CN108032725B - Combined gear train type automobile hybrid power system - Google Patents
Combined gear train type automobile hybrid power system Download PDFInfo
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- CN108032725B CN108032725B CN201810022520.0A CN201810022520A CN108032725B CN 108032725 B CN108032725 B CN 108032725B CN 201810022520 A CN201810022520 A CN 201810022520A CN 108032725 B CN108032725 B CN 108032725B
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- 238000010586 diagram Methods 0.000 description 6
- 230000005611 electricity Effects 0.000 description 3
- 241000282414 Homo sapiens Species 0.000 description 2
- 230000005856 abnormality Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
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- 230000007547 defect Effects 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000003912 environmental pollution Methods 0.000 description 1
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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
- B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
- B60K6/54—Transmission for changing ratio
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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
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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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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/60—Other road transportation technologies with climate change mitigation effect
- Y02T10/62—Hybrid vehicles
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/84—Data processing systems or methods, management, administration
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
- Y02T10/92—Energy efficient charging or discharging systems for batteries, ultracapacitors, supercapacitors or double-layer capacitors specially adapted for vehicles
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Transportation (AREA)
- Mechanical Engineering (AREA)
- Structure Of Transmissions (AREA)
- Electric Propulsion And Braking For Vehicles (AREA)
Abstract
The combined gear train type automobile hybrid power system comprises an engine, two motors, a battery pack, an inverter, three driving gears, four driven gears, a shifting fork joint sleeve, a clutch and a combined gear train speed change mechanism, wherein the combined gear train speed change mechanism comprises a sun gear, an outer planet gear, an inner planet gear, a planet carrier, a central wheel, a brake disc, an inner gear ring and two brakes; the combined wheel train type automobile hybrid power system has four-gear speed change capability, has a pure electric single-motor driving mode, a pure electric double-motor driving mode, a hybrid parallel driving mode, a hybrid series driving mode, an engine independent driving mode and an inertial energy recovery mode, can stably and rapidly realize mode switching, can rapidly change gear speed ratio according to actual running conditions of the automobile, realizes energy optimal configuration, and improves the dynamic property and economical efficiency of the automobile.
Description
Technical Field
The invention belongs to the technical field of automobile hybrid power, and particularly relates to a combined gear train type automobile hybrid power system.
Background
At present, the problems of climate abnormality and environmental pollution caused by excessive application of fossil fuels have become the primary issues affecting the future common fate of human beings, and for the common future of human beings, active efforts are being made in all countries of the world to find new energy sources capable of replacing fossil energy sources, so that the new energy sources are the most effective solutions in the present, and the new energy automobiles are imperative to replace traditional fuel automobiles in the field of automobiles with the forefront of fossil energy consumption.
No matter how high the emission standard of the fuel automobile is, the exhaust gas emitted by the fuel automobile inevitably pollutes the environment, so that the problem of exhaust gas emission is not solved, and only the condition and the root cause are treated. Furthermore, statistics show that under the road condition of more than 8 road types, a common fuel automobile can only exert 40% of the power potential, and in a severely congested urban area, the power potential can even drop to 25%, so that the low-efficiency emission of the fuel automobile is normal.
Therefore, automobile engineers put forward a compromise scheme, namely, develop a hybrid electric vehicle with both a fuel engine and a motor, which not only gives play to the advantages of long continuous working time and good dynamic property of the fuel engine, but also gives play to the advantages of no pollution and low noise of the motor, thereby realizing the purpose of supplementing the advantages, improving the comprehensive thermal efficiency of the vehicle by more than 10%, and reducing the exhaust emission by more than 30%.
Since the first hybrid vehicle was taken off line in 1997 worldwide, all automobile factories and shops all over the world have put on horses and all automobile manufacturers have developed various characteristic automobile hybrid systems, but the existing automobile hybrid systems still have a defect in terms of operational mode diversity and mode switching.
Disclosure of Invention
Aiming at the problems existing in the prior art, the invention provides a combined gear train type automobile hybrid power system which is provided with a pure electric single motor driving mode, a pure electric double motor driving mode, a mixed parallel driving mode, a mixed series driving mode, an engine independent driving mode and an inertial energy recovery mode, can realize mode switching stably and rapidly, can change gear speed ratio rapidly according to actual running conditions of a vehicle, realizes optimal configuration of energy, and improves dynamic property and economical efficiency of the vehicle.
In order to achieve the above purpose, the present invention adopts the following technical scheme: a combined gear train type automobile hybrid power system comprises an engine, a first motor, a second motor, a battery pack, an inverter, a first driving gear, a second driving gear, a third driving gear, a first driven gear, a second driven gear, a third driven gear, a fourth driven gear, a shifting fork joint sleeve and a combined gear train speed change mechanism; the power output shaft of the engine is connected with the motor shaft of the first motor through a clutch, the first driving gear and the second driving gear are both arranged on the motor shaft of the first motor, and the first driving gear and the second driving gear only have rotational freedom degrees relative to the motor shaft of the first motor; the shifting fork joint sleeve is arranged on a motor shaft of the first motor between the first driving gear and the second driving gear, has only axial movement freedom degree relative to the motor shaft of the first motor, and is respectively engaged and matched with the first driving gear and the second driving gear; the third driving gear is fixedly arranged on a motor shaft of the second motor; the first driven gear and the second driven gear are fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the first driven gear is meshed with the first driving gear, and the second driven gear is simultaneously meshed with the second driving gear and the third driving gear; the third driven gear is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the fourth driven gear is fixedly arranged on a wheel shaft of a wheel, and the third driven gear is meshed with the fourth driven gear; the battery pack is electrically connected with the first motor and the second motor through the inverter respectively.
The first driving gear and the first driven gear form a speed-increasing transmission gear set, the second driving gear and the second driven gear form a constant-speed transmission gear set, and the third driving gear and the second driven gear form a speed-reducing transmission gear set.
The combined gear train speed change mechanism comprises a sun gear, an outer planet gear, an inner planet gear, a planet carrier, a central gear, a brake disc, an inner gear ring, a first brake and a second brake; the sun gear is fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the planet gear carrier is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the outer planet gear and the inner planet gear are radially arranged on the planet gear carrier, and the outer planet gear and the inner planet gear only have rotational degrees of freedom on the planet gear carrier; the outer planetary gear is meshed with the inner planetary gear, the sun gear and the inner gear ring simultaneously; the center wheel and the brake disc are sleeved on a power input shaft of the combined gear train speed change mechanism in a coaxial mode, and the center wheel and the brake disc only have rotational freedom degrees relative to the power input shaft of the combined gear train speed change mechanism, and are meshed with the inner planetary gear; the first brake is in braking fit with the brake disc, and the second brake is in braking fit with the annular gear.
When the first brake is released and the second brake is combined, the brake disc is in a free state, the annular gear is in a braking state, and the combined gear train speed change mechanism is in a high-speed gear; when the first brake is combined and the second brake is released, the brake disc is in a braking state, the annular gear is in a free state, and the combined gear train speed change mechanism is in a low-speed gear.
When the first driving gear and the first driven gear form a speed-increasing transmission gear set for power transmission, and the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a first gear ratio; when the constant-speed transmission gear set formed by the second driving gear and the second driven gear transmits power, and when the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a second-speed gear ratio; when the first driving gear and the first driven gear form a speed-increasing transmission gear set for power transmission, and the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a three-speed gear ratio; when the constant-speed transmission gear set formed by the second driving gear and the second driven gear transmits power, and the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a four-speed gear ratio.
The invention has the beneficial effects that:
the combined wheel train type automobile hybrid power system provided by the invention has a pure electric single motor driving mode, a pure electric double motor driving mode, a mixed parallel driving mode, a mixed series driving mode, an engine independent driving mode and an inertial energy recovery mode, can realize mode switching stably and rapidly, can change gear speed ratio rapidly according to actual running conditions of a vehicle, realizes energy optimal configuration, and improves the dynamic property and economical efficiency of the vehicle.
Drawings
FIG. 1 is a schematic diagram of a combined train type automotive hybrid system according to the present invention;
FIG. 2 is a schematic power transfer diagram of the present invention in a single motor drive mode;
FIG. 3 is a schematic diagram of the power transfer of the present invention in a dual electric motor drive mode;
FIG. 4 is a schematic diagram of the power transfer in a hybrid parallel drive mode of the present invention;
FIG. 5 is a schematic power transfer diagram of the present invention in a hybrid series drive mode;
FIG. 6 is a schematic power transfer diagram of the present invention in an engine-only drive mode;
FIG. 7 is a schematic representation of the power transfer of the present invention in an inertial energy recovery mode;
in the figure, 1-engine, 2-first motor, 3-second motor, 4-battery pack, 5-inverter, 6-first driving gear, 7-second driving gear, 8-third driving gear, 9-first driven gear, 10-second driven gear, 11-third driven gear, 12-fourth driven gear, 13-shift fork jointing sleeve, 14-clutch, 15-wheel, 16-sun gear, 17-outer planetary gear, 18-inner planetary gear, 19-planetary carrier, 20-center wheel, 21-brake disc, 22-inner gear ring, 23-first brake, 24-second brake.
Description of the embodiments
The invention will now be described in further detail with reference to the drawings and to specific examples.
As shown in fig. 1, a combined gear train type automobile hybrid power system comprises an engine 1, a first motor 2, a second motor 3, a battery pack 4, an inverter 5, a first driving gear 6, a second driving gear 7, a third driving gear 8, a first driven gear 9, a second driven gear 10, a third driven gear 11, a fourth driven gear 12, a shifting fork joint sleeve 13 and a combined gear train speed change mechanism; the power output shaft of the engine 1 is connected with the motor shaft of the first motor 2 through a clutch 14, the first driving gear 6 and the second driving gear 7 are both arranged on the motor shaft of the first motor 2, and the first driving gear 6 and the second driving gear 7 only have rotational freedom degrees relative to the motor shaft of the first motor 2; the shifting fork joint sleeve 13 is arranged on the motor shaft of the first motor 2 between the first driving gear 6 and the second driving gear 7, the shifting fork joint sleeve 13 has only axial movement freedom degree relative to the motor shaft of the first motor 2, and the shifting fork joint sleeve 13 is respectively engaged and matched with the first driving gear 6 and the second driving gear 7; the third driving gear 8 is fixedly arranged on a motor shaft of the second motor 3; the first driven gear 9 and the second driven gear 10 are fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the first driven gear 9 is meshed with the first driving gear 6, and the second driven gear 10 is simultaneously meshed with the second driving gear 7 and the third driving gear 8; the third driven gear 11 is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the fourth driven gear 12 is fixedly arranged on a wheel shaft of the wheel 15, and the third driven gear 11 is meshed with the fourth driven gear 12; the battery pack 4 is electrically connected to the first motor 2 and the second motor 3 via an inverter 5, respectively.
The first driving gear 6 and the first driven gear 9 form a speed increasing transmission gear set, the second driving gear 7 and the second driven gear 10 form a constant speed transmission gear set, and the third driving gear 8 and the second driven gear 10 form a speed reducing transmission gear set.
The combined gear train speed change mechanism comprises a sun gear 16, an outer planetary gear 17, an inner planetary gear 18, a planetary gear carrier 19, a central gear 20, a brake disc 21, an inner gear ring 22, a first brake 23 and a second brake 24; the sun gear 16 is fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the planet carrier 19 is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the outer planet wheel 17 and the inner planet wheel 18 are radially arranged on the planet carrier 19, and the outer planet wheel 17 and the inner planet wheel 18 only have rotational freedom degrees on the planet carrier 19; the outer planetary gear 17 is meshed with the inner planetary gear 18, the sun gear 16 and the inner gear ring 22 at the same time; the center wheel 20 and the brake disc 21 are sleeved on a power input shaft of the combined gear train speed change mechanism in a coaxial mode, the center wheel 20 and the brake disc 21 only have rotational freedom degrees relative to the power input shaft of the combined gear train speed change mechanism, and the center wheel 20 is meshed with the inner planet wheel 18; the first brake 23 is in braking engagement with the brake disc 21, and the second brake 24 is in braking engagement with the ring gear 22.
When the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the annular gear 22 is in a braking state, and the combined gear train speed change mechanism is in a high-speed gear; when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 is in a braking state, the annular gear 22 is in a free state, and the combined gear train speed change mechanism is in a low gear.
When the first driving gear 6 and the first driven gear 9 form a speed-increasing transmission gear set for power transmission, and when the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a first gear ratio; when the constant-speed transmission gear set formed by the second driving gear 7 and the second driven gear 10 transmits power, and when the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a second-speed gear ratio; when the first driving gear 6 and the first driven gear 9 form a speed-increasing transmission gear set for power transmission, and when the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a three-speed gear ratio; when the second driving gear 7 and the second driven gear 10 form a constant-speed transmission gear set for power transmission, and when the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a four-speed gear ratio.
The use of the invention is described below with reference to the accompanying drawings:
embodiment one: pure electric single motor driving mode
In this mode, as shown in fig. 2, the engine 1 is not operated, the clutch 14 is disengaged, the first motor 2 or the second motor 3 can be selected as a power output motor according to the actual condition, and the battery pack 4 supplies electric power to the first motor 2 or the second motor 3 through the inverter 5.
When the first motor 2 is selected as a power output motor, the second motor 3 does not work, the shifting fork joint sleeve 13 is positioned at the left position or the right position, the shifting fork joint sleeve 13 is jointed with the first driving gear 6 or the second driving gear 7, and then the power of the first motor 2 is transmitted to the power input shaft of the combined gear train speed change mechanism through a speed increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10); at the same time, the second motor 3 is driven to idle through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10);
when the second motor 3 is used as a power output motor, the first motor 2 does not work, the shifting fork joint sleeve 13 is in the middle position, and then the power of the second motor 3 is transmitted to the power input shaft of the combined gear train speed change mechanism through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10); at the same time, the first driving gear 6 and the second driving gear 7 idle;
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the power input shaft of the combined gear train speed change mechanism drives the sun gear 16 to rotate at first, the outer planetary gear 17 is driven to rotate, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the outer planetary gear 17 and the meshing transmission with the inner gear ring 22, and the rotation of the planetary gear carrier 19 is realized through the revolution of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the power input shaft of the combined gear train speed change mechanism drives the sun wheel 16 to rotate at first, so as to drive the outer planetary wheel 17 to rotate, the revolution of the inner planetary wheel 18 around the central wheel 20 is realized through the rotation of the outer planetary wheel 17 and the meshing transmission with the inner planetary wheel 18, and the rotation of the planetary wheel carrier 19 is realized through the revolution of the inner planetary wheel 18; at the same time, the ring gear 22 idles;
the third driven gear 11 is driven to rotate by the rotation of the planet carrier 19, so that the fourth driven gear 12 meshed with the third driven gear 11 is driven to rotate, and finally the wheel 15 is driven to rotate.
Embodiment two: pure electric double-motor driving mode
In this mode, as shown in fig. 3, the engine 1 is not operated, the clutch 14 is disengaged, the first motor 2 and the second motor 3 are simultaneously operated as power output motors, and the battery pack 4 supplies electric power to the first motor 2 and the second motor 3 through the inverter 5.
The shifting fork jointing sleeve 13 is positioned at the left position or the right position, so that the shifting fork jointing sleeve 13 is jointed with the first driving gear 6 or the second driving gear 7, and then the power of the first motor 2 is transmitted to the power input shaft of the combined gear train speed change mechanism through a speed increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10); at the same time, the power of the second motor 3 is transmitted to the power input shaft of the combined gear train speed change mechanism through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10);
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the power input shaft of the combined gear train speed change mechanism drives the sun gear 16 to rotate at first, the outer planetary gear 17 is driven to rotate, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the outer planetary gear 17 and the meshing transmission with the inner gear ring 22, and the rotation of the planetary gear carrier 19 is realized through the revolution of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the power input shaft of the combined gear train speed change mechanism drives the sun wheel 16 to rotate at first, so as to drive the outer planetary wheel 17 to rotate, the revolution of the inner planetary wheel 18 around the central wheel 20 is realized through the rotation of the outer planetary wheel 17 and the meshing transmission with the inner planetary wheel 18, and the rotation of the planetary wheel carrier 19 is realized through the revolution of the inner planetary wheel 18; at the same time, the ring gear 22 idles;
the third driven gear 11 is driven to rotate by the rotation of the planet carrier 19, so that the fourth driven gear 12 meshed with the third driven gear 11 is driven to rotate, and finally the wheel 15 is driven to rotate.
Embodiment III: hybrid parallel drive mode
In this mode, as shown in fig. 4, the engine 1 is operated, the clutch 14 is engaged, and the first motor 2 or the second motor 3 may be used as a power output motor alone or the first motor 2 and the second motor 3 may be used as power output motors at the same time, depending on the actual conditions, and the battery pack 4 supplies electric power to the first motor 2 and the second motor 3 through the inverter 5.
When the engine 1 and the first motor 2 are selected to be combined, the shifting fork joint sleeve 13 is positioned at the left position or the right position, and the shifting fork joint sleeve 13 is jointed with the first driving gear 6 or the second driving gear 7, so that the coupling power of the engine 1 and the first motor 2 is transmitted to the power input shaft of the combined gear train speed change mechanism through a speed increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10); at the same time, the second motor 3 is driven to idle through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10);
when the engine 1 and the second motor 3 are selected to be combined, the shifting fork joint sleeve 13 is in the middle position, and then the power of the engine 1 is transmitted to the power input shaft of the combined gear train speed change mechanism through a speed increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10); at the same time, the power of the second motor 3 is transmitted to the power input shaft of the combined gear train speed change mechanism through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10), and the power of the engine 1 and the power of the second motor 3 are coupled to the power input shaft of the combined gear train speed change mechanism;
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the power input shaft of the combined gear train speed change mechanism drives the sun gear 16 to rotate at first, the outer planetary gear 17 is driven to rotate, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the outer planetary gear 17 and the meshing transmission with the inner gear ring 22, and the rotation of the planetary gear carrier 19 is realized through the revolution of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the power input shaft of the combined gear train speed change mechanism drives the sun wheel 16 to rotate at first, so as to drive the outer planetary wheel 17 to rotate, the revolution of the inner planetary wheel 18 around the central wheel 20 is realized through the rotation of the outer planetary wheel 17 and the meshing transmission with the inner planetary wheel 18, and the rotation of the planetary wheel carrier 19 is realized through the revolution of the inner planetary wheel 18; at the same time, the ring gear 22 idles;
the third driven gear 11 is driven to rotate by the rotation of the planet carrier 19, so that the fourth driven gear 12 meshed with the third driven gear 11 is driven to rotate, and finally the wheel 15 is driven to rotate.
Embodiment four: hybrid series drive mode
In this mode, as shown in fig. 5, the engine 1 is operated, the clutch 14 is engaged, the first motor 2 serves as a generator, and the second motor 3 serves as a power output motor.
The shifting fork joint sleeve 13 is positioned in the middle position, the engine 1 outputs mechanical energy to drive the first motor 2 to generate electricity, the electric energy generated by the first motor 2 is provided for the second motor 3 through the inverter 5, the other path charges the battery pack 4, and the power of the second motor 3 is transmitted to the power input shaft of the combined gear train speed change mechanism through the reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10);
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the power input shaft of the combined gear train speed change mechanism drives the sun gear 16 to rotate at first, the outer planetary gear 17 is driven to rotate, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the outer planetary gear 17 and the meshing transmission with the inner gear ring 22, and the rotation of the planetary gear carrier 19 is realized through the revolution of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the power input shaft of the combined gear train speed change mechanism drives the sun wheel 16 to rotate at first, so as to drive the outer planetary wheel 17 to rotate, the revolution of the inner planetary wheel 18 around the central wheel 20 is realized through the rotation of the outer planetary wheel 17 and the meshing transmission with the inner planetary wheel 18, and the rotation of the planetary wheel carrier 19 is realized through the revolution of the inner planetary wheel 18; at the same time, the ring gear 22 idles;
the third driven gear 11 is driven to rotate by the rotation of the planet carrier 19, so that the fourth driven gear 12 meshed with the third driven gear 11 is driven to rotate, and finally the wheel 15 is driven to rotate.
Fifth embodiment: engine alone drive mode
In this mode, as shown in fig. 6, the engine 1 is operated, the clutch 14 is engaged, and neither the first motor 2 nor the second motor 3 is operated.
The shifting fork jointing sleeve 13 is positioned at the left position or the right position, so that the shifting fork jointing sleeve 13 is jointed with the first driving gear 6 or the second driving gear 7, and then the power of the engine 1 is transmitted to the power input shaft of the combined gear train speed change mechanism through a speed increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10); at the same time, the first motor 2 is driven to idle through a speed-increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant-speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10), and the second motor 3 is driven to idle through a speed-reducing transmission gear set (the third driving gear 8 is meshed with the second driven gear 10);
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the power input shaft of the combined gear train speed change mechanism drives the sun gear 16 to rotate at first, the outer planetary gear 17 is driven to rotate, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the outer planetary gear 17 and the meshing transmission with the inner gear ring 22, and the rotation of the planetary gear carrier 19 is realized through the revolution of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the power input shaft of the combined gear train speed change mechanism drives the sun wheel 16 to rotate at first, so as to drive the outer planetary wheel 17 to rotate, the revolution of the inner planetary wheel 18 around the central wheel 20 is realized through the rotation of the outer planetary wheel 17 and the meshing transmission with the inner planetary wheel 18, and the rotation of the planetary wheel carrier 19 is realized through the revolution of the inner planetary wheel 18; at the same time, the ring gear 22 idles;
the third driven gear 11 is driven to rotate by the rotation of the planet carrier 19, so that the fourth driven gear 12 meshed with the third driven gear 11 is driven to rotate, and finally the wheel 15 is driven to rotate.
Example six: inertial energy recovery mode
In this mode, as shown in fig. 7, the vehicle is in a coasting or braking phase, the engine 1 is not operated, the clutch 14 is disengaged, and both the first motor 2 and the second motor 3 act as generators.
In the process of vehicle sliding or braking, the inertial kinetic energy of the vehicle is converted into the rotating mechanical energy of the wheels 15, and the wheels 15 drive the fourth driven gear 12 to rotate, so as to drive the third driven gear 11 meshed with the fourth driven gear to rotate, and further drive the planet carrier 19 to rotate;
when the first brake 23 is released and the second brake 24 is combined, the brake disc 21 is in a free state, the inner gear ring 22 is in a braking state, the revolution of the outer planetary gear 17 around the sun gear 16 is realized through the rotation of the planetary gear carrier 19, the autorotation of the outer planetary gear 17 is realized through the meshing transmission with the inner gear ring 22, and the sun gear 16 is driven to rotate through the autorotation of the outer planetary gear 17; at the same time, the inner planetary wheels 18, the center wheel 20 and the brake disc 21 idle;
when the first brake 23 is combined and the second brake 24 is released, the brake disc 21 and the central wheel 20 are in a braking state, the inner gear ring 22 is in a free state, the revolution of the outer planetary wheel 17 around the sun wheel 16 is realized through the rotation of the planetary wheel carrier 19, the revolution of the inner planetary wheel 18 around the central wheel 20 and the rotation of the inner planetary wheel 18 are realized through the meshing transmission of the inner planetary wheel 18, the revolution of the outer planetary wheel 17 around the central wheel 20 and the rotation of the inner planetary wheel 18 are realized through the rotation of the inner planetary wheel 18, and the rotation of the outer planetary wheel 17 drives the sun wheel 16 to rotate through the rotation of the outer planetary wheel 17; at the same time, the ring gear 22 idles;
the power input shaft of the combined gear train speed change mechanism is driven to rotate through the rotation of the sun gear 16, so that power is transmitted to the first motor 2 through a speed-increasing transmission gear set (the first driving gear 6 is meshed with the first driven gear 9) or a constant-speed transmission gear set (the second driving gear 7 is meshed with the second driven gear 10), the first motor 2 is driven to generate electricity, and the electric energy generated by the first motor 2 charges the battery pack 4 through the inverter 5; at the same time, power is transmitted to the second motor 3 through a reduction transmission gear set (the third driving gear 8 is meshed with the second driven gear 10), the second motor 3 is driven to generate electricity, and the electric energy generated by the second motor 3 charges the battery pack 4 through the inverter 5.
When the required braking force is small, it is possible to selectively turn off any one of the first motor 2 and the second motor 3, and charge the battery pack 4 by only one motor.
The embodiments are not intended to limit the scope of the invention, but rather are intended to cover all equivalent implementations or modifications that can be made without departing from the scope of the invention.
Claims (2)
1. The utility model provides a combination train formula car hybrid system which characterized in that: the gear shifting mechanism comprises an engine, a first motor, a second motor, a battery pack, an inverter, a first driving gear, a second driving gear, a third driving gear, a first driven gear, a second driven gear, a third driven gear, a fourth driven gear, a shifting fork joint sleeve and a combined gear train speed changing mechanism; the power output shaft of the engine is connected with the motor shaft of the first motor through a clutch, the first driving gear and the second driving gear are both arranged on the motor shaft of the first motor, and the first driving gear and the second driving gear only have rotational freedom degrees relative to the motor shaft of the first motor; the shifting fork joint sleeve is arranged on a motor shaft of the first motor between the first driving gear and the second driving gear, has only axial movement freedom degree relative to the motor shaft of the first motor, and is respectively engaged and matched with the first driving gear and the second driving gear; the third driving gear is fixedly arranged on a motor shaft of the second motor; the first driven gear and the second driven gear are fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the first driven gear is meshed with the first driving gear, and the second driven gear is simultaneously meshed with the second driving gear and the third driving gear; the third driven gear is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the fourth driven gear is fixedly arranged on a wheel shaft of a wheel, and the third driven gear is meshed with the fourth driven gear; the battery pack is electrically connected with the first motor and the second motor through the inverter respectively; the first driving gear and the first driven gear form a speed-increasing transmission gear set, the second driving gear and the second driven gear form a constant-speed transmission gear set, and the third driving gear and the second driven gear form a speed-reducing transmission gear set; the combined gear train speed change mechanism comprises a sun gear, an outer planet gear, an inner planet gear, a planet carrier, a central gear, a brake disc, an inner gear ring, a first brake and a second brake; the sun gear is fixedly arranged on a power input shaft of the combined gear train speed change mechanism, the planet gear carrier is fixedly arranged on a power output shaft of the combined gear train speed change mechanism, the outer planet gear and the inner planet gear are radially arranged on the planet gear carrier, and the outer planet gear and the inner planet gear only have rotational degrees of freedom on the planet gear carrier; the outer planetary gear is meshed with the inner planetary gear, the sun gear and the inner gear ring simultaneously; the center wheel and the brake disc are sleeved on a power input shaft of the combined gear train speed change mechanism in a coaxial mode, and the center wheel and the brake disc only have rotational freedom degrees relative to the power input shaft of the combined gear train speed change mechanism, and are meshed with the inner planetary gear; the first brake is in braking fit with the brake disc, and the second brake is in braking fit with the annular gear; when the first brake is released and the second brake is combined, the brake disc is in a free state, the annular gear is in a braking state, and the combined gear train speed change mechanism is in a high-speed gear; when the first brake is combined and the second brake is released, the brake disc is in a braking state, the annular gear is in a free state, and the combined gear train speed change mechanism is in a low-speed gear.
2. A combination train automotive hybrid system according to claim 1, characterized in that: when the first driving gear and the first driven gear form a speed-increasing transmission gear set for power transmission, and the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a first gear ratio; when the constant-speed transmission gear set formed by the second driving gear and the second driven gear transmits power, and when the combined gear train speed change mechanism is in a high-speed gear, the automobile hybrid power system is in a second-speed gear ratio; when the first driving gear and the first driven gear form a speed-increasing transmission gear set for power transmission, and the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a three-speed gear ratio; when the constant-speed transmission gear set formed by the second driving gear and the second driven gear transmits power, and the combined gear train speed change mechanism is in a low-speed gear, the automobile hybrid power system is in a four-speed gear ratio.
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| CN108556622B (en) * | 2018-05-18 | 2021-08-06 | 芜湖易迅生产力促进中心有限责任公司 | Worm gear and worm transmission for electric automobile and speed changing method |
| CN109720192B (en) * | 2019-01-16 | 2021-07-20 | 江苏大学 | Multi-mode switching power transmission device for loader |
| CN114312330B (en) * | 2021-11-30 | 2024-04-09 | 江苏大学 | Electric automobile braking gear shifting control method and system |
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