CN105691195A - Series-parallel double-planet-row two-mode hybrid electric automobile gearbox - Google Patents
Series-parallel double-planet-row two-mode hybrid electric automobile gearbox Download PDFInfo
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- CN105691195A CN105691195A CN201610146230.8A CN201610146230A CN105691195A CN 105691195 A CN105691195 A CN 105691195A CN 201610146230 A CN201610146230 A CN 201610146230A CN 105691195 A CN105691195 A CN 105691195A
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- Prior art keywords
- clutch
- gear
- brake
- seat
- planetary gear
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K17/00—Arrangement or mounting of transmissions in vehicles
- B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
- B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
- B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/22—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs
- B60K6/36—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings
- B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
- B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
- B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
- B60K6/543—Transmission for changing ratio the transmission being a continuously variable transmission
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
- Hybrid Electric Vehicles (AREA)
Abstract
The invention provides a series-parallel double-planet-row two-mode hybrid electric automobile gearbox and relates to the technical field of automobiles. The gearbox comprises a front planet row, a rear planet row, a clutch, a brake, a motor system, a main reducer and a box body. Switching of different working modes is realized by controlling engagement and disengagement of the clutch and the brake. The grade ability of the automobiles can be improved during low-speed running. The transmission efficiency of the automobiles can be improved during high-speed running. The cost is lowered.
Description
Technical field
The present invention 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, not only to possess the basic function such as rotational speed regulation, deceleration increasing torsion, 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, demand for meeting dynamic property generally requires the motor that mesh power bigger grade, thus there is the problem that hardware utilization is relatively low, meanwhile, THS system there is also the phenomenon that when climbing capacity difference and high speed during low 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 only introduces power dividing path and operation principle mostly, it does not have form normalized structure, simultaneously, such patent only considers power dividing part mostly, it does not have puts it in whole transmission system and is designed。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, also without the global design carrying out 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
The present invention 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; the present invention 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。
Transmission input shaft 1, public gear ring 5, front-seat planetary gear 6, front-seat planetary gear support axle 7, front planet row subframe 8, front-seat sun wheel shaft 21 and front-seat planet carrier 33 are drawn together in described front planet package, 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 it is solid optical axis that described front-seat planetary gear supports axle 7, and front-seat planetary gear 6 is supported on axle 7 at front-seat planetary gear by sliding bearing empty set；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 and supports axle 7；Front-seat planetary gear supports axle 7 and 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 axle 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, it is solid optical axis that described heel row planetary gear supports axle 10, and heel row planetary gear 9 is supported on axle 10 at heel row planetary gear by sliding bearing empty set；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 and supports axle 10；Heel row planetary gear supports axle 10 and 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 front casing 2, middle casing 3, rear box 24 and end cap 23, and front casing 2 is 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。
The present invention compared with prior art, has the beneficial effect that:
1. a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case of the present invention 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。
2. a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case of the present invention passes through the combination of clutch and separating of brake; 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。
3. a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case of the present invention 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; under at a high speed, there is higher transmission efficiency; thus the relatively small motor of power grade can be adopted; improve hardware utilization, reduce cost。
Accompanying drawing explanation
Below in conjunction with accompanying drawing, the invention will be further described:
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 of the present invention；
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 of the present invention；
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 of the present invention；
Fig. 4 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case structure principle chart of the present invention；
Fig. 5 is a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case of the present invention 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 of the present invention 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 of the present invention 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 of the present invention；
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 of the present invention；
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 of the present invention；
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 of the present invention；
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 of the present invention；
In figure: 1. transmission input shaft, 2. casing before, 3. casing in, 4. a motor, 5. public gear ring, 6. front-seat planetary gear, 7. front-seat planetary gear supports axle, 8. planet row subframe before, 9. heel row planetary gear, 10. heel row planetary gear supports axle, 11. heel row planet carrier, 12. heel row sun wheel shaft, 13. clutch rotating hub, 14. clutch plunger, 15. clutch friction plate, 16. clutch steel disc, 17. endless drive part, 18. clutch spring, 19. clutch spring holder, 20. clutch driven member, 21. front-seat sun wheel shaft, 22. No. two motors, 23. end cap, 24. rear box, 25. brake locks hub, 26. brake plunger, 27. brake steel disc, 28. brake bush, 29. brake spring, 30. brake spring seat, 31. final drive input gear, 32. rear planet row subframe, 33. front-seat planet carrier, 34. output shaft of gear-box, 35. main reducing gear output gear, 36. electromotor, A. brake, B. clutch。
Detailed description of the invention
Below in conjunction with accompanying drawing, the invention will be further described:
Consult Fig. 1, Fig. 4; the invention provides a kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case, 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。
Consulting Fig. 1, Fig. 2, Fig. 4, transmission input shaft 1, public gear ring 5, front-seat planetary gear 6, front-seat planetary gear support axle 7, front planet row subframe 8, front-seat sun wheel shaft 21 and front-seat planet carrier 33 have been drawn together in described front planet package。
Consulting 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 transmitting the power of since engine 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；It is solid optical axis that described front-seat planetary gear supports axle 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 and supports axle 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 transmitting the power from No. two motors 22, and inside is provided with oil leab。
Consulting 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 is supported on axle 7 at front-seat planetary gear by sliding bearing empty set；Front-seat planetary gear supports axle 7 and is installed between front-seat planet carrier 33 and front planet row subframe 8；Public gear ring 5 passes through sliding bearing empty set on transmission input shaft 1, and is coordinated by the external splines of left end and the internal spline of 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。
Consulting 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 axle 10, heel row planet carrier 11, heel row sun wheel shaft 12, final drive input gear 31 and rear planet row subframe 32。
Consulting Fig. 1, Fig. 2, Fig. 4, described heel row planetary gear 9 is cylindrical helical gear structure；It is solid optical axis that described heel row planetary gear supports axle 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 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 and supports axle 10。
Consulting 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 is supported on axle 10 at heel row planetary gear by sliding bearing empty set；Heel row planetary gear supports axle 10 and 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。
Consulting 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。
Consult 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。
Consulting 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。
Consulting 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。
Consulting 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。
Consulting 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。
Consulting Fig. 1, described electric system includes 4, No. two motors 22 of a motor。
Consulting 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。
Consulting 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。
Consulting 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。
Consulting 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。
Consulting 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；。
Consulting Fig. 1, described casing mainly includes front casing 2, middle casing 3, end cap 23, rear box 24。
Consulting 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 along the circumferential direction 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。
Consulting 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
Consulting 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
Consulting 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 off 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 brake bush 28 and brake steel disc 27 is pressed together, 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 a 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 all done and are controlled, unpowered input and output。
2, electronic infinite variable speed pattern
Consulting 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 brake A and clutch B in conjunction with situation。
Low-speed mode
Consulting 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。When being short of power, a motor 4 carries out certain power compensation by public gear ring 5。
Fast mode
Consult 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 clutch friction plate 15 and clutch steel disc 16 is pressed together, 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
Consulting 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:
Transmission input shaft (1) is drawn together in described front planet package, public gear ring (5), front-seat planetary gear (6), front-seat planetary gear supports axle (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 it is solid optical axis that described front-seat planetary gear supports axle (7), and front-seat planetary gear (6) is supported on axle (7) at front-seat planetary gear by sliding bearing empty set；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 and supports axle (7)；Front-seat planetary gear supports axle (7) and 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 axle (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, it is solid optical axis that described heel row planetary gear supports axle (10), and heel row planetary gear (9) is supported on axle (10) at heel row planetary gear by sliding bearing empty set；Described heel row planet carrier (11) and final drive input gear (31) are structure as a whole；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 and supports axle (10)；Heel row planetary gear supports axle (10) and 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, with brake bush (28) spline fitted 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, 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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| CN201610146230.8A CN105691195B (en) | 2016-03-15 | 2016-03-15 | A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case |
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| CN201610146230.8A CN105691195B (en) | 2016-03-15 | 2016-03-15 | A kind of series parallel type double planet wheel rows of mixing bimodulus hybrid electric vehicle gearshift case |
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Cited By (5)
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| CN106183800A (en) * | 2016-09-06 | 2016-12-07 | 吉林大学 | A kind of double clutch planetary hybrid vehicle 48V power drive system |
| 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 |
| CN107757337A (en) * | 2017-10-30 | 2018-03-06 | 吉林大学 | Double-planet oil extraction electricity series-parallel connection bimodulus hybrid power system |
| CN108297674A (en) * | 2017-10-24 | 2018-07-20 | 广西玉柴机器股份有限公司 | Double electric machine double row planetary gear hybrid power assembly |
| CN108426024A (en) * | 2018-02-11 | 2018-08-21 | 意宁液压股份有限公司 | Dynamic brake and the integrated transmission device of planetary reduction gear |
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| CN107791821B (en) * | 2017-11-06 | 2019-10-29 | 吉林大学 | Double planet wheel rows of mixing mixed connection bimodulus hybrid power system |
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