the global design of change speed gear box.A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case achieves the structuring of dual mode system, in this field not yet related invention.
Summary of the invention
This utility model be for overcoming that prior art hardware utilization is low, low speed time climbing capacity difference and transmission efficiency is low during high speed problem, it is provided that a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case.
For solving above-mentioned technical problem; this utility model adopts the following technical scheme that realization: described a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case, including front planet row, rear planet row, clutch, brake, electric system, main reducing gear and casing.
Described front planet package includes transmission input shaft 1, public gear ring 5, front-seat planetary gear 6, front-seat planetary gear support shaft 7, front planet row subframe 8, front-seat sun wheel shaft 21 and front-seat planet carrier 33, described transmission input shaft 1 is structure as a whole with front-seat planet carrier 33, the left end of transmission input shaft 1 passes through roller bearings in front casing 2, the right-hand member of transmission input shaft 1 is provided with axle journal, is supported in the blind hole of front-seat sun wheel shaft 21 by sliding bearing；Described public gear ring 5 is by sliding bearing empty set on transmission input shaft 1, and public gear ring 5 left end and motor 4 output shaft are connected by spline；Described front-seat planetary gear 6 is helical gears, and described front-seat planetary gear support shaft 7 is solid optical axis, and front-seat planetary gear 6 passes through sliding bearing empty set in front-seat planetary gear support shaft 7；Described front planet row subframe 8 is circular ring structure, along the circumferential direction has some counter sinks, is used for installing front-seat planetary gear support shaft 7；Front-seat planetary gear support shaft 7 is arranged between front-seat planet carrier 33 and front planet row subframe 8；Described front-seat sun wheel shaft 21 is gear shaft, left end is front-seat sun gear, and it is provided with blind hole, front-seat sun wheel shaft 21 right-hand member and No. two motor 22 output shafts are connected by spline, the sun gear of front-seat sun wheel shaft 21 often engages with front-seat planetary gear 6, and front-seat planetary gear 6 often engages with public gear ring 5 left end gear ring.
Described rear planet row includes public gear ring 5, heel row planetary gear 9, heel row planetary gear support shaft 10, heel row planet carrier 11, heel row sun wheel shaft 12, final drive input gear 31 and rear planet row subframe 32, described heel row planetary gear 9 is helical gears, described heel row planetary gear support shaft 10 is solid optical axis, and heel row planetary gear 9 passes through sliding bearing empty set in heel row planetary gear support shaft 10；Described heel row planet carrier 11 is structure as a whole with final drive input gear 31；Described heel row sun wheel shaft 12 is hollow gear shaft, and by sliding bearing empty set in front-seat sun wheel shaft 21, heel row sun wheel shaft 12 left end is heel row sun gear, and middle part is the optical axis for supporting final drive input gear 31, and right-hand member has external splines；Described rear planet row subframe 32 is circular ring structure, along the circumferential direction has some counter sinks, is used for installing heel row planetary gear support shaft 10；Heel row planetary gear support shaft 10 is arranged between heel row planet carrier 11 and rear planet row subframe 32；The sun gear of heel row sun wheel shaft 12 often engages with heel row planetary gear 9, and heel row planetary gear 9 often engages with the right-hand member gear ring of public gear ring 5.
Described clutch includes clutch rotating hub 13, clutch plunger 14, clutch friction plate 15, clutch steel disc 16, endless drive part 17, clutch spring 18, clutch spring holder 19 and clutch driven member 20, described clutch rotating hub 13 is cup-shaped structure, clutch rotating hub 13 is enclosed within heel row sun wheel shaft 12 by spline fitted, and the inside outer wall of clutch rotating hub 13 has the internal spline that the external splines with clutch steel disc 16 coordinates；Described clutch plunger 14 is disc structure, and outer wall and inwall have the cannelure of mounting O-shaped rings, and clutch plunger 14 is installed in the plunger shaft of clutch rotating hub 13；Described clutch friction plate 15 is loop configuration, and inner side has internal spline, and described clutch steel disc 16 is loop configuration, and outside has external splines；Clutch steel disc 16 is installed in clutch rotating hub 13 by spline fitted, and clutch friction plate 15 is installed on clutch driven member 20 by spline fitted, clutch steel disc 16 and the alternate installation of clutch friction plate 15；The external splines that the internal spline with clutch rotating hub 13 coordinates is had outside described endless drive part 17, the external splines of endless drive part 17 coordinates with the internal spline of clutch rotating hub 13, and it is spacing by snap ring, the external splines that the internal spline with brake bush 28 coordinates is had, with brake bush 28 spline fitted inside endless drive part 17 inside endless drive part 17；Described clutch spring 18 is helical spring, described clutch spring holder 19 is loop configuration, clutch spring holder 19 is provided with the boss of fixed clutch spring 18, clutch spring 18 is installed on the boss of clutch spring holder 19, and clutch spring holder 19 is fixed in clutch rotating hub 13 by snap ring；Described clutch driven member 20 is disc structure, and outside has the external splines that the internal spline with clutch friction plate 15 coordinates, and clutch driven member 20 is enclosed within front-seat sun wheel shaft 21 by spline fitted.
Described brake includes brake locks hub 25, brake plunger 26, brake steel disc 27, brake bush 28, brake spring 29, brake spring seat 30, described brake locks hub 25 is cup-shaped structure, brake locks hub 25 inside outer wall has the internal spline that the external splines with brake steel disc 27 coordinates, and brake locks hub 25 outer exterior wall has the external splines of the internal spline tabling with rear box 24；Brake locks hub 25 is fixed in rear box 24 by spline fitted, and described brake plunger 26 is disc structure, and outer wall and inwall have the cannelure of mounting O-shaped rings, and brake plunger 26 is installed in the plunger shaft of brake locks hub 25；Described brake steel disc 27 is loop configuration, and outside has external splines；Described brake bush 28 is loop configuration, and inner side has internal spline；Brake steel disc 27 is installed on brake locks hub 25 by spline fitted, and brake bush 28 is installed on endless drive part 17 by spline fitted, brake steel disc 27 and the alternate installation of brake bush 28.Described brake spring 29 is helical spring；Described brake spring seat 30 is loop configuration, and brake spring seat 30 is provided with the boss of fixing brake spring 29, and brake spring 29 is installed on the boss of brake spring seat 30, and brake spring seat 30 is fixed on brake locks hub 25 by snap ring.
Described electric system includes a motor 4 and No. two motors 22, and a described motor 4 is permagnetic synchronous motor, is fixed on middle casing 3, and the output shaft of a motor 4 is hollow axle, and top has internal spline, matches with the external splines of public gear ring 5 left end；Described No. two motors 22 are permagnetic synchronous motor, are fixed on rear box 24, are matched with front-seat sun wheel shaft 21 by spline in top.
Described main reducing gear includes final drive input gear 31, output shaft of gear-box 34 and main reducing gear output gear 35, described output shaft of gear-box 34 has the keyway coordinated with main reducing gear output gear 35, main reducing gear output gear 35 is coordinated with output shaft of gear-box 34 by flat key, and output shaft of gear-box 34 is installed on middle casing 3 and rear box 24 by rolling bearing；Final drive input gear 31 often engages with main reducing gear output gear 35.
Described casing mainly includes that front casing 2, middle casing 3, rear box 24 and end cap 23, front casing 2 are connected with middle casing 3 by bolt, and middle casing 3 is connected with rear box 24 by bolt, and is positioned by alignment pin, and rear box 24 is connected with end cap 23 by bolt.
Described a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case is divided into pure electronic, electronic infinite variable speed, three kinds of mode of operations of regenerative braking, and wherein electronic infinite variable speed pattern is divided into fast mode and low-speed mode according to the combination of Clutch and brake with separating.
This utility model compared with prior art, has the beneficial effect that:
A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case the most described in the utility model is by the combination of the separation of clutch with brake; open low-speed mode; locking heel row sun wheel shaft; after now, planet row has deceleration increasing torsion effect, it is possible to increase climbing capacity during low vehicle speeds.
A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case the most described in the utility model is separated with brake by the combination of clutch; open fast mode; together with front row sun wheel shaft is affixed to heel row sun wheel shaft; shorten power transfer path, it is possible to increase transmission efficiency during high vehicle speeds.
A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case the most described in the utility model has high speed and two kinds of mode of operations of low speed; compared with single mode hybrid electric vehicle gearshift case; there is under low speed more big speed ratio; there is under Gao Su higher transmission efficiency; thus the relatively small motor of power grade can be used; improve hardware utilization, reduce cost.
Accompanying drawing explanation
The utility model is described in further detail below in conjunction with the accompanying drawings:
Fig. 1 is the sectional view on a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case front view described in the utility model；
Fig. 2 is the partial view of double planet wheel rows of mixing structure in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Fig. 3 is the partial view of Clutch and brake structure in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Fig. 4 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case structure principle chart described in the utility model；
Fig. 5 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model structure principle chart under electric-only mode with braking mode；
Fig. 6 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model structure principle chart in the low-speed mode；
Fig. 7 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model structure principle chart in high speed mode.
Fig. 8 is the axonometric drawing of clutch rotating hub in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Fig. 9 is the axonometric drawing of clutch friction plate in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Figure 10 is the axonometric drawing of clutch steel disc in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Figure 11 is the axonometric drawing of annular driving member in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
Figure 12 is the axonometric drawing of brake locks hub in a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case described in the utility model；
nullIn figure: 1. transmission input shaft，2. casing before，3. casing in，4. a motor，The most public gear ring，6. front-seat planetary gear，7. front-seat planetary gear support shaft，8. planet row subframe before，9. heel row planetary gear，10. heel row planetary gear support shaft，11. heel row planet carriers，12. heel row sun wheel shaft，13. clutch rotating hub，14. clutch plungers，15. clutch friction plates，16. clutch steel discs，17. endless drive parts，18. clutch springs，19. clutch spring holders，20. clutch driven members，21. front-seat sun wheel shaft，22. No. two motors，23. end caps，24. rear box，25. brake locks hubs，26. brake plungers，27. brake steel discs，28. brake bush，29. brake springs，30. brake spring seats，31. final drive input gear，Planet row subframe after 32.，33. front-seat planet carriers，34. output shaft of gear-box，35. main reducing gear output gears，36. electromotors，A. brake，B. clutch.
Detailed description of the invention
The utility model is described in further detail below in conjunction with the accompanying drawings:
Refering to Fig. 1, Fig. 4; this utility model provides a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case, and described a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case mainly includes front planet row, rear planet row, clutch, brake, electric system, main reducing gear and casing.
Refering to Fig. 1, Fig. 2, Fig. 4, described front planet package has included transmission input shaft 1, public gear ring 5, front-seat planetary gear 6, front-seat planetary gear support shaft 7, front planet row subframe 8, front-seat sun wheel shaft 21 and front-seat planet carrier 33.
Refering to Fig. 1, Fig. 2, Fig. 4, described transmission input shaft 1 is multidiameter, is structure as a whole with front-seat planet carrier 33, and left end has external splines for transmission from the power of electromotor 36, and right-hand member is provided with axle journal, and inside is provided with oil leab；The described public gear ring 5 i.e. gear ring of front planet row is made of one structure with the gear ring of rear planet row, and left end has external splines for transmitting the power from a motor 4；Described front-seat planetary gear 6 is cylindrical helical gear structural member；Described front-seat planetary gear support shaft 7 is solid optical axis；Described front planet row subframe 8 is circular ring structure, along the circumferential direction has some counter sinks, is used for installing front-seat planetary gear support shaft 7；Described front-seat sun wheel shaft 21 is gear shaft, and left end is front-seat sun gear, and is provided with blind hole, and right-hand member has external splines for transmission from the power of No. two motors 22, and inside is provided with oil leab.
Refering to Fig. 1, Fig. 2, Fig. 4, transmission input shaft 1 left end is by roller bearings in front casing 2, and right-hand member is supported in the blind hole of front-seat sun wheel shaft 21 by sliding bearing；Front-seat planetary gear 6 passes through sliding bearing empty set in front-seat planetary gear support shaft 7；Front-seat planetary gear support shaft 7 is installed between front-seat planet carrier 33 and front planet row subframe 8；Public gear ring 5 by sliding bearing empty set on transmission input shaft 1, and by the internal spline cooperation of the external splines of left end with motor 4 output shaft；Front-seat sun wheel shaft 21 is coordinated by the external splines of right-hand member and the internal spline of No. two motor 22 output shafts；The sun gear of front-seat sun wheel shaft 21 often engages with front-seat planetary gear 6, and front-seat planetary gear 6 often engages with the gear ring of public gear ring 5 left end.
Refering to Fig. 1, Fig. 2, Fig. 4, described rear planet row includes public gear ring 5, heel row planetary gear 9, heel row planetary gear support shaft 10, heel row planet carrier 11, heel row sun wheel shaft 12, final drive input gear 31 and rear planet row subframe 32.
Refering to Fig. 1, Fig. 2, Fig. 4, described heel row planetary gear 9 is cylindrical helical gear structure；Described heel row planetary gear support shaft 10 is solid optical axis；Described heel row planet carrier 11 is structure as a whole with final drive input gear 31；Described heel row sun wheel shaft 12 is hollow gear shaft, and left end is heel row sun gear, and middle part is the optical axis for supporting final drive input gear 31, and right-hand member has external splines；Described rear planet row subframe 32 is circular ring structure, along the circumferential direction has some counter sinks, is used for installing heel row planetary gear support shaft 10.
Refering to Fig. 1, Fig. 2, Fig. 4, heel row sun wheel shaft 12 passes through sliding bearing empty set in front-seat sun wheel shaft 21；Final drive input gear 31 is supported on the optical axis portion of heel row sun wheel shaft 12；Heel row planetary gear 9 passes through sliding bearing empty set in heel row planetary gear support shaft 10；Heel row planetary gear support shaft 10 is arranged between heel row planet carrier 11 and rear planet row subframe 32；The sun gear of heel row sun wheel shaft 12 often engages with heel row planetary gear 9, and heel row planetary gear 9 often engages with the right-hand member gear ring of public gear ring 5.
Refering to Fig. 1, Fig. 3, Fig. 4, described clutch includes clutch rotating hub 13, clutch plunger 14, clutch friction plate 15, clutch steel disc 16, endless drive part 17, clutch spring 18, clutch spring holder 19, clutch driven member 20.
Refering to Fig. 1, Fig. 3, Fig. 4, Fig. 8, Fig. 9, Figure 10, Figure 11, described clutch rotating hub 13 is cup-shaped structure, inner wall has the internal spline that the external splines with heel row sun wheel shaft 12 matches, and inside outer wall has the internal spline that the external splines with clutch steel disc 16 coordinates；Described clutch plunger 14 is disc structure, and outer wall and inwall have the cannelure of mounting O-shaped rings；Described clutch friction plate 15 is loop configuration, and inner side has internal spline；Described clutch steel disc 16 is loop configuration, and outside has external splines；Described endless drive part 17 is loop configuration, and outside has the external splines that the internal spline with clutch rotating hub 13 coordinates, and inner side has the external splines that the internal spline with brake bush 28 coordinates；Described clutch spring 18 is helical spring；Described clutch spring holder 19 is loop configuration, and clutch spring holder 19 is provided with the boss of fixed clutch spring 18；Described clutch driven member 20 is disc structure, and outside has the external splines that the internal spline with clutch friction plate 15 coordinates, and inner side has the internal spline that the external splines with front-seat sun wheel shaft 21 coordinates.
Refering to Fig. 1, Fig. 3, Fig. 4, clutch rotating hub 13 is enclosed within heel row sun wheel shaft 12 by spline fitted；Clutch plunger 14 is installed in the plunger shaft of clutch rotating hub 13；Clutch spring 18 is installed on the boss of clutch spring holder 19, and clutch spring holder 19 is fixed in clutch rotating hub 13 by snap ring；Clutch steel disc 16 is installed in clutch rotating hub 13 by spline fitted, and clutch friction plate 15 is installed on clutch driven member 20 by spline fitted, clutch steel disc 16 and the alternate installation of clutch friction plate 15；Clutch driven member 20 is enclosed within front-seat sun wheel shaft 21 by spline fitted；The external splines of endless drive part 17 coordinates with the internal spline of clutch rotating hub 13, and spacing by snap ring.
Refering to Fig. 1, Fig. 3, Fig. 4, described brake includes brake locks hub 25, brake plunger 26, brake steel disc 27, brake bush 28, brake spring 29, brake spring seat 30.
Refering to Fig. 1, Fig. 3, Fig. 4, Figure 12, described brake locks hub is cup-shaped structure, and inside outer wall has the internal spline that the external splines with brake steel disc 27 coordinates, and outer exterior wall has the external splines of the internal spline tabling with rear box 24；Described brake plunger 26 is disc structure, and outer wall and inwall have the cannelure of mounting O-shaped rings；Described brake steel disc 27 is loop configuration, and outside has external splines；Described brake bush 28 is loop configuration, and inner side has internal spline；Described brake spring 29 is helical spring；Described brake spring seat 30 is loop configuration, and is provided with the boss of fixing brake spring 29.
Refering to Fig. 1, Fig. 3, Fig. 4, brake locks hub 25 is fixed in rear box 24 by spline fitted；Brake plunger 26 is installed in the plunger shaft of brake locks hub 25；Brake spring 29 is installed on the boss of brake spring seat 30, and brake spring seat 30 is fixed on brake locks hub 25 by snap ring；Brake steel disc 27 is installed on brake locks hub 25 by spline fitted, and brake bush 28 is installed on endless drive part 17 by spline fitted, brake steel disc 27 and the alternate installation of brake bush 28.
Refering to Fig. 1, described electric system includes 4, No. two motors 22 of a motor.
Refering to Fig. 1, a described motor 4 is permasyn morot, and motor output shaft is hollow axle, and motor output shaft top has internal spline；Described No. two motors 22 are permasyn morot, and motor output shaft top has internal spline.
Refering to Fig. 1, a motor 4 is fixed on middle casing 3, and its output shaft is matched with public gear ring 5 by spline；No. two motors 22 are fixed on rear box 24, and its output shaft is matched with front-seat sun wheel shaft 21 by spline.
Refering to Fig. 1, described main reducing gear includes final drive input gear 31, output shaft of gear-box 34 and main reducing gear output gear 35.
Refering to Fig. 1, described output shaft of gear-box 34 is multidiameter, and axle has the keyway coordinated with main reducing gear output gear 35；Described main reducing gear output gear 35 is disc type spur gear.
Refering to Fig. 1, output shaft of gear-box 34 is installed on middle casing 3 and rear box 24 by rolling bearing；Main reducing gear output gear 35 is coordinated with output shaft of gear-box 34 by flat key；Final drive input gear 31 often engages with main reducing gear output gear 35.
Refering to Fig. 1, described casing mainly includes front casing 2, middle casing 3, end cap 23, rear box 24.
Refering to Fig. 1, described front casing 2 is shell construction, along the circumferential direction has unthreaded hole；Described middle casing 3 is shell construction, and two ends the most all have screwed hole；Described end cap 23 is disk-shaped structure, along the circumferential direction has unthreaded hole；Described rear box 24 is shell construction, and left end has unthreaded hole, and right-hand member has screwed hole.
Refering to Fig. 1, front casing 2 is connected with middle casing 3 by bolt；Middle casing 3 is connected with rear box 24 by bolt, and is positioned by alignment pin；Rear box 24 is connected with end cap 23 by bolt.
Operation principle divides with mode of operation
Refering to Fig. 1, Fig. 4, described a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case has three power inputs, is 36, motor 4 of electromotor and No. two motors 22 respectively；The power of electromotor 34 is inputted by transmission input shaft 1, and the power of a motor 4 is inputted by public gear ring 5, and the power of No. two motors 22 is inputted by front-seat sun wheel shaft 21.
1, electric-only mode
Refering to Fig. 1, Fig. 4, Fig. 5, electric-only mode is mainly used in starting vehicle and low cruise.Under electric-only mode, clutch plunger 14 is positioned on the left of clutch rotating hub 13, there is gap between clutch friction plate 15 and clutch steel disc 16, and clutch B is in released state；Brake plunger 26 moves to left, and is pressed together with brake steel disc 27 by brake bush 28, and brake A is in engagement state, brake locks hub 25 via endless drive part 17, clutch rotating hub 13 by heel row sun wheel shaft 12 locking.Now, only No. one motor 4 works, and power is inputted by public gear ring 5, is finally exported by heel row planet carrier 11 through heel row planetary gear 9.Now, transmission input shaft 1 and front-seat sun wheel shaft 21 are not the most done and are controlled, unpowered input and output.
2, electronic infinite variable speed pattern
Refering to Fig. 1, Fig. 4, Fig. 6, Fig. 7, electronic infinite variable speed pattern can be divided into low-speed mode and fast mode according to the combination situation of brake A Yu clutch B.
Low-speed mode
Refering to Fig. 1, Fig. 4, Fig. 6, under low-speed mode, clutch B is in released state, and brake A is in bonding state, heel row sun wheel shaft 12 locking.Now, the power of electromotor 36 is inputted by transmission input shaft 1, and No. two motors 22 are connected with front-seat sun wheel shaft 21, and for regulating the operating point of electromotor 36, power is finally exported by heel row planet carrier 11.In the case of being short of power, a motor 4 carries out certain power compensation by public gear ring 5.
Fast mode
Refering to Fig. 1, Fig. 4, Fig. 7, under fast mode, brake plunger 26 is positioned at the right survey of brake locks hub 25, gap is there is between brake bush 28 and brake steel disc 27, brake A is in released state, and clutch plunger 14 moves to right, and is pressed together with clutch steel disc 16 by clutch friction plate 15, clutch B is in bonding state, and heel row sun wheel shaft 12 is connected by clutch rotating hub 13, clutch driven member 20 with front-seat sun wheel shaft 21.The power of electromotor 36 is inputted by transmission input shaft 1, is finally exported power by heel row planet carrier 11 through public gear ring 5.No. two motors 22 are for regulating the operating point of electromotor 36, and a motor 4 carries out certain power compensation.
3, braking mode
Refering to Fig. 1, Fig. 4, Fig. 5, under braking mode, clutch B is in released state, and brake A is in bonding state, heel row sun wheel shaft 12 locking, and in vehicle travel process, wheel drives public gear ring 5 to rotate by heel row planet carrier 11.In braking procedure, the torque capacity that the braking moment of vehicle demand can provide if less than a motor 4, brake force is all provided by a motor 4, is electric energy by changes mechanical energy, and is stored in battery.If the torque capacity that the braking moment of vehicle demand can provide if greater than a motor 4, a part of brake force is provided by a motor 4, is electric energy by changes mechanical energy, is stored in battery, and another part brake force is provided by traditional mechanical brake.
Claims (1)
1. a series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case, including front planet row, rear planet row, clutch, brake, electric system, main reducing gear and casing, it is characterised in that:
Described front planet package includes transmission input shaft (1), public gear ring (5), front-seat planetary gear (6), front-seat planetary gear support shaft (7), front planet row subframe (8), front-seat sun wheel shaft (21) and front-seat planet carrier (33), described transmission input shaft (1) is structure as a whole with front-seat planet carrier (33), the left end of transmission input shaft (1) passes through roller bearings in front casing (2), the right-hand member of transmission input shaft (1) is provided with axle journal, it is supported in the blind hole of front-seat sun wheel shaft (21) by sliding bearing；Described public gear ring (5) is by sliding bearing empty set on transmission input shaft (1), and public gear ring (5) left end and motor (4) output shaft are connected by spline；Described front-seat planetary gear (6) is helical gears, and described front-seat planetary gear support shaft (7) is solid optical axis, and front-seat planetary gear (6) passes through sliding bearing empty set on front-seat planetary gear support shaft (7)；Described front planet row subframe (8) is circular ring structure, along the circumferential direction has some counter sinks, is used for installing front-seat planetary gear support shaft (7)；Front-seat planetary gear support shaft (7) is arranged between front-seat planet carrier (33) and front planet row subframe (8)；Described front-seat sun wheel shaft (21) is gear shaft, left end is front-seat sun gear, and it is provided with blind hole, front-seat sun wheel shaft (21) right-hand member and No. two motor (22) output shafts are connected by spline, the sun gear of front-seat sun wheel shaft (21) often engages with front-seat planetary gear (6), and front-seat planetary gear (6) is often engaged with public gear ring (5) left end gear ring；
Described rear planet row includes public gear ring (5), heel row planetary gear (9), heel row planetary gear support shaft (10), heel row planet carrier (11), heel row sun wheel shaft (12), final drive input gear (31) and rear planet row subframe (32), described heel row planetary gear (9) is helical gears, described heel row planetary gear support shaft (10) is solid optical axis, and heel row planetary gear (9) passes through sliding bearing empty set in heel row planetary gear support shaft (10)；Described heel row planet carrier (11) is structure as a whole with final drive input gear (31)；Described heel row sun wheel shaft (12) is hollow gear shaft, by sliding bearing empty set on front-seat sun wheel shaft (21), heel row sun wheel shaft (12) left end is heel row sun gear, middle part is for be used for supporting the optical axis of final drive input gear (31), and right-hand member has external splines；Described rear planet row subframe (32) is circular ring structure, along the circumferential direction has some counter sinks, is used for installing heel row planetary gear support shaft (10)；Heel row planetary gear support shaft (10) is arranged between heel row planet carrier (11) and rear planet row subframe (32)；The sun gear of heel row sun wheel shaft (12) often engages with heel row planetary gear (9), and heel row planetary gear (9) often engages with the right-hand member gear ring of public gear ring (5)；
Described clutch includes clutch rotating hub (13), clutch plunger (14), clutch friction plate (15), clutch steel disc (16), endless drive part (17), clutch spring (18), clutch spring holder (19) and clutch driven member (20), described clutch rotating hub (13) is cup-shaped structure, clutch rotating hub (13) is enclosed within heel row sun wheel shaft (12) by spline fitted, the inside outer wall of clutch rotating hub (13) has the internal spline that the external splines with clutch steel disc (16) coordinates；Described clutch plunger (14) is disc structure, and outer wall and inwall have the cannelure of mounting O-shaped rings, and clutch plunger (14) is installed in the plunger shaft of clutch rotating hub (13)；Described clutch friction plate (15) is loop configuration, and inner side has internal spline, and described clutch steel disc (16) is loop configuration, and outside has external splines；Clutch steel disc (16) is installed in clutch rotating hub (13) by spline fitted, clutch friction plate (15) is installed on clutch driven member (20) by spline fitted, clutch steel disc (16) and clutch friction plate (15) alternate installation；Described endless drive part (17) outside has the external splines that the internal spline with clutch rotating hub (13) coordinates, the external splines of endless drive part (17) coordinates with the internal spline of clutch rotating hub (13), and it is spacing by snap ring, endless drive part (17) inner side has the external splines that the internal spline with brake bush (28) coordinates, endless drive part (17) inner side and brake bush (28) spline fitted；Described clutch spring (18) is helical spring, described clutch spring holder (19) is loop configuration, clutch spring holder (19) is provided with the boss of fixed clutch spring (18), clutch spring (18) is installed on the boss of clutch spring holder (19), and clutch spring holder (19) is fixed in clutch rotating hub (13) by snap ring；Described clutch driven member (20) is disc structure, outside has the external splines that the internal spline with clutch friction plate (15) coordinates, and clutch driven member (20) is enclosed within front-seat sun wheel shaft (21) by spline fitted；
Described brake includes brake locks hub (25), brake plunger (26), brake steel disc (27), brake bush (28), brake spring (29), brake spring seat (30), described brake locks hub (25) is cup-shaped structure, brake locks hub (25) inside outer wall has the internal spline that the external splines with brake steel disc (27) coordinates, and brake locks hub (25) outer exterior wall has the external splines of the internal spline tabling with rear box (24)；Brake locks hub (25) is fixed in rear box (24) by spline fitted, described brake plunger (26) is disc structure, outer wall and inwall have the cannelure of mounting O-shaped rings, and brake plunger (26) is installed in the plunger shaft of brake locks hub (25)；Described brake steel disc (27) is loop configuration, and outside has external splines；Described brake bush (28) is loop configuration, and inner side has internal spline；Brake steel disc (27) is installed on brake locks hub (25) by spline fitted, brake bush (28) is installed on endless drive part (17) by spline fitted, brake steel disc (27) and brake bush (28) alternate installation, described brake spring (29) is helical spring；Described brake spring seat (30) is loop configuration, brake spring seat (30) is provided with the boss of fixing brake spring (29), brake spring (29) is installed on the boss of brake spring seat (30), and brake spring seat (30) is fixed on brake locks hub (25) by snap ring；
Described electric system includes a motor (4) and No. two motors (22), a described motor (4) is permagnetic synchronous motor, it is fixed on casing (3), the output shaft of a number motor (4) is hollow axle, top has internal spline, matches with the external splines of public gear ring (5) left end；No. two described motors (22) are permagnetic synchronous motor, are fixed on rear box (24), are matched with front-seat sun wheel shaft (21) by spline in top；
Described main reducing gear includes final drive input gear (31), output shaft of gear-box (34) and main reducing gear output gear (35), described output shaft of gear-box (34) has the keyway coordinated with main reducing gear output gear (35), main reducing gear output gear (35) is coordinated with output shaft of gear-box (34) by flat key, and output shaft of gear-box (34) is installed on middle casing (3) and rear box (24) by rolling bearing；Final drive input gear (31) often engages with main reducing gear output gear (35)；
Described casing mainly includes front casing (2), middle casing (3), rear box (24) and end cap (23), front casing (2) is connected with middle casing (3) by bolt, middle casing (3) is connected with rear box (24) by bolt, and positioned by alignment pin, rear box (24) is connected with end cap (23) by bolt.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620197733.3U CN205417162U (en) | 2016-03-15 | 2016-03-15 | Bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620197733.3U CN205417162U (en) | 2016-03-15 | 2016-03-15 | Bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star |
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| CN205417162U true CN205417162U (en) | 2016-08-03 |
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|---|---|---|---|
| CN201620197733.3U Withdrawn - After Issue CN205417162U (en) | 2016-03-15 | 2016-03-15 | Bimodulus hybrid vehicle gearbox is arranged to series -parallel connection formula double row star |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105691195A (en) * | 2016-03-15 | 2016-06-22 | 吉林大学 | Series-parallel double-planet-row two-mode hybrid electric automobile gearbox |
| CN106864246A (en) * | 2017-01-17 | 2017-06-20 | 江苏大学 | A kind of hybrid power vehicle double row planetary gear arranges formula power coupling mechanism and control method |
| CN107650666A (en) * | 2017-08-31 | 2018-02-02 | 上海众联能创新能源科技股份有限公司 | The electric parallel-serial hybrid power system of planetary gear type oil |
| CN108180281A (en) * | 2018-02-27 | 2018-06-19 | 徐州徐工基础工程机械有限公司 | A kind of split type planet carrier used in rotary digging drill power head torque structure |
-
2016
- 2016-03-15 CN CN201620197733.3U patent/CN205417162U/en not_active Withdrawn - After Issue
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105691195A (en) * | 2016-03-15 | 2016-06-22 | 吉林大学 | Series-parallel double-planet-row two-mode hybrid electric automobile gearbox |
| CN105691195B (en) * | 2016-03-15 | 2017-10-31 | 吉林大学 | A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case |
| CN106864246A (en) * | 2017-01-17 | 2017-06-20 | 江苏大学 | A kind of hybrid power vehicle double row planetary gear arranges formula power coupling mechanism and control method |
| CN107650666A (en) * | 2017-08-31 | 2018-02-02 | 上海众联能创新能源科技股份有限公司 | The electric parallel-serial hybrid power system of planetary gear type oil |
| CN108180281A (en) * | 2018-02-27 | 2018-06-19 | 徐州徐工基础工程机械有限公司 | A kind of split type planet carrier used in rotary digging drill power head torque structure |
| CN108180281B (en) * | 2018-02-27 | 2024-03-08 | 徐州徐工基础工程机械有限公司 | Split type planet carrier adopted in torque increasing structure of power head of rotary drilling rig |
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Granted publication date: 20160803 Effective date of abandoning: 20171031 |
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