CN105751885A - Hybrid powder gearbox of high-power engineering vehicle - Google Patents
Hybrid powder gearbox of high-power engineering vehicle Download PDFInfo
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- CN105751885A CN105751885A CN201610274320.5A CN201610274320A CN105751885A CN 105751885 A CN105751885 A CN 105751885A CN 201610274320 A CN201610274320 A CN 201610274320A CN 105751885 A CN105751885 A CN 105751885A
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- brake
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- diesel engine
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Classifications
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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
-
- 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
- B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
- F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
- F16H3/62—Gearings having three or more central gears
- F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
- F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three sets of orbital gears
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H2200/00—Transmissions for multiple ratios
- F16H2200/20—Transmissions using gears with orbital motion
- F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
- F16H2200/2043—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with five engaging means
Abstract
The invention provides a hybrid powder gearbox of a high-power engineering vehicle, and belongs to the technical field of power transmission systems.The gearbox comprises a gearbox shell, a motor, three planet rows, two clutches, three brakes, an input shaft, a middle shaft, an output shaft and a hydraulic control system.When independently working, the motor is connected with the clutches or the brakes, power is transmitted to the output shaft through the middle shaft, and three transmission speed ratios and backup functions can be achieved; when independently working, a diesel engine is connected with the clutches or the brakes, power is transmitted to the output shaft through the input shaft, and six transmission speed ratios can be achieved; when the diesel engine and the motor work together, higher torque can be provided, and the diesel engine works in the optimal fuel economical area as mush as possible.Power gear shifting can be achieved, the whole gearbox is simple in form, compact in structure, high in bearing capacity and high in transmission efficiency, power performance of the vehicle can be improved to a great extent, and fuel economy is improved.
Description
Technical field
The invention belongs to power drive system technical field, particularly relate to a kind of hybrid power gearbox being applied to high-power engineering truck.
Background technology
Current energy shortage has become the major issue that the whole world faces, and Technology of Hybrid Electric Vehicle can be effectively improved the output of vehicle low speed power and fuel oil consumption, it has also become the developing direction of auto industry.High-power engineering truck (such as heavy mining truck) operationally, works, under low speed and start operating performance under low speed of being everlasting, start and stop operating mode, it is possible to driving with motor, under decelerating mode, motor can realize Brake energy recovery, charges the battery.
In the design documents and materials of hybrid power gearbox, also finding no the hybrid power gearbox suitable in high-power engineering truck, this hybrid power gearbox can improve the fuel economy of vehicle to a great extent.
Summary of the invention
It is an object of the invention to: for improving the fuel economy of high-power engineering truck, promote vehicles dynamic performance, it is proposed that a kind of hybrid power gearbox being suitably applied on high-power engineering truck.
The hybrid power gearbox of high-power engineering truck, including diesel engine, 2 clutches, 3 brakes, motor, 3 planet rows P1, P2, P3, it is characterised in that:
The P3 planet carrier of described diesel engine, motor and planet row coaxially exports；
Described motor is integrated between planet row P1 and P2；
Described planet row P1 includes: P1 arranges sun gear, P1 ranks star-wheel, P1 ranks carrier, P1 toothrow circle；Wherein P1 seniority among brothers and sisters carrier is connected with diesel engine, and P1 arranges sun gear and can be connected with diesel engine through clutch C1, or is connected with brake B1, and P1 toothrow circle is connected with motor；
Described planet row P2 includes: P2 arranges sun gear, P2 ranks star-wheel, P2 ranks carrier, P2 toothrow circle；Wherein P2 seniority among brothers and sisters carrier is connected with P3 toothrow circle, and P2 arranges sun gear and is connected with motor, and P2 toothrow circle is connected with motor through clutch C2, or is connected with brake B2；
Described planet row P3 includes: P3 arranges sun gear, P3 ranks star-wheel, P3 ranks carrier, P3 toothrow circle；Wherein P3 ranks carrier as output shaft, and P3 arranges sun gear and is connected with motor, and P3 toothrow circle is ranked carrier with P2 and is connected, or is connected with brake B3.
During described diesel engine one grade, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 Guan Bi, brake B3 Guan Bi, gear ratio 4.11；
During described diesel engine two grades, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 disconnect, brake B2 Guan Bi, brake B3 Guan Bi, gear ratio 3.02；
During described diesel engine third gear, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 Guan Bi, brake B3 disconnect, gear ratio 2.11；
During described diesel engine fourth gear, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 disconnect, brake B2 Guan Bi, brake B3 disconnect, gear ratio 1.56；
During described diesel engine five grades, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects, gear ratio 1；
During described diesel engine six grades, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects, gear ratio 0.74.
During the generating of described motor, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 disconnects, brake B3 disconnects；
During one grade of described motor, clutch C1 disconnects, brake B1 disconnects, clutch C2 disconnects, brake B2 disconnects, brake B3 Guan Bi；
During two grades of described motor, clutch C1 disconnects, brake B1 disconnects, clutch C2 disconnects, brake B2 Guan Bi, brake B3 disconnect；
During described motor third gear, clutch C1 disconnects, brake B1 disconnects, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects.
Diesel engine and electronic function cooperation, be provided that bigger moment of torsion.
Vehicle reverses gear when travelling, and described motor reverses, clutch C1 disconnection, brake B1 disconnection, clutch C2 disconnection, brake B2 disconnection, brake B3 Guan Bi.
When motor of the present invention works alone, connecting through clutch or brake, power is delivered to output shaft by jackshaft, it may be achieved 3 kinds of transmission speed ratios and gear reversing function；When diesel engine works alone, connecting through clutch or brake, power is delivered to output shaft by power shaft, it may be achieved 6 kinds of transmission speed ratios；When diesel engine and motor cooperation, it is provided that bigger moment of torsion, and diesel engine is allowed to be operated in best fuel-economy district as far as possible.
Having the beneficial effect that of the technique scheme of the present invention:
One is that integration degree is high, and motor is placed between planet row P1, P2, makes overall structure form simple, compact, and reliability is high, and provides gear reversing function；Two is the Technology of Hybrid Electric Vehicle that can realize cascade, under low speed and start operating performance, it is possible to drive with motor, it is necessary to can realize combination drive under high pulling torque operating mode, realize energy regenerating under decelerating mode；Three is that described change speed gear box speed ratio meets desirable gear ratios, while improving shifting comfort, is greatly improved the fuel economy of vehicle.
Accompanying drawing explanation
Fig. 1 is the hybrid power gearbox structure principle chart of the present invention；
Fig. 2 is the hybrid power gearbox motor 1 of present invention power flow chart when keeping off；
Fig. 3 is the hybrid power gearbox diesel engine 1 of present invention power flow chart when keeping off；
Fig. 4 is the hybrid power gearbox structure chart of the present invention；
[main element symbol description]
1-diesel engine；2-P1 arranges sun gear；3-P1 ranks carrier；4-P1 toothrow circle；5-clutch C1；6-brake B1；7-clutch C2；8-brake B2；9-brake B3；10-P3 toothrow circle；11-P3 ranks carrier；12-P3 arranges sun gear；13-P2 toothrow circle；14-P2 ranks carrier；15-P2 arranges sun gear；16-motor.
Detailed description of the invention
For making the technical problem to be solved in the present invention, technical scheme and advantage clearly, it is described in detail below in conjunction with the accompanying drawings and the specific embodiments.
The present invention provides a kind of hybrid power gearbox for high-power engineering truck, as Figure 1 and Figure 4, for schematic diagram and the structure chart of this hybrid power gearbox, including gear box casing, motor, 3 planet rows, 2 clutches and 3 brakes, power shaft, jackshaft, output shaft and hydraulic control system.
Being illustrated in figure 1 the hybrid power gearbox principle schematic of the present invention, power is inputted by diesel engine or motor, power can be made with different speed ratio output by switch clutch and brake, meet the duty requirements of vehicle.
Time as shown in table 1 for hybrid power gearbox electric motor operation of the present invention, shift process is embodied as.
When reversing gear, brake B3 closes, and motor reverses, and its output torque is delivered to P3 and arranges sun gear, and P3 toothrow circle is fixed, and ranks carrier output by P3；
During 1 gear, brake B3 closes, and motor rotates forward, and its output torque is delivered to P3 and arranges sun gear, and P3 toothrow circle is fixed, and ranks carrier output by P3；
During 2 gear, brake B2 closes, and motor rotates forward, and its output torque is delivered to P2 row's sun gear and P3 arranges sun gear, and P2 toothrow circle is fixed, and P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
During 3 gear, clutch C2 closes, and motor rotates forward, and its output torque is delivered to P2 row's sun gear, P2 toothrow circle and P3 and arranges sun gear, and P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
Gear switch when table 1 motor works independently
Time as shown in table 2 for hybrid power gearbox diesel engine of the present invention work, shift process is embodied as.
During 1 gear, clutch C1, brake B2, brake B3 close, diesel engine rotates forward, its output torque is delivered to P1 and arranges sun gear and P1 seniority among brothers and sisters carrier, exporting P2 through P1 toothrow circle and arrange sun gear and P3 row's sun gear, P2 toothrow circle is fixed, and P2 ranks carrier and is connected with P3 toothrow circle, P3 toothrow circle is fixed, and ranks carrier output eventually through P3；
During 2 gear, brake B1, brake B2, brake B3 close, diesel engine rotates forward, its output torque is delivered to P1 and ranks carrier, and P1 arranges sun gear and fixes, and exports P2 through P1 toothrow circle and arranges sun gear and P3 row's sun gear, P2 toothrow circle is fixed, P2 ranks carrier and is connected with P3 toothrow circle, and P3 toothrow circle is fixed, and ranks carrier output eventually through P3；
During 3 gear, clutch C1, brake B2 close, diesel engine rotates forward, its output torque is delivered to P1 and arranges sun gear and P1 seniority among brothers and sisters carrier, export P2 through P1 toothrow circle and arrange sun gear and P3 row's sun gear, P2 toothrow circle is fixed, and P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
During 4 gear, brake B1, brake B2 close, diesel engine rotates forward, its output torque is delivered to P1 and ranks carrier, P1 arranges sun gear and fixes, and exports P2 through P1 toothrow circle and arranges sun gear and P3 row's sun gear, and P2 toothrow circle is fixed, P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
During 5 gear, clutch C1, clutch C2 close, and diesel engine rotates forward, its output torque is delivered to P1 and arranges sun gear and P1 seniority among brothers and sisters carrier, exporting P2 through P1 toothrow circle and arrange sun gear, P2 toothrow circle and P3 row's sun gear, P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
During 6 gear, brake B1, clutch C2 close, diesel engine rotates forward, its output torque is delivered to P1 and ranks carrier, P1 arranges sun gear and fixes, exporting P2 through P1 toothrow circle and arrange sun gear, P2 toothrow circle and P3 row's sun gear, P2 ranks carrier and is connected with P3 toothrow circle, ranks carrier output eventually through P3；
Gear switch when table 2 diesel engine works independently
The above is the preferred embodiment of the present invention; it should be pointed out that, for those skilled in the art, under the premise without departing from principle of the present invention; can also making some improvements and modifications, these improvements and modifications also should be regarded as protection scope of the present invention.
Claims (5)
1. the hybrid power gearbox of high-power engineering truck, including diesel engine, 2 clutches, 3 brakes, motor, 3 planet rows P1, P2, P3, it is characterised in that:
The P3 planet carrier of described diesel engine, motor and planet row coaxially exports；
Described motor is integrated between planet row P1 and P2；
Described planet row P1 includes: P1 arranges sun gear, P1 ranks star-wheel, P1 ranks carrier, P1 toothrow circle；Wherein P1 seniority among brothers and sisters carrier is connected with diesel engine, and P1 arranges sun gear and can be connected with diesel engine through clutch C1, or is connected with brake B1, and P1 toothrow circle is connected with motor；
Described planet row P2 includes: P2 arranges sun gear, P2 ranks star-wheel, P2 ranks carrier, P2 toothrow circle；Wherein P2 seniority among brothers and sisters carrier is connected with P3 toothrow circle, and P2 arranges sun gear and is connected with motor, and P2 toothrow circle is connected with motor through clutch C2, or is connected with brake B2；
Described planet row P3 includes: P3 arranges sun gear, P3 ranks star-wheel, P3 ranks carrier, P3 toothrow circle；Wherein P3 ranks carrier as output shaft, and P3 arranges sun gear and is connected with motor, and P3 toothrow circle is ranked carrier with P2 and is connected, or is connected with brake B3.
2. the hybrid power gearbox of high-power engineering truck according to claim 1, it is characterised in that:
During described diesel engine one grade, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 Guan Bi, brake B3 Guan Bi, gear ratio 4.11；
During described diesel engine two grades, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 disconnect, brake B2 Guan Bi, brake B3 Guan Bi, gear ratio 3.02；
During described diesel engine third gear, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 Guan Bi, brake B3 disconnect, gear ratio 2.11；
During described diesel engine fourth gear, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 disconnect, brake B2 Guan Bi, brake B3 disconnect, gear ratio 1.56；
During described diesel engine five grades, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects, gear ratio 1；
During described diesel engine six grades, clutch C1 disconnects, brake B1 Guan Bi, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects, gear ratio 0.74.
3. the hybrid power gearbox of high-power engineering truck according to claim 1, it is characterised in that:
During the generating of described motor, clutch C1 Guan Bi, brake B1 disconnect, clutch C2 disconnects, brake B2 disconnects, brake B3 disconnects；
During one grade of described motor, clutch C1 disconnects, brake B1 disconnects, clutch C2 disconnects, brake B2 disconnects, brake B3 Guan Bi；
During two grades of described motor, clutch C1 disconnects, brake B1 disconnects, clutch C2 disconnects, brake B2 Guan Bi, brake B3 disconnect；
During described motor third gear, clutch C1 disconnects, brake B1 disconnects, clutch C2 Guan Bi, brake B2 disconnect, brake B3 disconnects.
4. the hybrid power gearbox of high-power engineering truck according to claim 1, it is characterised in that:
Diesel engine and electronic function cooperation, be provided that bigger moment of torsion.
5. the hybrid power gearbox of high-power engineering truck according to claim 1, it is characterised in that:
Vehicle reverses gear when travelling, and described motor reverses, clutch C1 disconnection, brake B1 disconnection, clutch C2 disconnection, brake B2 disconnection, brake B3 Guan Bi.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610274320.5A CN105751885B (en) | 2016-04-28 | 2016-04-28 | The hybrid power gearbox of high-power engineering truck |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201610274320.5A CN105751885B (en) | 2016-04-28 | 2016-04-28 | The hybrid power gearbox of high-power engineering truck |
Publications (2)
| Publication Number | Publication Date |
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| CN105751885A true CN105751885A (en) | 2016-07-13 |
| CN105751885B CN105751885B (en) | 2018-03-13 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN201610274320.5A Expired - Fee Related CN105751885B (en) | 2016-04-28 | 2016-04-28 | The hybrid power gearbox of high-power engineering truck |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106394226A (en) * | 2016-09-19 | 2017-02-15 | 北京科技大学 | Hybrid power gearbox of large-power vehicle |
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| DE102012216230A1 (en) * | 2012-09-13 | 2014-03-13 | Zf Friedrichshafen Ag | Planetary construction-type multi-stage reduction gear i.e. machine gear box, for motor car, has shaft coupled to housing over brake, where clutch, brake and another brake are designed as slat shifting elements |
| CN104340043A (en) * | 2013-07-28 | 2015-02-11 | 张崇信 | Automatic gearbox transmission system for hybrid electric vehicle |
| CN205553895U (en) * | 2016-04-28 | 2016-09-07 | 北京科技大学 | High -power engineering vehicle's hybrid gearbox |
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2016
- 2016-04-28 CN CN201610274320.5A patent/CN105751885B/en not_active Expired - Fee Related
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20060105879A1 (en) * | 2003-07-31 | 2006-05-18 | Peter Tiesler | Multi-stage automatic transmission with three planetary gearwheel assemblies |
| CN101371061A (en) * | 2005-01-04 | 2009-02-18 | 通用汽车公司 | Electrically variable transmision having three interconnected planetary gear sets |
| CN101563252A (en) * | 2006-12-18 | 2009-10-21 | 丰田自动车株式会社 | Hybrid drive device |
| DE102012216230A1 (en) * | 2012-09-13 | 2014-03-13 | Zf Friedrichshafen Ag | Planetary construction-type multi-stage reduction gear i.e. machine gear box, for motor car, has shaft coupled to housing over brake, where clutch, brake and another brake are designed as slat shifting elements |
| CN104340043A (en) * | 2013-07-28 | 2015-02-11 | 张崇信 | Automatic gearbox transmission system for hybrid electric vehicle |
| CN205553895U (en) * | 2016-04-28 | 2016-09-07 | 北京科技大学 | High -power engineering vehicle's hybrid gearbox |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106394226A (en) * | 2016-09-19 | 2017-02-15 | 北京科技大学 | Hybrid power gearbox of large-power vehicle |
| CN106394226B (en) * | 2016-09-19 | 2018-10-26 | 北京科技大学 | The hybrid power gearbox of High-Powered Vehicle |
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| Publication number | Publication date |
|---|---|
| CN105751885B (en) | 2018-03-13 |
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