WO2024087600A1 - Hybrid power transmission assembly, hybrid electric drive system, and vehicle - Google Patents

Hybrid power transmission assembly, hybrid electric drive system, and vehicle Download PDF

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Publication number
WO2024087600A1
WO2024087600A1 PCT/CN2023/095712 CN2023095712W WO2024087600A1 WO 2024087600 A1 WO2024087600 A1 WO 2024087600A1 CN 2023095712 W CN2023095712 W CN 2023095712W WO 2024087600 A1 WO2024087600 A1 WO 2024087600A1
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WO
WIPO (PCT)
Prior art keywords
gear
shaft
assembly
shaft assembly
actuator
Prior art date
Application number
PCT/CN2023/095712
Other languages
French (fr)
Chinese (zh)
Inventor
唐琛
李曼丽
雷君
薛龙
曹大顾
Original Assignee
东风汽车集团股份有限公司
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Publication of WO2024087600A1 publication Critical patent/WO2024087600A1/en

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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
    • B60K6/24—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 combustion engines
    • 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
    • B60K6/26—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 motors or the generators
    • 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
    • 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
    • B60K6/22—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
    • B60K6/40—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 assembly or relative disposition of components
    • 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
    • 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

Definitions

  • the present invention belongs to the technical field of hybrid power transmissions, and in particular relates to a hybrid power transmission mechanism assembly, a hybrid power electric drive system and a vehicle.
  • Hybrid vehicle drive technology is the core stage of the development process of new energy vehicles. Improving fuel economy and reducing emissions are important issues facing hybrid technology.
  • the mainstream hybrid electric drive products on the market are still mostly dual-motor single-speed hybrids, which can achieve pure electric, series/parking power generation and parallel/engine direct drive and other working modes, and are suitable for HEV and PHEV models at the same time.
  • multi-speed hybrid engines have become a development trend. Due to the increase in the number of gears, the structure of the entire power transmission device has become complicated, the structure of the entire power transmission device has become huge, and the entire axial size will also increase.
  • the present disclosure provides a hybrid transmission mechanism assembly, a hybrid electric drive system and a vehicle, which can reduce the assembly volume, improve the mounting performance and meet a more flexible layout.
  • a hybrid transmission mechanism assembly comprising an engine input shaft assembly, a generator, an ICE intermediate shaft assembly, a differential shaft assembly, an EV intermediate shaft assembly, a drive motor input shaft assembly and a drive motor that are transmission-connected; wherein the engine input shaft assembly is coaxially arranged with the generator, and the drive motor input shaft assembly is coaxially arranged with the drive motor; the generator and the drive motor are located on the same side; the installation height of the engine input shaft assembly is located between the drive motor and the differential shaft assembly, and the projection of the engine input shaft assembly on the vertical plane has an overlapping part with the projection of the drive motor and the differential shaft assembly on the vertical plane; the engine input shaft assembly comprises a planetary row, at least one actuator, at least one support bearing, at least one gear gear and an inner ring shaft; the inner ring shaft is sleeved outside the planetary row, and the inner ring shaft is transmission-connected with the inner ring of the planetary row; the at least one actuator, the
  • a hybrid electric drive system including: a housing assembly, provided with a shaft gear cavity and a motor cavity; the above-mentioned hybrid power transmission mechanism assembly, in which the engine input shaft assembly, the drive motor input shaft assembly, the ICE intermediate shaft assembly, the EV intermediate shaft assembly and the differential shaft assembly are all installed in the shaft gear cavity, and the generator and the drive motor are both installed in the motor cavity; a shift mechanism assembly, installed in the shaft gear cavity, and acting on the actuator.
  • a vehicle comprising the above-mentioned hybrid electric drive system.
  • FIG1 is a schematic structural diagram of a hybrid transmission mechanism assembly according to some embodiments of the present disclosure.
  • FIG2 is a schematic structural diagram of the hybrid power transmission mechanism assembly of FIG1 at a certain viewing angle
  • FIG3 is a schematic structural diagram of the hybrid power transmission mechanism assembly of FIG1 from another perspective
  • FIG4 is a full cross-sectional view of the engine input shaft assembly in the hybrid transmission mechanism assembly of FIG1 ;
  • FIG5 is a schematic structural diagram of an internal lubrication passage of the engine input shaft assembly of FIG4 ;
  • FIG6 is a schematic structural diagram of the inner ring gear shaft in the engine input shaft assembly of FIG4 ;
  • FIG7 is a full cross-sectional view of the inner gear ring shaft of FIG6;
  • FIG8 is an overall structural diagram of a hybrid electric drive system according to some embodiments of the present disclosure.
  • FIG9 is a schematic diagram of the structure of the hybrid electric drive system of FIG8 after the end cover is removed;
  • FIG10 is a schematic diagram of the structure of the hybrid electric drive system of FIG8 after the right housing is removed.
  • FIG. 11 is a schematic structural diagram of the middle plate of the hybrid electric drive system of FIG. 8 .
  • 600-hybrid power transmission assembly 610-engine input shaft assembly; 620-generator, 621-generator rotor, 622-second hollow cavity; 630-ICE intermediate shaft assembly, 631-ICE intermediate shaft, 632-first ICE intermediate gear, 633-second ICE intermediate gear; 640-differential shaft assembly; 650-EV intermediate shaft assembly, 651-EV intermediate shaft, 652-first EV intermediate gear, 653-second EV intermediate gear; 660-drive motor input shaft assembly, 661-input shaft, 662-transmission gear; 670-drive motor, 671-rotor of drive motor.
  • 200-inner gear ring shaft 201-inner hole; 210-sleeve portion; 220-cover portion, 221-gear sleeve portion, 222-baffle portion, 223-inner spline; 230-first mounting position; 240-assembly position, 241-inner hole wall; 250-second mounting position; 260-limiting structure, 261-circlip groove, 262-end face, 263-convex edge, 264-hole shoulder; 270-oil guide hole; 280-oil guide groove.
  • 10-oil guide pipe 11-oil outlet hole, 12-oil outlet; 20-oil guide piece; 30-bushing; 40-actuator, 41-gear hub, 42- Combining teeth, S1-first actuator, S2-second actuator; 50-first gear, 51-gear ring, 52-connecting part; 60-second gear; 70-circlip; 80-sleeve.
  • FIG. 1 is a schematic diagram of the structure of a hybrid transmission mechanism assembly according to some embodiments of the present disclosure
  • FIG. 2 is a schematic diagram of the structure of the hybrid transmission mechanism assembly of FIG. 1 at a certain viewing angle
  • FIG. 3 is a schematic diagram of the structure of the hybrid transmission mechanism assembly of FIG. 1 at another viewing angle.
  • a hybrid transmission mechanism assembly 600 is provided, as shown in FIGS. 1 to 3 , which may include an engine input shaft assembly 610, a generator 620, an ICE intermediate shaft assembly 630, a differential shaft assembly 640, an EV intermediate shaft assembly 650, a drive motor input shaft assembly 660, and a drive motor 670.
  • 610 is connected to the engine by transmission, and the engine input shaft assembly 610 is provided with a planetary gear 100, an actuator and a gear gear, so that gear shifting can be realized. That is, the hybrid power transmission mechanism assembly 600 can realize the hybrid power input of the engine + motor, and the multi-gear of the hybrid engine.
  • the positions of the above-mentioned assemblies are arranged; the engine input shaft assembly 610 is coaxially arranged with the generator 620, that is, the rotor 621 of the generator 620 is directly connected to the input shaft (sun gear shaft 110, planetary carrier 120 or inner gear ring shaft 200) of the engine input shaft assembly 610 by transmission, for example, by key connection, gear connection, etc.
  • the drive motor input shaft assembly 660 is coaxially arranged with the drive motor 670, that is, the rotor 671 of the drive motor 670 is directly connected to the input shaft 661 of the drive motor input shaft assembly 660 by transmission, for example, by key connection, gear connection, etc., and a transmission gear 662 is integrally formed on the input shaft 661 of the drive motor input shaft assembly 660.
  • the generator 620 and the drive motor 670 are located on the same side.
  • FIG2 and FIG3 show the structure of the hybrid transmission mechanism assembly 600 when the generator 620 and the drive motor 670 are located on the left side of the engine input shaft assembly 610.
  • the motor assembly generator 620 and the drive motor 670
  • the shaft gear assembly engine input shaft assembly 610, ICE intermediate shaft assembly 630, differential shaft assembly 640, EV intermediate shaft assembly 650, drive motor input shaft assembly 660
  • the motor is usually cooled by oil injection, and the working voltage of the motor is relatively high
  • the bearings of the shaft gear assembly are usually actively lubricated
  • the voltage of the electronic components such as the shift motor and the sensor is relatively low.
  • the scheme of arranging the motor coaxially with the input shaft can reduce the one-way size of the hybrid transmission mechanism assembly 600.
  • the axis center position of the drive motor 670 is the highest, the overall height of the ICE intermediate shaft assembly 630 and the differential shaft assembly 640 is the lowest, the installation height of the engine input shaft assembly 610 is located between the drive motor 670 and the differential shaft assembly 640, and the projection of the engine input shaft assembly 610 on the vertical plane overlaps with the projection of the drive motor 670 and the differential shaft assembly 640 on the vertical plane. Therefore, the axis center of the engine input shaft assembly 610, the axis center of the drive motor 670 and the axis center of the differential shaft assembly 640 are distributed in a triangular shape, as shown in FIG1.
  • the triangular distribution structure can not only reduce the one-way size of the hybrid transmission mechanism assembly 600, but also has a stable structure.
  • the triangular distribution can provide installation space for the ICE intermediate shaft assembly 630 and the EV intermediate shaft assembly 650, and can further reduce the size of the hybrid transmission mechanism assembly 600 on a plane perpendicular to the axis of the engine input shaft.
  • the axis of the EV intermediate shaft assembly 650 is located in a triangular area surrounded by the axis of the engine input shaft assembly 610, the drive motor 670, and the differential shaft assembly 640.
  • the axis of the ICE intermediate shaft assembly 630 is located below the axis line connecting the engine input shaft assembly 610 and the differential shaft assembly 640, and the axis of the ICE intermediate shaft assembly 630 is at the lowest height.
  • the engine input shaft assembly 610 is used to connect the engine, and the gear change of the engine is also achieved through the engine input shaft assembly 610.
  • FIG4 is a full cross-sectional view of the engine input shaft assembly in the hybrid transmission mechanism assembly of FIG1.
  • the engine input shaft assembly 610 may include a planetary gear 100, at least one actuator, at least one support bearing, at least one gear gear and an inner ring shaft 200; the inner ring shaft 200 is sleeved outside the planetary gear 100, and the inner ring shaft 200 is transmission-connected with the inner ring 150 of the planetary gear 100, serving as a part of the planetary gear 100; at least one actuator, at least one support bearing, and at least one gear gear are all arranged on the inner ring shaft 200.
  • the transmission function of the planetary gear 100, the installation of the actuator, the installation of the gear gear and the necessary axial limiting function can be integrated at the same time, thereby greatly improving the integration of the hybrid transmission mechanism assembly 600, reducing the functional volume of the hybrid transmission mechanism assembly 600 in the axial direction, and making it have more flexible layout and mounting performance.
  • the shift mechanism acts on the actuator, which changes the torque transmission path so that gears of different diameters participate in the power transmission, thereby achieving gear shifting.
  • the torque of the engine input shaft assembly 610 is transmitted to the EV intermediate shaft assembly 650 and the ICE intermediate shaft assembly 630 by the gear gears.
  • the EV intermediate shaft assembly 650 may include an EV intermediate shaft 651 and a first EV intermediate gear 652 and a second EV intermediate gear 653 mounted on the EV intermediate shaft 651.
  • the diameter of the first EV intermediate gear 652 is larger than that of the second EV intermediate gear 653.
  • the second EV intermediate gear 653 is relatively small, the second EV intermediate gear 653 and the EV intermediate shaft 651 can be integrally formed, and the first EV intermediate gear 652 is mounted on the EV intermediate shaft 651, and the two are connected by a key.
  • the EV intermediate shaft assembly 650 is connected to the engine input shaft assembly 610 and the drive motor input shaft assembly 660 through the first EV intermediate gear 652, specifically, the first EV intermediate gear 652 is meshed with the first gear 50 and the drive gear 662 of the drive motor input shaft assembly 660; the EV intermediate shaft assembly 650 is connected to the differential shaft assembly 640 through the second EV intermediate gear 653.
  • the ICE intermediate shaft assembly 630 may include an ICE intermediate shaft 631 and a first ICE intermediate gear 632 and a second ICE intermediate gear 633 mounted on the ICE intermediate shaft 631.
  • the diameter of the first ICE intermediate gear 632 is larger than that of the second ICE intermediate gear 633. Since the second ICE intermediate gear 633 is smaller, the second ICE intermediate gear 633 and the ICE intermediate shaft 631 may be integrally formed, and the first ICE intermediate gear 632 is sleeved on the ICE intermediate shaft 631, and the two are connected by a key.
  • the ICE intermediate shaft assembly 630 is transmission-connected to the engine input shaft assembly 610 through the first ICE intermediate gear 632, specifically, the first ICE intermediate gear 632 is meshed with the second gear 60; the ICE intermediate shaft assembly 630 is transmission-connected to the differential shaft assembly 640 through the second ICE intermediate gear 633.
  • the engine input shaft assembly 610 is the most important shaft-tooth assembly in the hybrid transmission mechanism assembly 600, which realizes the functions of engine power input, energy recovery, and gear shifting.
  • the inner ring gear shaft 200 in the engine input shaft assembly 610 serves as a supporting skeleton to realize the installation and fixation of the planetary gear 100, at least one actuator, at least one support bearing, and at least one gear gear.
  • the engine input shaft assembly 610 is provided with only one planetary gear 100, as shown in FIG. 4, and the planetary gear 100 may include a sun gear shaft 110, a planet carrier 120, a sun gear 130, a planetary gear 140, and an inner ring gear 150.
  • the sun gear 130 is mounted on the sun gear shaft 110, or is integrally formed with the sun gear shaft 110.
  • the planetary gear 140 is mounted on the planetary gear 140 shaft 123 of the planetary carrier 120 through the planetary gear 140 bearing 40 .
  • the sun gear 130 , the planetary gear 140 and the inner ring gear 150 are arranged and meshed in sequence from the inside to the outside.
  • the inner ring gear 150 is transmission-connected to the inner ring gear shaft 200 .
  • the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100 is connected to the engine to realize the engine power input.
  • the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100 is connected to the generator 620 to realize the motor power input.
  • the inner gear ring shaft 200 is sleeved on the planetary carrier shaft 121 or the sun gear shaft 110 of the planetary gear row 100 for engine power input.
  • the inner gear ring shaft 200 and the planetary carrier shaft 121 are used as outputs, and the inner gear ring shaft 200 is correspondingly sleeved on the planetary carrier shaft 121, and the inner gear ring shaft 200 or the planetary carrier shaft 121 is provided with a connection structure for transmission connection with the generator 620.
  • the planetary gear row 100 uses the planetary carrier shaft 121 as input, the inner ring gear shaft 200 and the sun gear shaft 110 are used as outputs, and the inner ring gear shaft 200 is correspondingly sleeved on the sun gear shaft 110, and the sun gear shaft 110 or the inner ring gear shaft 200 is provided with a connection structure for transmission connection with the generator 620.
  • the planetary gear row 100 uses the planetary carrier shaft 121 to input engine power, and the inner ring gear shaft 200 and the sun gear shaft 110 output engine power.
  • the inner ring gear shaft 200 is sleeved on the sun gear shaft 110.
  • the inner gear ring shaft 200 may include a sleeve portion 210 and a cover portion 220.
  • the sleeve portion 210 is a sleeve structure that can be mounted on a shaft, such as the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear 100.
  • the sleeve portion 210 has a relatively long axial dimension, and may be provided with a plurality of first mounting positions 230 for mounting the actuator 40, or a plurality of assembly positions 240 for setting the support bearing, or a plurality of second mounting positions 250 for setting the gear position.
  • the cover portion 220 is in transmission connection with the inner gear ring 150 of the planetary gear 100, and participates in the operation of the planetary gear 100 as a part of the planetary gear 100. Both the inner hole profile and the outer profile of the cover portion 220 may be used as the assembly position 240 for setting the support bearing or the second mounting position 250 for setting the gear. Therefore, by setting the inner ring gear shaft 200, the transmission function of the planetary gear 100, the installation of the actuator 40, the installation of the gear gear and the necessary axial limiting function can be integrated at the same time, thereby greatly improving the integration of the engine input shaft assembly 610, reducing the functional volume of the engine input shaft assembly 610, and making the electric drive system equipped with the engine input shaft assembly 610 have more flexible layout and mounting performance.
  • the cover portion 220 of the inner gear ring shaft 200 and the inner gear ring 150 of the planetary gear row 100 can be specifically integrally formed, welded or keyed.
  • the inner gear ring shaft 200, the planetary carrier shaft 121, and the sun gear shaft 110 need to rotate during operation, and there is a speed difference under certain working conditions, so it is necessary to install a bearing between the inner gear ring shaft 200 and the sun gear shaft 110 or the planetary carrier shaft 121, and the inner ring of the bearing is sleeved on the sun gear shaft 110 or the planetary carrier shaft 121, and the inner gear ring shaft 200 is sleeved on the outer ring of the bearing.
  • the inner gear ring shaft 200 is sleeved on the sun gear shaft 110 through two needle bearings 177b, as shown in Figure 4.
  • the inner gear ring shaft 200 may be an integral structure, that is, the sleeve portion 210 and the cover portion 220 are integrally formed by casting or machining.
  • the inner gear ring shaft 200 may also be a split structure, and the sleeve portion 210 and the cover portion 220 may be fixedly connected by welding, bonding, screwing, etc.
  • the inner gear ring shaft 200 is a one-piece structure formed by casting, and then the inner and outer surfaces are machined, and the material may be a metal material such as stainless steel and cast aluminum.
  • the cover portion 220 of the inner gear ring shaft 200 is covered on the main part of the planetary gear 100, and the sun gear 130, the planetary gear 140, and the inner gear ring 150 of the planetary gear 100 are all located in the inner hole of the cover portion 220.
  • the cover portion 220 may include a gear sleeve portion 221 and a baffle portion 222, and the inner ring of the baffle portion 222 is connected to the shaft sleeve portion 210, and the outer ring is connected to the gear sleeve portion 221.
  • the structure of the gear sleeve portion 221 is similar to that of the shaft sleeve portion 210, and both are shaft sleeve structures.
  • the gear sleeve portion 221 is transmission-connected to the inner gear ring 150 of the planetary gear 100.
  • the baffle portion 222 may be an annular flat plate, an annular spherical shell, or a three-dimensional structure composed of multiple connecting rods. The specific structural form of the baffle portion 222 is not limited in this disclosure.
  • the shaft sleeve portion 210, the baffle portion 222, and the gear sleeve portion 221 may be an integrated structure, or fixedly connected by welding, bonding, screwing, etc.
  • the gear sleeve portion 221 and the inner gear ring 150 may be an integral structure or key-connected to achieve power transmission, so that the entire inner gear ring shaft 200 can rotate together with the inner gear ring 150 of the planetary gear set 100 .
  • the gear sleeve 221 is connected to the inner gear ring 150 through a spline
  • the inner profile of the gear sleeve 221 is provided with an inner spline 223
  • the inner profile of the inner gear ring 150 is a tooth meshing with the planetary gear 140
  • the outer profile is an outer spline
  • the inner gear ring 150 is axially inserted into the inner spline 223
  • one side of the inner gear ring 150 is axially limited by the inner end face 262 of the baffle 222
  • a retaining spring groove 261 is provided on the inner spline 223 of the gear sleeve 221, and after the retaining spring 70 is installed in the retaining spring groove 261, the retaining spring 70 can axially limit the other side of the inner gear ring 150.
  • the retaining spring 70 is a detachable structure and will not affect the installation and removal of the inner gear ring 150.
  • the multiple component installation positions on the inner gear ring shaft 200 mainly include a first installation position 230 for installing the actuator 40, an assembly position 240 for setting the support bearing, and a second installation position 250 for setting the gear.
  • the actuator 40 can be a synchronizer or a clutch, and the actuator 40 can be loosely mounted on the inner gear ring shaft 200, or fixedly connected or transmission connected to the inner gear ring shaft 200.
  • the support bearing is used to install the inner gear ring shaft 200 on the housing assembly 300.
  • the gear can be a gear gear or a transmission gear that only plays a transmission role.
  • the gear can be loosely mounted on the inner gear ring shaft 200, or fixedly connected or transmission connected to the inner gear ring shaft 200.
  • other component installation positions can also be set on the inner gear ring shaft 200 according to specific circumstances, such as a component installation position for installing an oil retaining member, a component installation position for setting a sensor, etc.
  • the first installation position 230 is only arranged on the sleeve portion 210, mainly because the action of the actuator 40 requires a certain axial space, and the axial dimension of the sleeve portion 210 is larger than that of the cover portion 220, which can meet the axial space required for the action of the actuator 40; on the other hand, the sleeve portion 210 is sleeved on the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100, and the cover portion 220 is sleeved on the sun gear 130, the planetary gear 140, and the inner ring gear 150 of the planetary gear row 100.
  • the radial dimension of the sleeve portion 210 is smaller than that of the cover portion 220, which is convenient for arranging the actuator 40.
  • the function of the actuator 40 is to change the transmission ratio of the planetary gear row 100, such as engaging the inner gear ring 150 of the planetary gear row 100 with the sun gear shaft 110 for joint rotation, engaging the inner gear ring 150 with the planet carrier for joint rotation, engaging the planet carrier with the sun gear shaft 110 for joint rotation, locking the inner gear ring 150, locking the sun gear 130, locking the planet gear 140, etc.
  • the first mounting position 230 is a key connection structure, so that the actuator 40 is transmission-connected with the inner gear ring shaft 200.
  • the actuator 40 can change the movement of the inner gear ring 150, such as engaging the inner gear ring 150 with the sun gear shaft 110 or the planet carrier, or locking the inner gear ring 150.
  • the inner gear ring shaft 200 is provided with a plurality of limiting structures 260 for axial limiting, and the limiting structures 260 may be limiting bosses, limiting steps or grooves for installing retaining springs 70. If the limiting structure 260 is used to limit the bearing axially, a limiting boss, limiting step or structural end face limiting is usually selected; if the limiting structure 260 is used to limit the gear axially, and the gear is connected to the inner gear ring shaft 200 by transmission, such as a spline connection, then retaining springs 70 are usually selected for axial limiting.
  • the outer surface of the sleeve part 210 is designed as a stepped shaft, specifically, from the far planetary gear end to the near planetary gear end, the outer diameter of the sleeve part 210 increases, and each structural part is mounted on the sleeve part 210 one by one.
  • the stepped shaft itself can form a number of limiting steps for axial positioning.
  • the stepped shaft is also provided with a number of convex edges 263 for axially limiting the shaft sleeve 80, bearings, etc.
  • a limiting structure 260 for axially limiting the actuator 40 is provided on the first installation position 230 to prevent the actuator 40 from Axial relative rotation occurs between the actuator 40 and the inner gear ring shaft 200.
  • the actuator 40 and the inner gear ring shaft 200 are splined, that is, the key connection structure of the first installation position 230 adopts an external spline, and the inner ring of the gear hub 41 and/or the combined tooth 42 of the actuator 40 is provided with an internal spline.
  • the actuator 40 and the inner gear ring shaft 200 are limited by a retaining spring 70, and the corresponding limiting structure 260 is a retaining spring groove 261 provided on the external spline, and the retaining spring 70 is stuck in the retaining spring groove 261 after the gear hub 41 and/or the combined tooth 42 of the actuator 40 are installed in place.
  • first support bearing 175 and the second support bearing 176 two support bearings are provided, namely, the first support bearing 175 and the second support bearing 176.
  • the first support bearing 175 and the second support bearing 176 can adopt ball bearings, needle bearings, thrust bearings, etc. Some embodiments adopt ball bearings.
  • the number of assembly positions 240 is correspondingly two, and both the gear sleeve part 221 and the shaft sleeve part 210 are provided with assembly positions 240.
  • the first support bearing 175 and the second support bearing 176 are respectively installed on the shaft sleeve part 210 and the cover part 220.
  • the first support bearing 175 is arranged in the inner hole of the cover part 220, and the second support bearing 176 is arranged between the first actuator S1 and the second actuator S2 through the shaft sleeve 80. Since the first support bearing 175 and the second support bearing 176 mainly play the role of supporting the inner gear ring shaft 200, they can both adopt ball bearings.
  • the first support bearing 175 is axially limited by the end surface 262 of the first mounting position 230, that is, the hole shoulder 264 formed by the first mounting position 230 and the supporting position of the cover part 220; the second support bearing 176 is axially limited by the boss provided on the sleeve 80.
  • the inner ring of the first support bearing 175 and the outer ring of the second support bearing 176 are respectively interference fit with the bearing mounting holes of the housing assembly 300.
  • the support bearing and the gear work in the form of rotation, and do not need to move axially, so they can be set on the cover part 220 and/or the sleeve part 210 according to actual needs.
  • the first support bearing 175 is installed on the assembly position 240 of the gear sleeve part 221, and the second support bearing 176 is installed on the assembly position 240 of the sleeve part 210.
  • FIG6 is a schematic diagram of the structure of the inner gear ring shaft in the engine input shaft assembly of FIG4 ;
  • FIG7 is a full cross-sectional view of the inner gear ring shaft of FIG6 .
  • the assembly position 240 of the cover part 220 is the inner hole wall 241 of the gear sleeve part 221
  • the assembly position 240 of the shaft sleeve part 210 is the bare rod section
  • the first support bearing 175 is interference fit with the inner hole wall 241
  • the second support bearing 176 is interference fit with the bare rod section.
  • a limiting structure 260 for axially limiting the first support bearing 175 is provided between the assembly position 240 of the gear sleeve part 221 and the installation position of the inner gear ring 150 , and the limiting structure 260 at this place can adopt end face limiting (such as shaft shoulder limiting, boss limiting) or retaining spring limiting.
  • end face limiting such as shaft shoulder limiting, boss limiting
  • retaining spring limiting As shown in FIG. 7 , in some embodiments, a hole shoulder 264 is formed between the inner hole wall 241 of the gear sleeve portion 221 and the inner spline 223 , and the hole shoulder 264 is used to axially limit the first support bearing 175 installed on the inner hole wall 241 .
  • a sleeve 80 is provided on the assembly position 240 of the sleeve portion 210, which can compensate for the diameter difference between the second support bearing 176 and the polished rod section on the one hand, and can be used for axial positioning of surrounding structural members on the other hand.
  • the sleeve 80 is press-fitted with the corresponding polished rod section by interference fit, and the second support bearing 176 is installed on the sleeve 80 by interference fit.
  • the surrounding structural members also play a role in axial positioning of the sleeve 80.
  • the engine input shaft assembly 610 is configured to meet the engine fourth gear, specifically, the engine fourth gear is achieved through two actuators 40 and two gear gears, the two actuators 40 and the two gear gears are respectively recorded as: the first actuator S1, the second actuator S2, the first gear gear 50 and the second gear gear 60.
  • the first actuator S1 and the second actuator S2 are both synchronizers, the first gear gear 50 is a large gear ring, and the engine third gear and the engine fourth gear are achieved; the second gear gear 60 is a small gear ring, and the engine first gear and the engine second gear are achieved.
  • the inner gear ring shaft 200 is provided with two first mounting positions 230, two assembly positions 240, and two second mounting positions 250.
  • the two first mounting positions 230 are distributed at both ends of the sleeve portion 210. It should be noted that the first mounting position 230 can be used to install all components of the actuator 40, or only part of the components of the actuator 40, such as only installing the gear hub 41 of the synchronizer or the single-sided coupling gear 42.
  • the two assembly positions 240 and the two second mounting positions 250 are respectively provided on the sleeve portion 210 and the cover portion 220, as shown in FIG6.
  • the first actuator S1 and the second actuator S2 are distributed at both ends of the sleeve portion 210.
  • the first actuator S1 and the second actuator S2 can use synchronizers (single or double) or clutches as needed.
  • the first actuator S1/the second actuator S2 can be set to selectively connect the sun gear shaft 110 and the inner gear ring shaft 200, selectively connect the planet carrier shaft 121 and the inner gear ring shaft 200, and selectively connect the inner gear ring shaft 200 and the first gear gear 50 according to actual needs.
  • the ring gear shaft 200 and the second gear gear 60 may be connected.
  • the first actuator S1 adopts a synchronizer, having a gear hub 41 and combining teeth 42 on both sides.
  • the gear hub 41 of the first actuator S1 is transmission-connected to the first mounting position 230; the combining teeth 42 on one side of the first actuator S1 are fixedly connected to the first gear gear 50; the combining teeth 42 on the other side of the first actuator S1 are fixedly connected to the second gear gear 60.
  • the first actuator S1 is used to optionally connect the inner ring shaft 200 to the first gear gear 50 or the second gear gear 60.
  • the second actuator S2 also uses a synchronizer, having a gear hub 41 and coupling teeth 42 on both sides.
  • the gear hub 41 of the second actuator S2 is transmission-connected to the sun gear shaft 110 of the planetary gear row 100, the coupling teeth 42 on one side of the second actuator S2 are transmission-connected to the shaft sleeve 210, and the coupling teeth 42 on the other side of the second actuator S2 are fixedly connected to the housing assembly 300.
  • the second actuator S2 is used to connect the sun gear shaft 110 to the inner gear ring shaft 200 or the housing assembly 300 to achieve different speed ratio outputs of the planetary gear row 100.
  • a thrust bearing is provided between the gear hub 41 of the second actuator S2 and the housing assembly 300, and the thrust bearing is sleeved on the sun gear shaft 110.
  • the first gear gear 50 and the second gear gear 60 are respectively installed at two second installation positions 250. Since the first gear gear 50 and the second gear gear 60 are both loosely sleeved on the inner gear ring shaft 200, the inner holes of the first gear gear 50 and the second gear gear 60 are both installed with bearings, such as ball bearings, as shown in FIG4. In some embodiments, if the gears are in transmission connection with the inner gear ring shaft 200, no bearings are required.
  • the gear sleeve portion 221 and the shaft sleeve portion 210 are both provided with second installation positions 250, that is, the first gear gear 50 is loosely sleeved on the gear sleeve portion 221 through a bearing, and the second gear gear 60 is loosely sleeved on the shaft sleeve portion 210 through a bearing.
  • the first gear 50 and the second gear 60 are both gear rings.
  • the first gear 50 is sleeved on the cover portion 220 through a needle bearing 177a
  • the second gear 60 is sleeved on the shaft sleeve portion 210 through a needle bearing 177c and is located between the first actuator S1 and the second support bearing 176.
  • Both the first gear 50 and the second gear 60 can rotate freely relative to the inner gear ring shaft 200.
  • the first gear 50 is a large gear ring, and the inner diameter of the first gear 50 is larger than that of the second gear 60.
  • the first gear gear 50 must not only meet the diameter requirement of being able to be sleeved on the cover part 220, but also meet the connection with the first actuator S1 installed on the sleeve part 210. Therefore, the first gear gear 50 is specifically configured to include a ring gear part 51 and a connecting part 52.
  • the ring gear part 51 is similar in structure to the sleeve part 221 of the inner gear ring shaft 200, both of which are sleeve structures.
  • the connecting part 52 is similar in structure to the baffle part 222 of the inner gear ring shaft 200, both of which are annular plate structures.
  • the ring gear part 51 and the connecting part 52 can be an integrally formed structure, or connected and fixed by welding or threaded fasteners.
  • the ring gear part 51 is sleeved on the cover part 220 through a needle bearing 177a, and the bearing is axially limited by a convex edge 263 provided on the outer surface of the cover part 220.
  • the connecting part 52 is fixedly connected to the coupling tooth 42 on one side of the first actuator S1.
  • the connecting part 52 and the coupling tooth 42 of the first actuator S1 can be integrally formed, welded, or transmission-connected.
  • the second gear 60 is fixedly connected to the coupling tooth 42 on the other side of the first actuator S1 , and the second gear 60 and the coupling tooth 42 of the first actuator S1 can be integrally formed, welded, or transmission-connected.
  • the second gear 60 is axially limited by the sleeve 80 of the second support bearing 176 .
  • a thrust bearing 178 is provided between the connecting portion 52 and the cover portion 220, specifically, a thrust bearing 178 is provided between the connecting portion 52 and the baffle portion 222. That is, the first gear position gear 50 is sleeved on the inner gear ring shaft 200 through the needle bearing 177a and the thrust bearing 178, and is axially limited by the thrust bearing 178 and the end face 262 outside the baffle portion 222.
  • the cover portion 220 of the inner gear ring shaft 200 is provided with an oil guide hole 270 that penetrates the wall thickness, so that the lubricating oil splashed in the planetary gear 100 can enter the gap between the first gear position gear 50 and the cover portion 220 through the oil guide hole 270 on the cover portion 220, and lubricate the needle bearing 177a and the thrust bearing 178 therein.
  • the lubrication requirements of the multiple bearings and gears need to be guaranteed. Specifically, splash lubrication or active lubrication can be used. Since the bearings and gears of the inner ring shaft 200 are compactly arranged and form an axial limiting effect on each other, it may be difficult to achieve the expected lubrication effect only by external splashing lubricating oil. Therefore, some embodiments adopt an active lubrication solution.
  • the shaft sleeve 210 is provided with at least one oil guide hole 270 penetrating the sleeve wall of the shaft sleeve 210.
  • the oil guide holes 270 are usually arranged in a plurality along the circumferential direction.
  • the plurality of oil guide holes 270 located in the same cross section are grouped together.
  • the shaft sleeve 210 may be provided with a plurality of groups of oil guide holes 270 along its axial direction.
  • the outer surface of the shaft sleeve 210 is provided with an oil guide groove 280 connected to the oil guide hole 270.
  • the oil guide groove 280 is connected to a group of oil guide holes 270.
  • the specific number of the oil guide grooves 280 is determined according to the embodiment of the present invention.
  • the oil guide groove 280 is a concave groove, and the lubricating oil flowing out of the oil guide hole 270 can be evenly distributed along the circumference by setting the oil guide groove 280.
  • the oil guide groove 280 is a groove, the groove can also be used as a backing groove when machining the outer surface of the inner gear ring shaft 200.
  • the cover portion 220 may also be provided with an oil guide hole 270, which may be selectively provided on the gear sleeve portion 221 and/or the baffle portion 222 to facilitate the lubricating oil to enter and exit the inner hole of the cover portion 220.
  • the baffle portion 222 may be provided with a plurality of oil guide holes 270, which are arranged to be inclined outwardly along the splashing direction, so that the splashed lubricating oil is thrown out from the oil guide hole 270 when the planetary gear 100 rotates, and lubricating the external structural parts of the inner gear ring shaft 200.
  • the planetary gear 100 is the main component for power distribution.
  • the lubrication of the planetary gear 100 is an important condition for ensuring the normal operation of the engine input shaft assembly 610.
  • the main lubrication requirement of the planetary gear 100 is the planetary gear bearing 171.
  • the number of planetary gear bearings 171 is large and the distribution is wide.
  • the installation position of the planetary gear bearing 171 is located in the area surrounded by the planetary carrier 120 and between the planetary gear 140 and the planetary gear shaft 123, it is blocked by the planetary gear 140 and the planetary carrier 120, and it is difficult for lubricating oil to enter the installation position of the planetary gear bearing 171. Therefore, the planetary gear bearing 171 is prone to ablation, affecting the use of the entire planetary gear 100.
  • FIG5 is a schematic diagram of the structure of the internal lubrication channel of the engine input shaft assembly of FIG4.
  • the planetary gear 100 is provided with a lubrication channel 160
  • the sun gear shaft 110 of the planetary gear 100 is provided with a first hollow cavity 111 that penetrates along the axial direction, and the sun gear shaft 110 can be integrally formed with the sun gear 130 of the planetary gear 100, or key-connected.
  • the sun gear shaft 110 is integrally formed with the sun gear 130.
  • the planet carrier 120 of the planetary gear 100 is provided with an oil collecting cavity 124, and the first hollow cavity 111, the oil collecting cavity 124 and the lubrication channel 160 are connected in sequence, and the outlet of the lubrication channel 160 faces the planetary gear bearing 171 of the planetary gear 100.
  • the sun gear shaft 110 is provided with a plurality of fourth oil guide holes 112 connected to the first hollow cavity 111, and the outlet of a fourth oil guide hole 112 among the plurality of fourth oil guide holes 112 faces the bearing between the sun gear shaft 110 and the inner ring shaft 200.
  • the lubrication channel 160 of the planetary carrier 120 may be an oil channel opened in the base material of the planetary carrier 120, or may be an oil channel formed by enclosing external components, as long as the lubricating oil can be delivered to the installation location of the planetary gear bearing 171.
  • the planetary gear bearing 171 is a needle bearing, specifically a full needle bearing or a steel cage needle bearing.
  • the planetary gear bearing 171 adopts a double-row needle bearing with a gasket in the middle. The gasket should form a gap with the planetary gear shaft 123 in the radial direction to ensure that the lubricating oil can enter the needle bearing and lubricate the roller surface of the needle bearing.
  • the planet carrier 120 may include a planet carrier shaft 121, a connecting plate 122, and a plurality of planetary gear shafts 123 connected in sequence, the planetary gear 140 is sleeved on the planetary gear shaft 123, a planetary gear bearing 171 is installed between the planetary gear 140 and the planetary gear shaft 123, and the two sides of the planetary gear 140 are respectively meshed with the gear of the sun gear 130 and the gear of the inner gear ring 150 through gears.
  • the planetary carrier shaft 121 is located at the center of the connecting plate 122, and the planetary gear shafts 123 are evenly distributed along the circumference with the planetary carrier shaft 121 as the center.
  • the planetary carrier shaft 121 and the connecting plate 122 can be detachably connected by threaded fasteners, snap-fit structures, etc., or fixed by welding, or the planetary carrier shaft 121 and the connecting plate 122 are an integrated structure. In some embodiments, the planetary carrier shaft 121 is pressed onto the connecting plate 122 by interference fit.
  • the connecting plate 122 and the planetary gear shaft 123 can also be detachably connected by threaded fasteners, snap-fit structures, etc., or welded and fixed, or the connecting plate 122 and the planetary gear shaft 123 are an integrated structure, which is not limited in the present disclosure.
  • the overall external shape and profile of the planetary carrier 120 are also not limited in the present disclosure, for example, the planetary carrier 120 can adopt a cage structure.
  • the planet carrier shaft 121 is provided with a connected oil collecting chamber 124 and a first oil guide hole 125.
  • the oil collecting chamber 124 is located at the center of the planet carrier shaft 121, preferably coaxial with the planet carrier shaft 121.
  • the planetary gear shaft 123 is provided with a second oil guide hole 126, and the outlet of the second oil guide hole 126 faces the planetary gear bearing 171 of the planetary gear row 100.
  • An oil guide member 20 is provided on the outer side of the connecting plate 122.
  • the first oil guide hole 125, the gap between the oil guide member 20 and the connecting plate 122, and the second oil guide hole 126 are connected in sequence to form a lubrication channel 160.
  • the oil guide member 20 is riveted to the planet carrier 120, and the oil guide member 20 guides the lubricating oil in the oil collecting chamber 124 that is thrown out from the first oil guide hole 125 under the action of centrifugation to the second oil guide hole 126.
  • an intermediate bearing 174 is provided between the planet carrier shaft 121 and the sun gear shaft 110.
  • the intermediate bearing 174 is a thrust bearing that can withstand a large axial force.
  • One end of the sun gear shaft 110 is against the planet carrier shaft 121 through the thrust bearing.
  • the thrust bearing can meet the working requirements of the planetary gear 100 when there is a speed difference between the planet carrier 120 and the sun gear shaft 110 under certain working conditions.
  • the intermediate bearing 174 is specifically located at the end of the sun gear shaft 110. In some embodiments, the intermediate bearing 174 can be located at the end of the sun gear shaft 110.
  • An inwardly concave bearing mounting groove 113 is provided at the end of the male wheel shaft 110 , and the bearing mounting groove 113 is connected to the first hollow cavity 111 , thereby making the internal gap of the intermediate bearing 174 connected to the first hollow cavity 111 , and the lubricating oil in the first hollow cavity 111 can enter the intermediate bearing 174 .
  • the second oil guide hole 126 may be a channel extending radially and/or axially along the planetary gear shaft 123, or may be a channel extending circumferentially along the planetary gear shaft 123, that is, the second oil guide hole 126 may be an axial straight channel, a radial straight channel, an oblique straight channel, a curved channel, etc., which is not limited in the present disclosure. As shown in FIG.
  • the second oil guide hole 126 includes an axial oil guide hole 1261 extending axially along the planetary gear shaft 123 and at least one radial oil guide hole 1262 extending radially along the planetary gear shaft 123, and the outlet of the radial oil guide hole 1262 constitutes the outlet of the lubrication channel 160.
  • the number of radial oil guide holes 1262 is determined according to the size of the planetary gear bearing 171, and is usually set to more than two. The outlets of the more than two radial oil guide holes 1262 are spaced and evenly distributed along the circumferential surface of the planetary gear shaft 123.
  • the second oil guide hole 126 includes an axial oil guide hole 1261 extending axially along the planetary gear shaft 123 and four radial oil guide holes 1262 extending radially along the planetary gear shaft 123.
  • the four radial oil guide holes 1262 are distributed at 90 degrees to each other to ensure that the oil reaches the planetary gear bearing 171 and avoid sintering of the entire planetary gear row 100 due to insufficient lubrication of the planetary gear bearing 171.
  • the inlet of the axial oil guide hole 1261 is set to be a flared port, and the flared port is preferably a circular flared port to reduce flow resistance.
  • the aperture of the flared port gradually increases from the middle to the end, so as to facilitate the entry of lubricating oil into the axial oil guide hole 1261.
  • a first planetary carrier bearing 172 is mounted on the planetary carrier 120, and the first planetary carrier bearing 172 is arranged in the lubrication channel 160, and the internal gap of the first planetary carrier bearing 172 is connected to the lubrication channel 160 for the circulation of lubricating oil. As shown in FIG5 , the first planetary carrier bearing 172 is mounted on the planetary carrier shaft 121 and is close to the connecting plate 122 of the planetary carrier 120.
  • the first planetary carrier bearing 172 is a thrust bearing, and the loose ring of the thrust bearing is in contact with the connecting plate 122, and the tight ring of the thrust bearing is connected and/or in contact with an external fixed member (for example, a housing assembly 300 for mounting the planetary gear 100), so that the planetary gear 100 is axially stable.
  • a channel for the circulation of lubricating oil can be formed between the loose ring and the tight ring, and the roller of the thrust bearing can also be lubricated when the lubricating oil circulates between the loose ring and the tight ring.
  • the first planetary carrier bearing 172 can also be arranged at other positions of the planetary carrier 120, and completely separated from the lubrication channel 160, so as to avoid the internal structure of the first planetary carrier bearing 172 from generating flow resistance.
  • a second planet carrier bearing 173 is further installed on the planet carrier shaft 121, and the second planet carrier bearing 173 adopts a needle bearing.
  • the planet carrier 120 is installed in the housing through the second planet carrier bearing 173.
  • the second planet carrier bearing 173 also needs lubrication during operation.
  • the planet carrier shaft 121 is provided with a third oil guide hole 127 connected to the oil collecting chamber 124, and the outlet of the third oil guide hole 127 faces the second planet carrier bearing 173.
  • the oil collecting chamber 124 is required to accommodate the end of the oil guide pipe 10 near the planetary row 100, and store a certain amount of oil to be transported to the third oil guide hole 127.
  • the oil collecting chamber 124 has a stepped hole structure, wherein the large hole section 1241 is used to accommodate the end of the oil guide pipe 10 near the planetary row 100, and the small hole section 1242 is connected to the third oil guide hole 127.
  • the sun gear shaft 110 is embedded with an oil guide pipe 10, and the oil guide pipe 10 is installed through the sun gear shaft 110 of the planetary gear row 100, specifically, it is installed through the first hollow cavity 111, and the end of the oil guide pipe 10 near the planetary gear row 100 extends into the oil collecting cavity 124 to guide the oil in the sun gear shaft 110 into the oil collecting cavity 124 of the planetary gear row.
  • the oil guide pipe 10 when the axial oil guide channel is relatively long, the oil guide pipe 10 is used to transfer the lubricating oil from the lubricating oil inlet at the end of the far planetary gear 100 to the planetary carrier 120 of the planetary gear 100, so as to avoid the situation that the oil is thrown out and cannot reach the planetary gear 100 due to the centrifugal force formed by the high-speed operation of the sun gear shaft 110, and the near planetary gear end of the oil guide pipe 10 extends into the oil collecting chamber 124, which can reduce the leakage of the lubricating oil at the gap between the sun gear shaft 110 and the planetary carrier 120.
  • the lubricating oil circulates in the lubrication channel 160 and finally flows to the planetary gear bearing 171 to lubricate the bearings of each planetary gear 140, ensure sufficient oil volume of the bearing, and avoid the safety problem of the whole vehicle caused by the ablation of the entire planetary gear 100.
  • the oil guide pipe 10 is provided with a plurality of oil outlet holes 11 spaced apart along the axial direction and/or radial direction of the oil guide pipe 10. There are usually a plurality of oil outlet holes 11 along the axial direction of the oil guide pipe, and the diameter and hole spacing of each oil outlet hole 11 are the same.
  • the oil outlet holes 11 may also be provided in a plurality, and the plurality of oil outlet holes 11 located at the same axial position are spaced apart along the circumferential direction, so that the oil can flow evenly into the first hollow cavity 111 of the sun gear shaft 110.
  • An additional oil outlet hole 11 may be provided at the axial position of the oil guide pipe 10 corresponding to the installation position of the bearing.
  • the distal planetary gear 100 end of the oil guide tube 10 is provided with more than one oil outlet 12. Since the oil outlet 12 is provided on the tube wall of the oil guide tube 10, oil can be discharged radially, reducing resistance and facilitating oil to enter the lubrication channel 160.
  • the oil outlet 12 can be set as a slot with an opening or a complete hole, for example, the oil outlet 12 can be a U-shaped slot or a circular hole.
  • the number of the oil outlets 12 is not limited in the present disclosure. For example, if the number of the oil outlets 12 is set to 3, the shapes of the 3 oil outlets 12 can be the same or different.
  • At least one bushing 30 is sleeved on the oil guiding tube 10, and the bushing 30 fills the gap between the oil guiding tube 10 and the cavity wall of the first hollow cavity 111.
  • the bushing 30 plays a role in supporting the oil guiding tube 10, and the material of the bushing 30 is copper or composite plastic.
  • the sun gear shaft 110 of the engine input shaft assembly 610 is rotatably connected to the rotor 621 of the generator 620, as shown in Figure 4.
  • the rotor 621 of the generator 620 is provided with a second hollow cavity 622 that penetrates along the axial direction, and the second hollow cavity 622 is connected to the first hollow cavity 111.
  • the rotor of the generator 620 is coaxially arranged with the planetary row 100.
  • the lubricating oil introduced into the oil inlet channel 303 of the housing assembly 300 is introduced into the first hollow cavity 111 of the planetary row 100 through the second hollow cavity 622.
  • the oil guide pipe 10 of the planetary row lubrication structure is installed in the second hollow cavity 622 and the first hollow cavity 111.
  • the far planetary row 100 end of the oil guide pipe 10 is directly connected to the oil inlet channel 303 of the housing assembly 300, and the near planetary row 100 end of the oil guide pipe 10 is directly connected to the oil collecting chamber 124 of the planetary carrier 120.
  • the rotor of the generator 620 By connecting the rotor of the generator 620 to the internal oil circuit of the planetary gear 100, the rotor of the motor acts as a pipeline for lubricating oil, which simplifies the structure of the lubrication system and improves the integration and vehicle mountability of the hybrid electric drive system 1000.
  • a hybrid electric drive system 1000 is provided according to a second aspect of the present disclosure.
  • FIG8 is an overall structural diagram of a hybrid electric drive system according to some embodiments of the present disclosure
  • FIG9 is a structural schematic diagram of the hybrid electric drive system of FIG8 after removing the end cover
  • FIG10 is a structural schematic diagram of the hybrid electric drive system of FIG8 after removing the right housing.
  • the hybrid electric drive system 1000 may include a housing assembly 300, a shift mechanism assembly 500, and the hybrid transmission mechanism assembly 600, and the shift mechanism assembly 500 and the hybrid transmission mechanism assembly 600 are both installed in the housing assembly 300.
  • the housing assembly 300 is provided with a shaft gear cavity 302 and a motor cavity 301
  • the generator 620 and the drive motor 670 of the hybrid transmission mechanism assembly 600 are both installed in the motor cavity 301
  • the shift mechanism assembly 500 and the engine input shaft assembly 610, the drive motor input shaft assembly 660, the ICE intermediate shaft assembly 630, the EV intermediate shaft assembly 650 and the differential shaft assembly 640 of the hybrid transmission mechanism assembly 600 are all installed in the shaft gear cavity 302.
  • the housing assembly 300 adopts a split structure.
  • the specific division method is not limited in this disclosure.
  • the housing assembly 300 can be divided in a horizontal plane to form two upper and lower housings, or divided in a vertical plane to form three left, middle and right housings.
  • the housing assembly 300 includes a right housing 310, a left housing 320 and an end cover 330 connected in sequence.
  • the right housing 310 and the left housing 320 enclose a shaft gear cavity 302.
  • the left housing 320 and the end cover 330 enclose a motor cavity 301, and the generator 620 and the drive motor 670 are both located in the motor cavity 301.
  • the left housing 320 is provided with an intermediate plate 321, and the intermediate plate 321 is a cover body, which is fixedly connected to the left housing 320 by threaded fasteners or welding.
  • the intermediate plate 321 is installed with a ball bearing 179 for supporting the rotor 621 of the generator 620, as shown in FIG. 4.
  • the coupling teeth 42 of the second actuator S2 are fixedly connected to the intermediate plate 321, and specifically, the coupling teeth 42 of the second actuator S2 can be directly processed on the intermediate plate 321. In some embodiments, the coupling teeth 42 of the second actuator S2 can also be welded or interference-pressed on the intermediate plate 321.
  • FIG11 is a schematic diagram of the structure of the middle plate of the hybrid electric drive system of FIG8.
  • the middle plate 321 is provided with a bearing hole 3211 for setting a bearing and an avoidance area 3212 for avoiding the shift fork of the shift mechanism assembly 500.
  • the middle plate 321 can be provided with a bearing, and a certain installation space can be formed between the middle plate 321 and the left housing 320.
  • a shift fork installation position can be set between the middle plate 321 and the left housing 320, and the shift fork can be installed in the shift fork installation position through the avoidance area 3212 on the middle plate 321, making the installation of the shift fork more convenient.
  • a bearing hole 3211 is provided on the middle plate 321 for setting the bearing of the rotor of the generator 620, increasing the number of bearing installation holes of the entire left housing 320.
  • the rotor 621 of the generator 620 is supported on the middle plate 321 and the end cover 330 by two bearings, and the planetary carrier shaft 121 of the planetary gear 100 is supported on the right housing 310 by the first planetary carrier bearing 172 and the second planetary carrier bearing 173.
  • the bottom of the left housing 320 forms an oil pan, and the lubricating oil falls into the oil pan after lubricating the hybrid transmission mechanism assembly 600.
  • An oil inlet channel 303 is provided in the end cover 330, and the oil inlet channel 303 is connected to the second hollow cavity 622 of the rotor 621 of the generator 620.
  • the lubricating oil is pumped by an external oil pump, so that the lubricating oil circulates in the oil pan, the oil inlet channel 303, the oil guide pipe 10 (or the second hollow cavity 622 and the first hollow cavity 111), and the lubrication channel 160.
  • the hybrid electric drive system 1000 also includes a controller assembly 400, which is used to control the operation of the motor and the shift mechanism assembly 500.
  • the controller assembly 400 can also control the operation of electronic devices such as the oil pump and some sensors (temperature sensors, pressure sensors, etc.) set inside the hybrid electric drive system 1000.
  • the controller assembly 400 can be set separately from the housing assembly 300 and connected by wires. As shown in Figure 8, in some embodiments, the controller assembly 400 is installed on the housing assembly 300, and the controller assembly 400 is provided with a control board, a drive board and an IGBT for controlling the generator 620 and the drive motor 670.
  • the controller assembly 400 has three output copper bars for electrical connection with the three-phase input copper bars of the generator 620 and the drive motor 670.
  • the controller assembly 400 also has a low-voltage wiring harness for connecting low-voltage equipment (sensors, pumps, etc.) on the housing assembly 300 or inside the housing assembly 300.
  • the specific structure of the controller assembly 400 can refer to the relevant disclosure of the prior art, and the present disclosure is not limited.
  • a vehicle is provided according to the third aspect of the present disclosure, which may include the hybrid electric drive system 1000, that is, the vehicle is a hybrid vehicle, powered by an engine and a motor. Since the vehicle is equipped with the hybrid electric drive system 1000, it at least has all the beneficial effects brought by the technical solution of the hybrid electric drive system 1000.
  • the hybrid electric drive system 1000 has high integration and small size, and can be installed in the engine compartment of vehicles of different models. Other undetailed structures of the vehicle can refer to the relevant disclosure of the prior art, and will not be described here.
  • the hybrid transmission mechanism assembly includes an engine input shaft assembly, a generator, an ICE intermediate shaft assembly, a differential shaft assembly, an EV intermediate shaft assembly, a drive motor input shaft assembly and a drive motor that are transmission-connected.
  • the engine input shaft assembly is transmission-connected to the engine, and the engine input shaft assembly is provided with a planetary gear, an actuator and a gear gear, so that gear shifting can be achieved. That is, the hybrid transmission mechanism assembly of the present disclosure can achieve hybrid power input of the engine + motor, and multi-gearing of the hybrid engine.
  • the hybrid transmission mechanism assembly has an engine input shaft assembly coaxially arranged with the generator, a drive motor input shaft assembly coaxially arranged with the drive motor, and the generator and the drive motor are located on the same side.
  • the motor assembly and the shaft gear assembly can be placed separately, thereby facilitating the design of the cooling and lubrication system and the high and low pressure partitioning.
  • the present disclosure adopts a technical solution of coaxially arranging the motor and the input shaft, which can reduce the one-way size of the hybrid transmission mechanism assembly.
  • the installation height of the engine input shaft assembly is located between the drive motor and the differential shaft assembly, and the projection of the engine input shaft assembly on the vertical plane overlaps with the projection of the drive motor and the differential shaft assembly on the vertical plane.
  • the axis of the engine input shaft assembly, the axis of the drive motor and the axis of the differential shaft assembly of the hybrid transmission mechanism assembly are distributed in a triangular shape, which can not only reduce the one-way size of the hybrid transmission mechanism assembly, but also the triangular distribution structure is stable, and the triangular distribution can provide installation space for the ICE intermediate shaft assembly and the EV intermediate shaft assembly.
  • the above structural design can reduce the size of the hybrid transmission mechanism assembly on a plane perpendicular to the axis of the engine input shaft.
  • the hybrid transmission mechanism assembly provided by the present disclosure has an inner gear ring shaft, which can be sleeved outside the planetary gear and is drivingly connected to the inner gear ring of the planetary gear.
  • the inner gear ring shaft is installed on the housing assembly through a support bearing, and multiple component installation positions can be set on it.
  • the actuator, support bearing and gear are all installed and fixed through the inner gear ring shaft.
  • the hybrid transmission mechanism assembly compared with the existing hybrid transmission, can reduce the size along the axial direction of the engine input shaft and on the plane perpendicular to the axis of the engine input shaft through the position design of the internal assembly, and by providing an inner ring shaft on the engine input shaft assembly, the planetary gear transmission function, actuator installation, gear gear installation and necessary axial limit function can be integrated at the same time, thereby greatly improving the integration of the hybrid transmission mechanism assembly, reducing the functional volume of the hybrid transmission mechanism assembly in the axial direction, so that it has more flexible layout and mounting performance.

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Abstract

A hybrid power transmission assembly (600), comprising an engine input shaft assembly (610), a generator (620), an ICE countershaft assembly (630), a differential shaft assembly (640), an EV countershaft assembly (650), a drive motor input shaft assembly (660), and a drive motor (670). Also disclosed are a hybrid electric drive system (1000) and a vehicle.

Description

一种混合动力变速机构总成、混合动力电驱动***和车辆A hybrid power transmission mechanism assembly, a hybrid power electric drive system and a vehicle
相关申请的交叉引用CROSS-REFERENCE TO RELATED APPLICATIONS
本申请要求于2022年10月24日提交的申请号为202211305951.0的中国专利申请的优先权，其全部内容通过引用并入本文。This application claims priority to Chinese patent application No. 202211305951.0 filed on October 24, 2022, the entire contents of which are incorporated herein by reference.
技术领域Technical Field
本公开属于混合动力变速箱技术领域，具体涉及一种混合动力变速机构总成、混合动力电驱动***和车辆。The present invention belongs to the technical field of hybrid power transmissions, and in particular relates to a hybrid power transmission mechanism assembly, a hybrid power electric drive system and a vehicle.
背景技术Background technique
随着当今社会人们对节能环保的意识日渐增强，新能源汽车技术开始迅猛发展。混合动力车辆驱动技术是新能源汽车发展过程的核心阶段。提高燃油经济性、降低排放是混合动力技术面临的重要课题。目前市场上主流混动电驱动产品还是双电机单档混动居多，可实现纯电、串联/驻车发电和并联/发动机直驱等工作模式，并同时适配HEV和PHEV车型。随着油耗及排放法规的加严，混动发动机多档化已成为发展趋势。由于挡位数量的增多，整个动力传动装置的结构也变得复杂，整个动力传动装置的结构变得庞大，整个轴向尺寸也会因此而增加。As people's awareness of energy conservation and environmental protection in today's society increases, new energy vehicle technology has begun to develop rapidly. Hybrid vehicle drive technology is the core stage of the development process of new energy vehicles. Improving fuel economy and reducing emissions are important issues facing hybrid technology. At present, the mainstream hybrid electric drive products on the market are still mostly dual-motor single-speed hybrids, which can achieve pure electric, series/parking power generation and parallel/engine direct drive and other working modes, and are suitable for HEV and PHEV models at the same time. With the tightening of fuel consumption and emission regulations, multi-speed hybrid engines have become a development trend. Due to the increase in the number of gears, the structure of the entire power transmission device has become complicated, the structure of the entire power transmission device has become huge, and the entire axial size will also increase.
发明内容Summary of the invention
为解决上述技术问题，本公开提供一种混合动力变速机构总成、混合动力电驱动***和车辆，能够缩小总成体积，提高搭载性能，满足更灵活的布置方式。In order to solve the above technical problems, the present disclosure provides a hybrid transmission mechanism assembly, a hybrid electric drive system and a vehicle, which can reduce the assembly volume, improve the mounting performance and meet a more flexible layout.
依据本公开的第一方面提供了一种混合动力变速机构总成，包括传动连接的发动机输入轴总成、发电机、ICE中间轴总成、差速器轴总成、EV中间轴总成、驱动电机输入轴总成和驱动电机；其中所述发动机输入轴总成与所述发电机同轴设置，所述驱动电机输入轴总成和所述驱动电机同轴设置；所述发电机和所述驱动电机位于同侧；所述发动机输入轴总成的安装高度位于所述驱动电机与所述差速器轴总成之间，且所述发动机输入轴总成在竖直面上的投影与所述驱动电机和所述差速器轴总成在竖直面上的投影具有重合部分；所述发动机输入轴总成包括行星排、至少一个执行机构、至少一个支撑轴承、至少一个挡位齿轮和内齿圈轴；所述内齿圈轴套设于所述行星排外，且所述内齿圈轴与所述行星排的内齿圈传动连接；所述至少一个执行机构、所述至少一个支撑轴承、所述至少一个挡位齿轮均设置于所述内齿圈轴上。According to a first aspect of the present disclosure, a hybrid transmission mechanism assembly is provided, comprising an engine input shaft assembly, a generator, an ICE intermediate shaft assembly, a differential shaft assembly, an EV intermediate shaft assembly, a drive motor input shaft assembly and a drive motor that are transmission-connected; wherein the engine input shaft assembly is coaxially arranged with the generator, and the drive motor input shaft assembly is coaxially arranged with the drive motor; the generator and the drive motor are located on the same side; the installation height of the engine input shaft assembly is located between the drive motor and the differential shaft assembly, and the projection of the engine input shaft assembly on the vertical plane has an overlapping part with the projection of the drive motor and the differential shaft assembly on the vertical plane; the engine input shaft assembly comprises a planetary row, at least one actuator, at least one support bearing, at least one gear gear and an inner ring shaft; the inner ring shaft is sleeved outside the planetary row, and the inner ring shaft is transmission-connected with the inner ring of the planetary row; the at least one actuator, the at least one support bearing and the at least one gear gear are all arranged on the inner ring shaft.
依据本公开的第二方面还提供一种混合动力电驱动***，包括：壳体总成，设有轴齿腔和电机腔；上述的混合动力变速机构总成，所述混合动力变速机构总成中，发动机输入轴总成、所述驱动电机输入轴总成、所述ICE中间轴总成、所述EV中间轴总成和所述差速器轴总成均安装于所述轴齿腔中，所述发电机和所述驱动电机均安装于所述电机腔中；换挡机构总成，安装于所述轴齿腔中，且作用于所述执行机构。According to the second aspect of the present disclosure, a hybrid electric drive system is also provided, including: a housing assembly, provided with a shaft gear cavity and a motor cavity; the above-mentioned hybrid power transmission mechanism assembly, in which the engine input shaft assembly, the drive motor input shaft assembly, the ICE intermediate shaft assembly, the EV intermediate shaft assembly and the differential shaft assembly are all installed in the shaft gear cavity, and the generator and the drive motor are both installed in the motor cavity; a shift mechanism assembly, installed in the shaft gear cavity, and acting on the actuator.
依据本公开的第三方面还提供一种车辆，包括上述的混合动力电驱动***。According to a third aspect of the present disclosure, a vehicle is also provided, comprising the above-mentioned hybrid electric drive system.
附图说明BRIEF DESCRIPTION OF THE DRAWINGS
为了更清楚地说明本公开实施方式中的技术方案，下面将对实施方式描述中所需要使用的附图作简单的介绍。显而易见地，下面描述中的附图仅仅是本公开的一些实施方式，对本领域技术人员来说，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。In order to more clearly illustrate the technical solutions in the embodiments of the present disclosure, the following briefly introduces the drawings required for the description of the embodiments. Obviously, the drawings described below are only some embodiments of the present disclosure, and those skilled in the art can obtain other drawings based on these drawings without creative work.
为了更完整地理解本公开及其有益效果，下面将结合附图来进行说明。其中，在下面 的描述中相同的附图标号表示相同部分。In order to more fully understand the present disclosure and its beneficial effects, the following will be described in conjunction with the accompanying drawings. The same drawing numbers in the description denote the same parts.
图1为依据本公开一些实施例的混合动力变速机构总成的结构示意图；FIG1 is a schematic structural diagram of a hybrid transmission mechanism assembly according to some embodiments of the present disclosure;
图2为图1的混合动力变速机构总成在某一视角下的结构示意图；FIG2 is a schematic structural diagram of the hybrid power transmission mechanism assembly of FIG1 at a certain viewing angle;
图3为图1的混合动力变速机构总成在另一视角下的结构示意图；FIG3 is a schematic structural diagram of the hybrid power transmission mechanism assembly of FIG1 from another perspective;
图4为图1的混合动力变速机构总成中发动机输入轴总成的全剖图；FIG4 is a full cross-sectional view of the engine input shaft assembly in the hybrid transmission mechanism assembly of FIG1 ;
图5为图4的发动机输入轴总成的内部润滑通道的结构示意图；FIG5 is a schematic structural diagram of an internal lubrication passage of the engine input shaft assembly of FIG4 ;
图6为图4的发动机输入轴总成中内齿圈轴的结构示意图；FIG6 is a schematic structural diagram of the inner ring gear shaft in the engine input shaft assembly of FIG4 ;
图7为图6的内齿圈轴的全剖图；FIG7 is a full cross-sectional view of the inner gear ring shaft of FIG6;
图8为依据本公开一些实施例的混合动力电驱动***的整体结构图；FIG8 is an overall structural diagram of a hybrid electric drive system according to some embodiments of the present disclosure;
图9为图8的混合动力电驱动***拆除端盖后的结构示意图；FIG9 is a schematic diagram of the structure of the hybrid electric drive system of FIG8 after the end cover is removed;
图10为图8的混合动力电驱动***拆除右壳体后的结构示意图；以及FIG10 is a schematic diagram of the structure of the hybrid electric drive system of FIG8 after the right housing is removed; and
图11为图8的混合动力电驱动***的中间板的结构示意图。FIG. 11 is a schematic structural diagram of the middle plate of the hybrid electric drive system of FIG. 8 .
附图标记说明：
1000-混合动力电驱动***；300-壳体总成；301-电机腔；302-轴齿腔；303-进油通道；
310-右壳体；320-左壳体，321-中间板，3211-轴承孔，3212-避让区；330-端盖；400-控制器总成；500-换挡机构总成。
600-混合动力变速机构总成；610-发动机输入轴总成；620-发电机，621-发电机的转子，
622-第二中空腔；630-ICE中间轴总成，631-ICE中间轴，632-第一ICE中间齿轮，633-第二ICE中间齿轮；640-差速器轴总成；650-EV中间轴总成，651-EV中间轴，652-第一EV中间齿轮，653-第二EV中间齿轮；660-驱动电机输入轴总成，661-输入轴，662-传动齿轮；670-驱动电机，671-驱动电机的转子。
200-内齿圈轴，201-内孔；210-轴套部；220-罩部，221-齿套部，222-挡板部，223-内
花键；230-第一安装位；240-装配位，241-内孔壁；250-第二安装位；260-限位结构，261-卡簧槽，262-端面，263-凸边，264-孔肩；270-导油孔；280-导油槽。
100-行星排；110-太阳轮轴，111-第一中空腔，1111-储油腔，1112-扩孔段，112-第四
导油孔，113-轴承安装槽；120-行星架，121-行星架轴，122-连接板，123-行星轮轴，124-集油腔，1241-大孔段，1242-小孔段，125-第一导油孔，126-第二导油孔，1261-轴向导油孔，1262-径向导油孔，127-第三导油孔；130-太阳轮；140-行星轮；150-内齿圈；160-润滑通道；171-行星轮轴承；172-第一行星架轴承；173-第二行星架轴承；174-中间轴承；175-第一支撑轴承；176-第二支撑轴承；177a-用于安装第一挡位齿轮的滚针轴承，177b-用于安装内齿圈轴的滚针轴承，177c-用于安装第二挡位齿轮的滚针轴承；178-推力轴承；179-球轴承。
10-导油管，11-出油孔，12-出油口；20-导油件；30-衬套；40-执行机构，41-齿毂，42-
结合齿，S1-第一执行机构，S2-第二执行机构；50-第一挡位齿轮，51-齿圈部，52-连接部；60-第二挡位齿轮；70-卡簧；80-轴套。Description of reference numerals:
1000-hybrid electric drive system; 300-housing assembly; 301-motor cavity; 302-shaft gear cavity; 303-oil inlet channel;
310 - right housing; 320 - left housing, 321 - middle plate, 3211 - bearing hole, 3212 - avoidance area; 330 - end cover; 400 - controller assembly; 500 - shift mechanism assembly.
600-hybrid power transmission assembly; 610-engine input shaft assembly; 620-generator, 621-generator rotor,
622-second hollow cavity; 630-ICE intermediate shaft assembly, 631-ICE intermediate shaft, 632-first ICE intermediate gear, 633-second ICE intermediate gear; 640-differential shaft assembly; 650-EV intermediate shaft assembly, 651-EV intermediate shaft, 652-first EV intermediate gear, 653-second EV intermediate gear; 660-drive motor input shaft assembly, 661-input shaft, 662-transmission gear; 670-drive motor, 671-rotor of drive motor.
200-inner gear ring shaft, 201-inner hole; 210-sleeve portion; 220-cover portion, 221-gear sleeve portion, 222-baffle portion, 223-inner spline; 230-first mounting position; 240-assembly position, 241-inner hole wall; 250-second mounting position; 260-limiting structure, 261-circlip groove, 262-end face, 263-convex edge, 264-hole shoulder; 270-oil guide hole; 280-oil guide groove.
100-planetary row; 110-sun gear shaft, 111-first hollow cavity, 1111-oil storage cavity, 1112-expanding section, 112-fourth oil guide hole, 113-bearing mounting groove; 120-planet carrier, 121-planet carrier shaft, 122-connecting plate, 123-planetary gear shaft, 124-oil collecting cavity, 1241-large hole section, 1242-small hole section, 125-first oil guide hole, 126-second oil guide hole, 1261-axial oil guide hole, 1262-radial oil guide hole, 127-third oil guide hole ; 130-sun gear; 140-planet gear; 150-inner ring gear; 160-lubrication channel; 171-planet gear bearing; 172-first planet carrier bearing; 173-second planet carrier bearing; 174-intermediate bearing; 175-first support bearing; 176-second support bearing; 177a-needle bearing for mounting the first gear gear, 177b-needle bearing for mounting the inner ring gear shaft, 177c-needle bearing for mounting the second gear gear; 178-thrust bearing; 179-ball bearing.
10-oil guide pipe, 11-oil outlet hole, 12-oil outlet; 20-oil guide piece; 30-bushing; 40-actuator, 41-gear hub, 42-
Combining teeth, S1-first actuator, S2-second actuator; 50-first gear, 51-gear ring, 52-connecting part; 60-second gear; 70-circlip; 80-sleeve.
具体实施方式Detailed ways
为下面将结合本公开实施方式中的附图，对本公开实施方式中的技术方案进行清楚、完整地描述。显然，所描述的实施方式仅仅是本公开一部分实施方式，而不是全部的实施方式。基于本公开中的实施方式，本领域技术人员在没有作出创造性劳动前提下所获得的所有其他实施方式，都属于本公开保护的范围。The technical solutions in the embodiments of the present disclosure will be described clearly and completely below in conjunction with the drawings in the embodiments of the present disclosure. Obviously, the described embodiments are only part of the embodiments of the present disclosure, not all of the embodiments. Based on the embodiments of the present disclosure, all other embodiments obtained by those skilled in the art without creative work are within the scope of protection of the present disclosure.
图1为依据本公开一些实施例的混合动力变速机构总成的结构示意图；图2为图1的混合动力变速机构总成在某一视角下的结构示意图图3为图1的混合动力变速机构总成在另一视角下的结构示意图。1 is a schematic diagram of the structure of a hybrid transmission mechanism assembly according to some embodiments of the present disclosure; FIG. 2 is a schematic diagram of the structure of the hybrid transmission mechanism assembly of FIG. 1 at a certain viewing angle; and FIG. 3 is a schematic diagram of the structure of the hybrid transmission mechanism assembly of FIG. 1 at another viewing angle.
依据本公开的第一方面提供一种混合动力变速机构总成600，如图1至图3所示，可以包括传动连接的发动机输入轴总成610、发电机620、ICE中间轴总成630、差速器轴总成640、EV中间轴总成650、驱动电机输入轴总成660和驱动电机670。由于发动机输入轴总成 610与发动机传动连接，发动机输入轴总成610设有行星排100、执行机构和挡位齿轮，因此能够实现挡位变换。也即混合动力变速机构总成600能实现发动机+电机的混合动力输入，以及混动发动机多挡化。According to a first aspect of the present disclosure, a hybrid transmission mechanism assembly 600 is provided, as shown in FIGS. 1 to 3 , which may include an engine input shaft assembly 610, a generator 620, an ICE intermediate shaft assembly 630, a differential shaft assembly 640, an EV intermediate shaft assembly 650, a drive motor input shaft assembly 660, and a drive motor 670. 610 is connected to the engine by transmission, and the engine input shaft assembly 610 is provided with a planetary gear 100, an actuator and a gear gear, so that gear shifting can be realized. That is, the hybrid power transmission mechanism assembly 600 can realize the hybrid power input of the engine + motor, and the multi-gear of the hybrid engine.
如图2和图3所示，针对上述各个总成的位置布置；发动机输入轴总成610与发电机620同轴设置，也即发电机620的转子621直接与发动机输入轴总成610的输入轴(太阳轮轴110、行星架120或内齿圈轴200)传动连接，例如采用键连接、齿轮连接等方式。驱动电机输入轴总成660和驱动电机670同轴设置，也即驱动电机670的转子671直接与驱动电机输入轴总成660的输入轴661传动连接，例如采用键连接、齿轮连接等方式，驱动电机输入轴总成660的输入轴661上一体成型有传动齿轮662。发电机620和驱动电机670位于同侧。以发动机输入轴总成610的轴线平行于车辆宽度方向为例，则发动机输入轴总成610靠近驾驶位的一侧为左侧(记为L)，发动机输入轴总成610靠近副驾驶位的一侧为右侧(记为R)，则发电机620和驱动电机670同位于发动机输入轴总成610的左侧或同位于发动机输入轴总成610的右侧。图2和图3示出了发电机620和驱动电机670同位于发动机输入轴总成610的左侧时的混合动力变速机构总成600的结构图。As shown in FIG. 2 and FIG. 3 , the positions of the above-mentioned assemblies are arranged; the engine input shaft assembly 610 is coaxially arranged with the generator 620, that is, the rotor 621 of the generator 620 is directly connected to the input shaft (sun gear shaft 110, planetary carrier 120 or inner gear ring shaft 200) of the engine input shaft assembly 610 by transmission, for example, by key connection, gear connection, etc. The drive motor input shaft assembly 660 is coaxially arranged with the drive motor 670, that is, the rotor 671 of the drive motor 670 is directly connected to the input shaft 661 of the drive motor input shaft assembly 660 by transmission, for example, by key connection, gear connection, etc., and a transmission gear 662 is integrally formed on the input shaft 661 of the drive motor input shaft assembly 660. The generator 620 and the drive motor 670 are located on the same side. Taking the case where the axis of the engine input shaft assembly 610 is parallel to the vehicle width direction, the side of the engine input shaft assembly 610 close to the driver's seat is the left side (denoted as L), and the side of the engine input shaft assembly 610 close to the co-driver's seat is the right side (denoted as R), and the generator 620 and the drive motor 670 are located on the left side of the engine input shaft assembly 610 or on the right side of the engine input shaft assembly 610. FIG2 and FIG3 show the structure of the hybrid transmission mechanism assembly 600 when the generator 620 and the drive motor 670 are located on the left side of the engine input shaft assembly 610.
通过将发电机620和驱动电机670设置在发动机输入轴总成610的同一侧，在布置时能够将电机总成(发电机620和驱动电机670)和轴齿总成(发动机输入轴总成610、ICE中间轴总成630、差速器轴总成640、EV中间轴总成650、驱动电机输入轴总成660)分开放置，从而便于冷却润滑***的设计以及高低电压分区：电机通常采用喷油冷却，并且电机的工作电压较大；轴齿总成的轴承通常采用主动润滑，并且其中换挡电机、传感器等电子器件的电压较小。并且电机与输入轴同轴设置的方案，能够缩小混合动力变速机构总成600的单向尺寸。By arranging the generator 620 and the drive motor 670 on the same side of the engine input shaft assembly 610, the motor assembly (generator 620 and drive motor 670) and the shaft gear assembly (engine input shaft assembly 610, ICE intermediate shaft assembly 630, differential shaft assembly 640, EV intermediate shaft assembly 650, drive motor input shaft assembly 660) can be placed separately during layout, thereby facilitating the design of the cooling and lubrication system and the high and low voltage partitioning: the motor is usually cooled by oil injection, and the working voltage of the motor is relatively high; the bearings of the shaft gear assembly are usually actively lubricated, and the voltage of the electronic components such as the shift motor and the sensor is relatively low. In addition, the scheme of arranging the motor coaxially with the input shaft can reduce the one-way size of the hybrid transmission mechanism assembly 600.
上述各个总成中，驱动电机670的轴心位置最高，ICE中间轴总成630和差速器轴总成640的整体高度最低，发动机输入轴总成610的安装高度位于驱动电机670与差速器轴总成640之间，并且发动机输入轴总成610在竖直面上的投影与驱动电机670和差速器轴总成640在竖直面上的投影具有重合部分。因此，发动机输入轴总成610的轴心、驱动电机670的轴心与差速器轴总成640的轴心呈三角形分布，如图1所示。三角形分布结构不仅能够缩小混合动力变速机构总成600的单向尺寸，而且结构稳定，此外，三角形分布能够为ICE中间轴总成630和EV中间轴总成650提供安装空间，能够进一步降低该混合动力变速机构总成600在垂直于发动机输入轴轴线的平面上的尺寸。如图1所示，在一些实施例中，EV中间轴总成650的轴心位于发动机输入轴总成610、驱动电机670和差速器轴总成640的轴心所围的三角形区域中。ICE中间轴总成630的轴心位于发动机输入轴总成610和差速器轴总成640的轴心连线的下方，并且ICE中间轴总成630的轴心的高度最低。Among the above assemblies, the axis center position of the drive motor 670 is the highest, the overall height of the ICE intermediate shaft assembly 630 and the differential shaft assembly 640 is the lowest, the installation height of the engine input shaft assembly 610 is located between the drive motor 670 and the differential shaft assembly 640, and the projection of the engine input shaft assembly 610 on the vertical plane overlaps with the projection of the drive motor 670 and the differential shaft assembly 640 on the vertical plane. Therefore, the axis center of the engine input shaft assembly 610, the axis center of the drive motor 670 and the axis center of the differential shaft assembly 640 are distributed in a triangular shape, as shown in FIG1. The triangular distribution structure can not only reduce the one-way size of the hybrid transmission mechanism assembly 600, but also has a stable structure. In addition, the triangular distribution can provide installation space for the ICE intermediate shaft assembly 630 and the EV intermediate shaft assembly 650, and can further reduce the size of the hybrid transmission mechanism assembly 600 on a plane perpendicular to the axis of the engine input shaft. As shown in FIG1 , in some embodiments, the axis of the EV intermediate shaft assembly 650 is located in a triangular area surrounded by the axis of the engine input shaft assembly 610, the drive motor 670, and the differential shaft assembly 640. The axis of the ICE intermediate shaft assembly 630 is located below the axis line connecting the engine input shaft assembly 610 and the differential shaft assembly 640, and the axis of the ICE intermediate shaft assembly 630 is at the lowest height.
发动机输入轴总成610用于连接发动机，发动机的挡位变化也是通过发动机输入轴总成610实现。图4为图1的混合动力变速机构总成中发动机输入轴总成的全剖图，如图4所示，发动机输入轴总成610可以包括行星排100、至少一个执行机构、至少一个支撑轴承、至少一个挡位齿轮和内齿圈轴200；内齿圈轴200套设于行星排100外，且内齿圈轴200与行星排100的内齿圈150传动连接，充当行星排100的一部分；至少一个执行机构、至少一个支撑轴承、至少一个挡位齿轮均设置于内齿圈轴200上。通过在发动机输入轴总成610设置有内齿圈轴200，可以同时集成行星排100传动功能、执行机构安装、挡位齿轮安装以及必要的轴向限位功能，从而极大的提高混合动力变速机构总成600的集成度，缩减混合动力变速机构总成600在轴线方向上的功能体积，使其具备更灵活的布置和搭载性能。The engine input shaft assembly 610 is used to connect the engine, and the gear change of the engine is also achieved through the engine input shaft assembly 610. FIG4 is a full cross-sectional view of the engine input shaft assembly in the hybrid transmission mechanism assembly of FIG1. As shown in FIG4, the engine input shaft assembly 610 may include a planetary gear 100, at least one actuator, at least one support bearing, at least one gear gear and an inner ring shaft 200; the inner ring shaft 200 is sleeved outside the planetary gear 100, and the inner ring shaft 200 is transmission-connected with the inner ring 150 of the planetary gear 100, serving as a part of the planetary gear 100; at least one actuator, at least one support bearing, and at least one gear gear are all arranged on the inner ring shaft 200. By providing an inner ring gear shaft 200 on the engine input shaft assembly 610, the transmission function of the planetary gear 100, the installation of the actuator, the installation of the gear gear and the necessary axial limiting function can be integrated at the same time, thereby greatly improving the integration of the hybrid transmission mechanism assembly 600, reducing the functional volume of the hybrid transmission mechanism assembly 600 in the axial direction, and making it have more flexible layout and mounting performance.
进行挡位切换时，换挡机构作用于执行机构，执行机构更改扭矩传递路径，使得不同直径齿轮参与到动力传递中，从而实现挡位变换。发动机输入轴总成610的扭矩由挡位齿轮传输至EV中间轴总成650和ICE中间轴总成630。如图2和图3所示，在一些实施例中，EV中间轴总成650可以包括EV中间轴651和安装于EV中间轴651上的第一EV中间齿轮652和第二EV中间齿轮653。第一EV中间齿轮652的直径大于第二EV中间齿轮653，由 于第二EV中间齿轮653较小，可将第二EV中间齿轮653与EV中间轴651一体成型，第一EV中间齿轮652套装于EV中间轴651上，二者通过键连接。EV中间轴总成650通过第一EV中间齿轮652与发动机输入轴总成610和驱动电机输入轴总成660传动连接，具体是第一EV中间齿轮652与第一挡位齿轮50和驱动电机输入轴总成660的传动齿轮662均啮合；EV中间轴总成650通过第二EV中间齿轮653与差速器轴总成640传动连接。When shifting gears, the shift mechanism acts on the actuator, which changes the torque transmission path so that gears of different diameters participate in the power transmission, thereby achieving gear shifting. The torque of the engine input shaft assembly 610 is transmitted to the EV intermediate shaft assembly 650 and the ICE intermediate shaft assembly 630 by the gear gears. As shown in FIGS. 2 and 3 , in some embodiments, the EV intermediate shaft assembly 650 may include an EV intermediate shaft 651 and a first EV intermediate gear 652 and a second EV intermediate gear 653 mounted on the EV intermediate shaft 651. The diameter of the first EV intermediate gear 652 is larger than that of the second EV intermediate gear 653. Since the second EV intermediate gear 653 is relatively small, the second EV intermediate gear 653 and the EV intermediate shaft 651 can be integrally formed, and the first EV intermediate gear 652 is mounted on the EV intermediate shaft 651, and the two are connected by a key. The EV intermediate shaft assembly 650 is connected to the engine input shaft assembly 610 and the drive motor input shaft assembly 660 through the first EV intermediate gear 652, specifically, the first EV intermediate gear 652 is meshed with the first gear 50 and the drive gear 662 of the drive motor input shaft assembly 660; the EV intermediate shaft assembly 650 is connected to the differential shaft assembly 640 through the second EV intermediate gear 653.
如图2和图3所示，在一些实施例中，ICE中间轴总成630可以包括ICE中间轴631和安装于ICE中间轴631上的第一ICE中间齿轮632和第二ICE中间齿轮633。第一ICE中间齿轮632的直径大于第二ICE中间齿轮633，由于第二ICE中间齿轮633较小，可将第二ICE中间齿轮633与ICE中间轴631一体成型，第一ICE中间齿轮632套装于ICE中间轴631上，二者通过键连接。ICE中间轴总成630通过第一ICE中间齿轮632与发动机输入轴总成610传动连接，具体是第一ICE中间齿轮632与第二挡位齿轮60啮合；ICE中间轴总成630通过第二ICE中间齿轮633与差速器轴总成640传动连接。As shown in FIG. 2 and FIG. 3 , in some embodiments, the ICE intermediate shaft assembly 630 may include an ICE intermediate shaft 631 and a first ICE intermediate gear 632 and a second ICE intermediate gear 633 mounted on the ICE intermediate shaft 631. The diameter of the first ICE intermediate gear 632 is larger than that of the second ICE intermediate gear 633. Since the second ICE intermediate gear 633 is smaller, the second ICE intermediate gear 633 and the ICE intermediate shaft 631 may be integrally formed, and the first ICE intermediate gear 632 is sleeved on the ICE intermediate shaft 631, and the two are connected by a key. The ICE intermediate shaft assembly 630 is transmission-connected to the engine input shaft assembly 610 through the first ICE intermediate gear 632, specifically, the first ICE intermediate gear 632 is meshed with the second gear 60; the ICE intermediate shaft assembly 630 is transmission-connected to the differential shaft assembly 640 through the second ICE intermediate gear 633.
发动机输入轴总成610是混合动力变速机构总成600中最为重要的轴齿总成，实现发动机动力输入、能量回收、挡位变换的功能。发动机输入轴总成610中内齿圈轴200作为支撑骨架，实现行星排100、至少一个执行机构、至少一个支撑轴承和至少一个挡位齿轮的安装固定。在一些实施例中发动机输入轴总成610仅设置一个行星排100，如图4所示，行星排100可以包括太阳轮轴110、行星架120、太阳轮130、行星轮140和内齿圈150。太阳轮130安装于太阳轮轴110上，或者与太阳轮轴110一体成型。行星轮140通过行星轮140轴承40安装于行星架120的行星轮140轴123上，太阳轮130、行星轮140和内齿圈150由内至外依次设置并且依次啮合，内齿圈150与内齿圈轴200传动连接。The engine input shaft assembly 610 is the most important shaft-tooth assembly in the hybrid transmission mechanism assembly 600, which realizes the functions of engine power input, energy recovery, and gear shifting. The inner ring gear shaft 200 in the engine input shaft assembly 610 serves as a supporting skeleton to realize the installation and fixation of the planetary gear 100, at least one actuator, at least one support bearing, and at least one gear gear. In some embodiments, the engine input shaft assembly 610 is provided with only one planetary gear 100, as shown in FIG. 4, and the planetary gear 100 may include a sun gear shaft 110, a planet carrier 120, a sun gear 130, a planetary gear 140, and an inner ring gear 150. The sun gear 130 is mounted on the sun gear shaft 110, or is integrally formed with the sun gear shaft 110. The planetary gear 140 is mounted on the planetary gear 140 shaft 123 of the planetary carrier 120 through the planetary gear 140 bearing 40 . The sun gear 130 , the planetary gear 140 and the inner ring gear 150 are arranged and meshed in sequence from the inside to the outside. The inner ring gear 150 is transmission-connected to the inner ring gear shaft 200 .
如图4所示，该发动机输入轴总成610中，行星排100的太阳轮轴110或行星架轴121与发动机连接，实现发动机动力输入。行星排100的太阳轮轴110或行星架轴121与发电机620连接，实现电机动力输入。内齿圈轴200套设于行星排100的用于进行发动机动力输入的行星架轴121或太阳轮轴110上。例如行星排100采用太阳轮轴110用于发动机输入，则内齿圈轴200和行星架轴121作为输出，内齿圈轴200相应套装于行星架轴121上，内齿圈轴200或行星架轴121上设有用于与发电机620传动连接的连接结构。若行星排100采用行星架轴121输入，则内齿圈轴200和太阳轮轴110作为输出，内齿圈轴200相应套装于太阳轮轴110上，则太阳轮轴110或内齿圈轴200上设有用于与发电机620传动连接的连接结构。在一些实施例中，行星排100采用行星架轴121输入发动机动力，内齿圈轴200和太阳轮轴110输出发动机动力的技术方案，内齿圈轴200套设于太阳轮轴110上。As shown in FIG4 , in the engine input shaft assembly 610 , the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100 is connected to the engine to realize the engine power input. The sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100 is connected to the generator 620 to realize the motor power input. The inner gear ring shaft 200 is sleeved on the planetary carrier shaft 121 or the sun gear shaft 110 of the planetary gear row 100 for engine power input. For example, if the planetary gear row 100 uses the sun gear shaft 110 for engine input, the inner gear ring shaft 200 and the planetary carrier shaft 121 are used as outputs, and the inner gear ring shaft 200 is correspondingly sleeved on the planetary carrier shaft 121, and the inner gear ring shaft 200 or the planetary carrier shaft 121 is provided with a connection structure for transmission connection with the generator 620. If the planetary gear row 100 uses the planetary carrier shaft 121 as input, the inner ring gear shaft 200 and the sun gear shaft 110 are used as outputs, and the inner ring gear shaft 200 is correspondingly sleeved on the sun gear shaft 110, and the sun gear shaft 110 or the inner ring gear shaft 200 is provided with a connection structure for transmission connection with the generator 620. In some embodiments, the planetary gear row 100 uses the planetary carrier shaft 121 to input engine power, and the inner ring gear shaft 200 and the sun gear shaft 110 output engine power. The inner ring gear shaft 200 is sleeved on the sun gear shaft 110.
如图4至图7所示，该内齿圈轴200可以包括轴套部210和罩部220，轴套部210为轴套结构，能套装于轴上，例如行星排100的太阳轮轴110或行星架轴121。轴套部210的轴向尺寸较长，其上可沿轴向设置若干用于安装执行机构40的第一安装位230，或者用于设置支撑轴承的装配位240、用于设置挡位齿轮的第二安装位250。罩部220与行星排100的内齿圈150传动连接，作为行星排100的一部分参与行星排100的运行，罩部220的内孔型面以及外型面均可作为用于设置支撑轴承的装配位240或用于设置齿轮的第二安装位250。由此，通过设置该内齿圈轴200，可以同时集成行星排100传动功能、执行机构40安装、挡位齿轮安装以及必要的轴向限位功能，从而极大的提高发动机输入轴总成610的集成度，缩减发动机输入轴总成610的功能体积，使得配置有该发动机输入轴总成610的电驱动***具备更灵活的布置和搭载性能。As shown in FIGS. 4 to 7 , the inner gear ring shaft 200 may include a sleeve portion 210 and a cover portion 220. The sleeve portion 210 is a sleeve structure that can be mounted on a shaft, such as the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear 100. The sleeve portion 210 has a relatively long axial dimension, and may be provided with a plurality of first mounting positions 230 for mounting the actuator 40, or a plurality of assembly positions 240 for setting the support bearing, or a plurality of second mounting positions 250 for setting the gear position. The cover portion 220 is in transmission connection with the inner gear ring 150 of the planetary gear 100, and participates in the operation of the planetary gear 100 as a part of the planetary gear 100. Both the inner hole profile and the outer profile of the cover portion 220 may be used as the assembly position 240 for setting the support bearing or the second mounting position 250 for setting the gear. Therefore, by setting the inner ring gear shaft 200, the transmission function of the planetary gear 100, the installation of the actuator 40, the installation of the gear gear and the necessary axial limiting function can be integrated at the same time, thereby greatly improving the integration of the engine input shaft assembly 610, reducing the functional volume of the engine input shaft assembly 610, and making the electric drive system equipped with the engine input shaft assembly 610 have more flexible layout and mounting performance.
内齿圈轴200的罩部220与行星排100的内齿圈150具体可采用一体成型、焊接或键连接。内齿圈轴200、行星架轴121、太阳轮轴110在工作时需要转动，并且某些工况下存在转速差，因此需要在内齿圈轴200与太阳轮轴110或行星架轴121之间安装轴承，轴承的内圈套设于太阳轮轴110或行星架轴121上，内齿圈轴200套设于轴承的外圈上。在一些实施例中，内齿圈轴200通过两个滚针轴承177b套装于太阳轮轴110上，如图4所示。The cover portion 220 of the inner gear ring shaft 200 and the inner gear ring 150 of the planetary gear row 100 can be specifically integrally formed, welded or keyed. The inner gear ring shaft 200, the planetary carrier shaft 121, and the sun gear shaft 110 need to rotate during operation, and there is a speed difference under certain working conditions, so it is necessary to install a bearing between the inner gear ring shaft 200 and the sun gear shaft 110 or the planetary carrier shaft 121, and the inner ring of the bearing is sleeved on the sun gear shaft 110 or the planetary carrier shaft 121, and the inner gear ring shaft 200 is sleeved on the outer ring of the bearing. In some embodiments, the inner gear ring shaft 200 is sleeved on the sun gear shaft 110 through two needle bearings 177b, as shown in Figure 4.
该内齿圈轴200可以是一体式结构，即轴套部210和罩部220通过铸造或机加工等一 体成型。该内齿圈轴200也可以是分体式结构，轴套部210和罩部220可以通过焊接、粘接、螺接等方式固定连接。在一些实施例中，该内齿圈轴200为铸造成型的一体式结构，然后通过机加工加工出内外型面，其材质可以是不锈钢、铸铝等金属材料。The inner gear ring shaft 200 may be an integral structure, that is, the sleeve portion 210 and the cover portion 220 are integrally formed by casting or machining. The inner gear ring shaft 200 may also be a split structure, and the sleeve portion 210 and the cover portion 220 may be fixedly connected by welding, bonding, screwing, etc. In some embodiments, the inner gear ring shaft 200 is a one-piece structure formed by casting, and then the inner and outer surfaces are machined, and the material may be a metal material such as stainless steel and cast aluminum.
内齿圈轴200的罩部220罩设于行星排100的主体部分上，行星排100的太阳轮130、行星轮140、内齿圈150均位于罩部220的内孔中。在一些实施例中，罩部220可以包括齿套部221和挡板部222，挡板部222的内环连接轴套部210、外环连接于齿套部221。齿套部221的结构与轴套部210类似，均为轴套结构，齿套部221与行星排100的内齿圈150传动连接。挡板部222可以是环形平板、环形球壳或者由多跟连杆构成的立体结构，挡板部222的具体结构形态本公开不做限制。轴套部210、挡板部222、齿套部221可以是一体式结构，或者通过焊接、粘接、螺接等方式固定连接。齿套部221与内齿圈150可以是一体式结构或者键连接，从而实现动力传动，使得整个内齿圈轴200能够跟随行星排100的内齿圈150共同转动。The cover portion 220 of the inner gear ring shaft 200 is covered on the main part of the planetary gear 100, and the sun gear 130, the planetary gear 140, and the inner gear ring 150 of the planetary gear 100 are all located in the inner hole of the cover portion 220. In some embodiments, the cover portion 220 may include a gear sleeve portion 221 and a baffle portion 222, and the inner ring of the baffle portion 222 is connected to the shaft sleeve portion 210, and the outer ring is connected to the gear sleeve portion 221. The structure of the gear sleeve portion 221 is similar to that of the shaft sleeve portion 210, and both are shaft sleeve structures. The gear sleeve portion 221 is transmission-connected to the inner gear ring 150 of the planetary gear 100. The baffle portion 222 may be an annular flat plate, an annular spherical shell, or a three-dimensional structure composed of multiple connecting rods. The specific structural form of the baffle portion 222 is not limited in this disclosure. The shaft sleeve portion 210, the baffle portion 222, and the gear sleeve portion 221 may be an integrated structure, or fixedly connected by welding, bonding, screwing, etc. The gear sleeve portion 221 and the inner gear ring 150 may be an integral structure or key-connected to achieve power transmission, so that the entire inner gear ring shaft 200 can rotate together with the inner gear ring 150 of the planetary gear set 100 .
如图4所示，在一些实施例中，齿套部221与内齿圈150通过花键连接，齿套部221的内型面设置内花键223，内齿圈150的内型面为与行星轮140啮合的齿、外型面为外花键，内齿圈150沿轴向卡入内花键223中，内齿圈150的一侧通过挡板部222的内部的端面262轴向限位，在齿套部221的内花键223设有卡簧槽261，卡簧槽261中安装卡簧70后，该卡簧70可对内齿圈150的另一侧进行轴向限位。由此确保齿套部221与内齿圈150不会发生轴向相对移动。并且卡簧70为可拆卸结构，不会影响内齿圈150的安装和拆卸。As shown in FIG. 4 , in some embodiments, the gear sleeve 221 is connected to the inner gear ring 150 through a spline, the inner profile of the gear sleeve 221 is provided with an inner spline 223, the inner profile of the inner gear ring 150 is a tooth meshing with the planetary gear 140, and the outer profile is an outer spline, the inner gear ring 150 is axially inserted into the inner spline 223, one side of the inner gear ring 150 is axially limited by the inner end face 262 of the baffle 222, and a retaining spring groove 261 is provided on the inner spline 223 of the gear sleeve 221, and after the retaining spring 70 is installed in the retaining spring groove 261, the retaining spring 70 can axially limit the other side of the inner gear ring 150. This ensures that the gear sleeve 221 and the inner gear ring 150 will not move relative to each other in the axial direction. In addition, the retaining spring 70 is a detachable structure and will not affect the installation and removal of the inner gear ring 150.
内齿圈轴200上的多个构件安装位主要包括用于安装执行机构40的第一安装位230、用于设置支撑轴承的装配位240和用于设置齿轮的第二安装位250。在一些实施例中，执行机构40可以是同步器或离合器，执行机构40可以是空套于内齿圈轴200上，或者是与内齿圈轴200固定连接或传动连接。支撑轴承用于将该内齿圈轴200安装于壳体总成300上。齿轮可以是挡位齿轮或者是仅起传动作用的传动齿轮，齿轮可以是空套于内齿圈轴200上，或者是与内齿圈轴200固定连接或传动连接。在一些实施例中，还可视具体情况在内齿圈轴200设置其他构件安装位，例如用于安装挡油件的构件安装位、用于设置传感器的构件安装位等。The multiple component installation positions on the inner gear ring shaft 200 mainly include a first installation position 230 for installing the actuator 40, an assembly position 240 for setting the support bearing, and a second installation position 250 for setting the gear. In some embodiments, the actuator 40 can be a synchronizer or a clutch, and the actuator 40 can be loosely mounted on the inner gear ring shaft 200, or fixedly connected or transmission connected to the inner gear ring shaft 200. The support bearing is used to install the inner gear ring shaft 200 on the housing assembly 300. The gear can be a gear gear or a transmission gear that only plays a transmission role. The gear can be loosely mounted on the inner gear ring shaft 200, or fixedly connected or transmission connected to the inner gear ring shaft 200. In some embodiments, other component installation positions can also be set on the inner gear ring shaft 200 according to specific circumstances, such as a component installation position for installing an oil retaining member, a component installation position for setting a sensor, etc.
上述构件安装位中，第一安装位230仅设于轴套部210上，主要是因为执行机构40动作是需要一定的轴向空间，而轴套部210相比于罩部220的轴向尺寸更大，能够满足执行机构40动作所需要的轴向空间；另一方面，轴套部210套设于行星排100的太阳轮轴110或行星架轴121上，罩部220套设于行星排100的太阳轮130、行星轮140、内齿圈150上，轴套部210相比于罩部220的径向尺寸更小，便于布置执行机构40。Among the above-mentioned component installation positions, the first installation position 230 is only arranged on the sleeve portion 210, mainly because the action of the actuator 40 requires a certain axial space, and the axial dimension of the sleeve portion 210 is larger than that of the cover portion 220, which can meet the axial space required for the action of the actuator 40; on the other hand, the sleeve portion 210 is sleeved on the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary gear row 100, and the cover portion 220 is sleeved on the sun gear 130, the planetary gear 140, and the inner ring gear 150 of the planetary gear row 100. The radial dimension of the sleeve portion 210 is smaller than that of the cover portion 220, which is convenient for arranging the actuator 40.
在一些实施例中，执行机构40的作用是改变行星排100的传动比，例如将行星排100的内齿圈150与太阳轮轴110接合共同转动、将内齿圈150与行星架接合共同转动、将行星架与太阳轮轴110接合共同转动、将内齿圈150锁定、将太阳轮130锁定、将行星轮140锁定等。在一些实施例中，第一安装位230为键连接结构，使得执行机构40与内齿圈轴200传动连接，由于内齿圈轴200与行星排100的内齿圈150传动连接，因此执行机构40可以改变内齿圈150的运动情况，例如将内齿圈150与太阳轮轴110或行星架接合，或者将内齿圈150锁定。In some embodiments, the function of the actuator 40 is to change the transmission ratio of the planetary gear row 100, such as engaging the inner gear ring 150 of the planetary gear row 100 with the sun gear shaft 110 for joint rotation, engaging the inner gear ring 150 with the planet carrier for joint rotation, engaging the planet carrier with the sun gear shaft 110 for joint rotation, locking the inner gear ring 150, locking the sun gear 130, locking the planet gear 140, etc. In some embodiments, the first mounting position 230 is a key connection structure, so that the actuator 40 is transmission-connected with the inner gear ring shaft 200. Since the inner gear ring shaft 200 is transmission-connected with the inner gear ring 150 of the planetary gear row 100, the actuator 40 can change the movement of the inner gear ring 150, such as engaging the inner gear ring 150 with the sun gear shaft 110 or the planet carrier, or locking the inner gear ring 150.
该内齿圈轴200上设有若干用于轴向限位的限位结构260，该限位结构260可以为限位凸台、限位台阶或用于安装卡簧70的凹槽。若限位结构260用于对轴承进行轴向限位，则通常选择限位凸台、限位台阶、结构端面限位；若限位结构260用于对齿轮进行轴向限位，齿轮与内齿圈轴200传动连接，例如花键连接，则通常选择卡簧70进行轴向限位。在限位结构260的设计上，为了方便执行机构40、挡位齿轮、轴承等结构件的安装，在一些实施例中，轴套部210的外型面设计为阶梯轴，具体是自远行星排端至近行星排端，轴套部210的外径呈增大趋势，各结构件逐个套装于轴套部210。阶梯轴自身可形成若干用于轴向定位的限位台阶，此外，该阶梯轴的上还设置有若干凸边263，用于对轴套80、轴承等进行轴向限位。The inner gear ring shaft 200 is provided with a plurality of limiting structures 260 for axial limiting, and the limiting structures 260 may be limiting bosses, limiting steps or grooves for installing retaining springs 70. If the limiting structure 260 is used to limit the bearing axially, a limiting boss, limiting step or structural end face limiting is usually selected; if the limiting structure 260 is used to limit the gear axially, and the gear is connected to the inner gear ring shaft 200 by transmission, such as a spline connection, then retaining springs 70 are usually selected for axial limiting. In the design of the limiting structure 260, in order to facilitate the installation of the actuator 40, the gear, the bearing and other structural parts, in some embodiments, the outer surface of the sleeve part 210 is designed as a stepped shaft, specifically, from the far planetary gear end to the near planetary gear end, the outer diameter of the sleeve part 210 increases, and each structural part is mounted on the sleeve part 210 one by one. The stepped shaft itself can form a number of limiting steps for axial positioning. In addition, the stepped shaft is also provided with a number of convex edges 263 for axially limiting the shaft sleeve 80, bearings, etc.
在第一安装位230上设有用于对执行机构40轴向限位的限位结构260，防止执行机构 40与内齿圈轴200之间发生轴向相对转动。具体在在一些实施例中，执行机构40与内齿圈轴200采用花键连接，也即第一安装位230的键连接结构采用外花键，执行机构40的齿毂41和/或结合齿42的内圈设置内花键。针对花键连接，执行机构40与内齿圈轴200采用卡簧70限位，对应的限位结构260为设于外花键的卡簧槽261，卡簧70在执行机构40的齿毂41和/或结合齿42安装到位后卡在卡簧槽261中。A limiting structure 260 for axially limiting the actuator 40 is provided on the first installation position 230 to prevent the actuator 40 from Axial relative rotation occurs between the actuator 40 and the inner gear ring shaft 200. Specifically, in some embodiments, the actuator 40 and the inner gear ring shaft 200 are splined, that is, the key connection structure of the first installation position 230 adopts an external spline, and the inner ring of the gear hub 41 and/or the combined tooth 42 of the actuator 40 is provided with an internal spline. For the spline connection, the actuator 40 and the inner gear ring shaft 200 are limited by a retaining spring 70, and the corresponding limiting structure 260 is a retaining spring groove 261 provided on the external spline, and the retaining spring 70 is stuck in the retaining spring groove 261 after the gear hub 41 and/or the combined tooth 42 of the actuator 40 are installed in place.
为保证内齿圈轴200安装稳定，在一些实施例中，支撑轴承设置两个，分别为第一支撑轴承175和第二支撑轴承176，第一支撑轴承175和第二支撑轴承176可采用滚珠轴承、滚针轴承、推力轴承等，一些实施例采用滚珠轴承。装配位240的数量相应为两个，齿套部221和轴套部210均设有装配位240。如图4所示，第一支撑轴承175和第二支撑轴承176分别安装于轴套部210和罩部220上，第一支撑轴承175设于罩部220的内孔中，第二支撑轴承176通过轴套80设于第一执行机构S1和第二执行机构S2之间，第一支撑轴承175和第二支撑轴承176由于主要起到支撑内齿圈轴200的作用，因此可均采用滚珠轴承。第一支撑轴承175通过第一安装位230的端面262，即罩部220的第一安装位230与支撑位所形成的孔肩264轴向限位；第二支撑轴承176通过轴套80上设置的凸台轴向限位。第一支撑轴承175的内环和第二支撑轴承176的外环分别与壳体总成300的轴承安装孔过盈配合。In order to ensure the stable installation of the inner gear ring shaft 200, in some embodiments, two support bearings are provided, namely, the first support bearing 175 and the second support bearing 176. The first support bearing 175 and the second support bearing 176 can adopt ball bearings, needle bearings, thrust bearings, etc. Some embodiments adopt ball bearings. The number of assembly positions 240 is correspondingly two, and both the gear sleeve part 221 and the shaft sleeve part 210 are provided with assembly positions 240. As shown in FIG. 4, the first support bearing 175 and the second support bearing 176 are respectively installed on the shaft sleeve part 210 and the cover part 220. The first support bearing 175 is arranged in the inner hole of the cover part 220, and the second support bearing 176 is arranged between the first actuator S1 and the second actuator S2 through the shaft sleeve 80. Since the first support bearing 175 and the second support bearing 176 mainly play the role of supporting the inner gear ring shaft 200, they can both adopt ball bearings. The first support bearing 175 is axially limited by the end surface 262 of the first mounting position 230, that is, the hole shoulder 264 formed by the first mounting position 230 and the supporting position of the cover part 220; the second support bearing 176 is axially limited by the boss provided on the sleeve 80. The inner ring of the first support bearing 175 and the outer ring of the second support bearing 176 are respectively interference fit with the bearing mounting holes of the housing assembly 300.
对于用于设置支撑轴承的装配位240和用于设置齿轮的第二安装位250，支撑轴承和齿轮的工作形式是转动，不需要发生轴向移动，因此可根据实际需要设置在罩部220和/或轴套部210上。第一支撑轴承175安装于齿套部221的装配位240上，第二支撑轴承176安装于轴套部210的装配位240上。As for the assembly position 240 for setting the support bearing and the second installation position 250 for setting the gear, the support bearing and the gear work in the form of rotation, and do not need to move axially, so they can be set on the cover part 220 and/or the sleeve part 210 according to actual needs. The first support bearing 175 is installed on the assembly position 240 of the gear sleeve part 221, and the second support bearing 176 is installed on the assembly position 240 of the sleeve part 210.
图6为图4的发动机输入轴总成中内齿圈轴的结构示意图；图7为图6的内齿圈轴的全剖图。如图6和图7所示，罩部220的装配位240为齿套部221的内孔壁241，轴套部210的装配位240为光杆段，第一支撑轴承175与内孔壁241过盈配合，第二支撑轴承176与光杆段过盈配合。齿套部221的装配位240与内齿圈150的安装处之间设有用于对第一支撑轴承175轴向限位的限位结构260，该处的限位结构260可采用端面限位(例如轴肩限位、凸台限位)或者卡簧限位。如图7所示，在一些实施例中，齿套部221的内孔壁241与内花键223之间形成孔肩264，通过孔肩264对内孔壁241上安装的第一支撑轴承175进行轴向限位。FIG6 is a schematic diagram of the structure of the inner gear ring shaft in the engine input shaft assembly of FIG4 ; FIG7 is a full cross-sectional view of the inner gear ring shaft of FIG6 . As shown in FIG6 and FIG7 , the assembly position 240 of the cover part 220 is the inner hole wall 241 of the gear sleeve part 221 , the assembly position 240 of the shaft sleeve part 210 is the bare rod section, the first support bearing 175 is interference fit with the inner hole wall 241 , and the second support bearing 176 is interference fit with the bare rod section. A limiting structure 260 for axially limiting the first support bearing 175 is provided between the assembly position 240 of the gear sleeve part 221 and the installation position of the inner gear ring 150 , and the limiting structure 260 at this place can adopt end face limiting (such as shaft shoulder limiting, boss limiting) or retaining spring limiting. As shown in FIG. 7 , in some embodiments, a hole shoulder 264 is formed between the inner hole wall 241 of the gear sleeve portion 221 and the inner spline 223 , and the hole shoulder 264 is used to axially limit the first support bearing 175 installed on the inner hole wall 241 .
在一些实施例中，轴套部210的装配位240上设有轴套80，一方面可以弥补第二支撑轴承176与光杆段的直径差，另一方面可以用于周围结构件的轴向限位，轴套80与对应的光杆段过盈压装，第二支撑轴承176过盈安装于轴套80上。轴套80用于周围结构件的轴向限位时，周围结构件同样对轴套80起到轴向限位的作用。In some embodiments, a sleeve 80 is provided on the assembly position 240 of the sleeve portion 210, which can compensate for the diameter difference between the second support bearing 176 and the polished rod section on the one hand, and can be used for axial positioning of surrounding structural members on the other hand. The sleeve 80 is press-fitted with the corresponding polished rod section by interference fit, and the second support bearing 176 is installed on the sleeve 80 by interference fit. When the sleeve 80 is used for axial positioning of surrounding structural members, the surrounding structural members also play a role in axial positioning of the sleeve 80.
在一些实施例中，发动机输入轴总成610设置为满足发动机四挡，具体是通过两个执行机构40和两个挡位齿轮实现发动机四挡，两个执行机构40和两个挡位齿轮分别记为：第一执行机构S1、第二执行机构S2、第一挡位齿轮50和第二挡位齿轮60。第一执行机构S1、第二执行机构S2均为同步器，第一挡位齿轮50为大齿圈，实现发动机三挡和发动机四挡；第二挡位齿轮60为小齿圈，实现发动机一挡和发动机二挡。In some embodiments, the engine input shaft assembly 610 is configured to meet the engine fourth gear, specifically, the engine fourth gear is achieved through two actuators 40 and two gear gears, the two actuators 40 and the two gear gears are respectively recorded as: the first actuator S1, the second actuator S2, the first gear gear 50 and the second gear gear 60. The first actuator S1 and the second actuator S2 are both synchronizers, the first gear gear 50 is a large gear ring, and the engine third gear and the engine fourth gear are achieved; the second gear gear 60 is a small gear ring, and the engine first gear and the engine second gear are achieved.
为了适配发动机输入轴总成610的挡位设计，内齿圈轴200的第一安装位230、装配位240、第二安装位250均设有两个。为保证两个第一安装位230上安装的两个执行机构40具有足够的轴向拨动空间，两个第一安装位230分布于轴套部210的两端，需要说明的是，第一安装位230可以安装执行机构40的所有构件，也可以仅用于安装执行机构40的部分构件，例如仅安装同步器的齿毂41或者单侧的结合齿42。为了缩小内齿圈轴200的轴向尺寸，提高设置有该内齿圈轴200的混动变速箱的搭载性能，在一些实施例中，两个装配位240和两个第二安装位250均分别设于轴套部210和罩部220上，如图6所示。In order to adapt to the gear design of the engine input shaft assembly 610, the inner gear ring shaft 200 is provided with two first mounting positions 230, two assembly positions 240, and two second mounting positions 250. In order to ensure that the two actuators 40 installed on the two first mounting positions 230 have sufficient axial shifting space, the two first mounting positions 230 are distributed at both ends of the sleeve portion 210. It should be noted that the first mounting position 230 can be used to install all components of the actuator 40, or only part of the components of the actuator 40, such as only installing the gear hub 41 of the synchronizer or the single-sided coupling gear 42. In order to reduce the axial size of the inner gear ring shaft 200 and improve the mounting performance of the hybrid transmission provided with the inner gear ring shaft 200, in some embodiments, the two assembly positions 240 and the two second mounting positions 250 are respectively provided on the sleeve portion 210 and the cover portion 220, as shown in FIG6.
在一些实施例中，第一执行机构S1和第二执行机构S2分布于轴套部210的两端。第一执行机构S1和第二执行机构S2可根据需要采用同步器(单边或双边)或离合器。第一执行机构S1/第二执行机构S2可根据实际需要设置为可选择地连接太阳轮轴110与内齿圈轴200、可选择地连接行星架轴121与内齿圈轴200、可选择地连接内齿圈轴200与第一挡位齿轮50 或可选择地连接内齿圈轴200与第二挡位齿轮60。In some embodiments, the first actuator S1 and the second actuator S2 are distributed at both ends of the sleeve portion 210. The first actuator S1 and the second actuator S2 can use synchronizers (single or double) or clutches as needed. The first actuator S1/the second actuator S2 can be set to selectively connect the sun gear shaft 110 and the inner gear ring shaft 200, selectively connect the planet carrier shaft 121 and the inner gear ring shaft 200, and selectively connect the inner gear ring shaft 200 and the first gear gear 50 according to actual needs. Alternatively, the ring gear shaft 200 and the second gear gear 60 may be connected.
在一些实施例中，第一执行机构S1采用同步器，具有齿毂41和两侧的结合齿42，第一执行机构S1的齿毂41与第一安装位230传动连接；第一执行机构S1的一侧的结合齿42与第一挡位齿轮50固定连接；第一执行机构S1的另一侧的结合齿42与第二挡位齿轮60固定连接，第一执行机构S1用于将内齿圈轴200可选地与第一挡位齿轮50或第二挡位齿轮60连接。第二执行机构S2同样采用同步器，具有齿毂41和两侧的结合齿42，第二执行机构S2的齿毂41与行星排100的太阳轮轴110传动连接，第二执行机构S2的一侧的结合齿42与轴套部210传动连接，第二执行机构S2的另一侧的结合齿42与壳体总成300固定连接，第二执行机构S2用于将太阳轮轴110可选地与内齿圈轴200或壳体总成300连接，实现行星排100不同的速比输出。为了提高该发动机输入轴总成610的轴向承载能力，第二执行机构S2的齿毂41与壳体总成300之间设有推力轴承，该推力轴承套装于太阳轮轴110上。In some embodiments, the first actuator S1 adopts a synchronizer, having a gear hub 41 and combining teeth 42 on both sides. The gear hub 41 of the first actuator S1 is transmission-connected to the first mounting position 230; the combining teeth 42 on one side of the first actuator S1 are fixedly connected to the first gear gear 50; the combining teeth 42 on the other side of the first actuator S1 are fixedly connected to the second gear gear 60. The first actuator S1 is used to optionally connect the inner ring shaft 200 to the first gear gear 50 or the second gear gear 60. The second actuator S2 also uses a synchronizer, having a gear hub 41 and coupling teeth 42 on both sides. The gear hub 41 of the second actuator S2 is transmission-connected to the sun gear shaft 110 of the planetary gear row 100, the coupling teeth 42 on one side of the second actuator S2 are transmission-connected to the shaft sleeve 210, and the coupling teeth 42 on the other side of the second actuator S2 are fixedly connected to the housing assembly 300. The second actuator S2 is used to connect the sun gear shaft 110 to the inner gear ring shaft 200 or the housing assembly 300 to achieve different speed ratio outputs of the planetary gear row 100. In order to improve the axial load-bearing capacity of the engine input shaft assembly 610, a thrust bearing is provided between the gear hub 41 of the second actuator S2 and the housing assembly 300, and the thrust bearing is sleeved on the sun gear shaft 110.
第一挡位齿轮50和第二挡位齿轮60分别安装于两个第二安装位250，由于第一挡位齿轮50和第二挡位齿轮60均空套于内齿圈轴200上，因此第一挡位齿轮50和第二挡位齿轮60的内孔均安装有轴承，例如滚珠轴承，如图4所示。在一些实施例中，若挡位齿轮与内齿圈轴200传动连接，则不需要设置轴承。为了降低内齿圈轴200的轴向长度，齿套部221和轴套部210均设有第二安装位250，也即第一挡位齿轮50通过轴承空套于齿套部221上，第二挡位齿轮60通过轴承空套于轴套部210上。The first gear gear 50 and the second gear gear 60 are respectively installed at two second installation positions 250. Since the first gear gear 50 and the second gear gear 60 are both loosely sleeved on the inner gear ring shaft 200, the inner holes of the first gear gear 50 and the second gear gear 60 are both installed with bearings, such as ball bearings, as shown in FIG4. In some embodiments, if the gears are in transmission connection with the inner gear ring shaft 200, no bearings are required. In order to reduce the axial length of the inner gear ring shaft 200, the gear sleeve portion 221 and the shaft sleeve portion 210 are both provided with second installation positions 250, that is, the first gear gear 50 is loosely sleeved on the gear sleeve portion 221 through a bearing, and the second gear gear 60 is loosely sleeved on the shaft sleeve portion 210 through a bearing.
如图4所示，第一挡位齿轮50和第二挡位齿轮60均为齿圈，第一挡位齿轮50通过滚针轴承177a空套于罩部220上，第二挡位齿轮60通过滚针轴承177c空套于轴套部210上、且位于第一执行机构S1与第二支撑轴承176之间，第一挡位齿轮50和第二挡位齿轮60均可相对于内齿圈轴200自由转动。在一些实施例中，第一挡位齿轮50为大齿圈，第一挡位齿轮50的内孔径大于第二挡位齿轮60。As shown in FIG4 , the first gear 50 and the second gear 60 are both gear rings. The first gear 50 is sleeved on the cover portion 220 through a needle bearing 177a, and the second gear 60 is sleeved on the shaft sleeve portion 210 through a needle bearing 177c and is located between the first actuator S1 and the second support bearing 176. Both the first gear 50 and the second gear 60 can rotate freely relative to the inner gear ring shaft 200. In some embodiments, the first gear 50 is a large gear ring, and the inner diameter of the first gear 50 is larger than that of the second gear 60.
第一挡位齿轮50既要满足能够套装于罩部220上的直径要求，又要满足与安装于轴套部210上的第一执行机构S1连接，因此，第一挡位齿轮50具体设置为包括齿圈部51和连接部52，齿圈部51与内齿圈轴200的齿套部221结构相似，均为轴套结构，连接部52与内齿圈轴200的挡板部222结构相似均为环形板结构。齿圈部51和连接部52可以是一体成型结构，或者通过焊接、螺纹紧固件连接固定。齿圈部51通过滚针轴承177a空套于罩部220上，该轴承通过罩部220外型面上设置的凸边263轴向限位。连接部52与第一执行机构S1的一侧的结合齿42固定连接，连接部52与第一执行机构S1的该结合齿42可以是一体成型、焊接固定或者传动连接。第二挡位齿轮60与第一执行机构S1的另一侧的结合齿42固定连接，第二挡位齿轮60与第一执行机构S1的该结合齿42可以是一体成型、焊接固定或者传动连接。第二挡位齿轮60通过第二支撑轴承176的轴套80轴向限位。The first gear gear 50 must not only meet the diameter requirement of being able to be sleeved on the cover part 220, but also meet the connection with the first actuator S1 installed on the sleeve part 210. Therefore, the first gear gear 50 is specifically configured to include a ring gear part 51 and a connecting part 52. The ring gear part 51 is similar in structure to the sleeve part 221 of the inner gear ring shaft 200, both of which are sleeve structures. The connecting part 52 is similar in structure to the baffle part 222 of the inner gear ring shaft 200, both of which are annular plate structures. The ring gear part 51 and the connecting part 52 can be an integrally formed structure, or connected and fixed by welding or threaded fasteners. The ring gear part 51 is sleeved on the cover part 220 through a needle bearing 177a, and the bearing is axially limited by a convex edge 263 provided on the outer surface of the cover part 220. The connecting part 52 is fixedly connected to the coupling tooth 42 on one side of the first actuator S1. The connecting part 52 and the coupling tooth 42 of the first actuator S1 can be integrally formed, welded, or transmission-connected. The second gear 60 is fixedly connected to the coupling tooth 42 on the other side of the first actuator S1 , and the second gear 60 and the coupling tooth 42 of the first actuator S1 can be integrally formed, welded, or transmission-connected. The second gear 60 is axially limited by the sleeve 80 of the second support bearing 176 .
为了进一步提高该发动机输入轴总成610的轴向承载能力，如图4所示，连接部52与罩部220之间设有推力轴承178，具体是连接部52与挡板部222之间设有推力轴承178。也就是说，第一挡位齿轮50通过滚针轴承177a和推力轴承178套在内齿圈轴200上，通过推力轴承178以及挡板部222外部的端面262轴向限位。内齿圈轴200的罩部220上设置有贯通壁厚的导油孔270，使得行星排100中飞溅的润滑油能够通过罩部220上的导油孔270进入第一挡位齿轮50与罩部220之间的缝隙中，润滑其中的滚针轴承177a和推力轴承178。In order to further improve the axial bearing capacity of the engine input shaft assembly 610, as shown in FIG4 , a thrust bearing 178 is provided between the connecting portion 52 and the cover portion 220, specifically, a thrust bearing 178 is provided between the connecting portion 52 and the baffle portion 222. That is, the first gear position gear 50 is sleeved on the inner gear ring shaft 200 through the needle bearing 177a and the thrust bearing 178, and is axially limited by the thrust bearing 178 and the end face 262 outside the baffle portion 222. The cover portion 220 of the inner gear ring shaft 200 is provided with an oil guide hole 270 that penetrates the wall thickness, so that the lubricating oil splashed in the planetary gear 100 can enter the gap between the first gear position gear 50 and the cover portion 220 through the oil guide hole 270 on the cover portion 220, and lubricate the needle bearing 177a and the thrust bearing 178 therein.
由于一些实施例的内齿圈轴200上需要安装多个轴承、齿轮，需要保证该多个轴承、齿轮的润滑需求，具体可以采用飞溅润滑或主动润滑的方式，由于内齿圈轴200各个轴承、齿轮布置紧凑，相互形成轴向限位的效果，因此仅通过外部飞溅的润滑油恐难以达到预期的润滑效果，因此，一些实施例采用主动润滑方案。Since multiple bearings and gears need to be installed on the inner ring shaft 200 of some embodiments, the lubrication requirements of the multiple bearings and gears need to be guaranteed. Specifically, splash lubrication or active lubrication can be used. Since the bearings and gears of the inner ring shaft 200 are compactly arranged and form an axial limiting effect on each other, it may be difficult to achieve the expected lubrication effect only by external splashing lubricating oil. Therefore, some embodiments adopt an active lubrication solution.
如图6和图7所示，轴套部210上设有至少一个贯通轴套部210套壁的导油孔270，导油孔270通常沿周向设置多个，位于同一横截面的多个导油孔270为一组，则轴套部210上沿其轴向可以设置多组导油孔270。在一些实施例中，轴套部210的外型面设有连通于导油孔270的导油槽280，导油槽280与一组导油孔270均连通，导油槽280的具体数量根据 实际需要而定。导油槽280为内凹的凹槽，通过设置导油槽280可以将导油孔270流出的润滑油沿周向均匀分布，另外，由于导油槽280为凹槽，该凹槽还可作为内齿圈轴200外型面机加工时的退刀槽。As shown in FIG6 and FIG7, the shaft sleeve 210 is provided with at least one oil guide hole 270 penetrating the sleeve wall of the shaft sleeve 210. The oil guide holes 270 are usually arranged in a plurality along the circumferential direction. The plurality of oil guide holes 270 located in the same cross section are grouped together. Then, the shaft sleeve 210 may be provided with a plurality of groups of oil guide holes 270 along its axial direction. In some embodiments, the outer surface of the shaft sleeve 210 is provided with an oil guide groove 280 connected to the oil guide hole 270. The oil guide groove 280 is connected to a group of oil guide holes 270. The specific number of the oil guide grooves 280 is determined according to the embodiment of the present invention. The oil guide groove 280 is a concave groove, and the lubricating oil flowing out of the oil guide hole 270 can be evenly distributed along the circumference by setting the oil guide groove 280. In addition, since the oil guide groove 280 is a groove, the groove can also be used as a backing groove when machining the outer surface of the inner gear ring shaft 200.
此外，在一些实施例中，罩部220上也可设置导油孔270，导油孔270可选择设置在齿套部221和/或挡板部222上，便于润滑油进出罩部220的内孔。如图2所示，在一些实施例中，挡板部222上可以设置若干导油孔270，该导油孔270设置为沿飞溅方向向外倾斜，便于行星排100转动时飞溅的润滑油从导油孔270中甩出，润滑内齿圈轴200外部的结构件。In addition, in some embodiments, the cover portion 220 may also be provided with an oil guide hole 270, which may be selectively provided on the gear sleeve portion 221 and/or the baffle portion 222 to facilitate the lubricating oil to enter and exit the inner hole of the cover portion 220. As shown in FIG2 , in some embodiments, the baffle portion 222 may be provided with a plurality of oil guide holes 270, which are arranged to be inclined outwardly along the splashing direction, so that the splashed lubricating oil is thrown out from the oil guide hole 270 when the planetary gear 100 rotates, and lubricating the external structural parts of the inner gear ring shaft 200.
发动机输入轴总成610中，行星排100是功率分流的主要零件，行星排100的润滑是保证该发动机输入轴总成610正常运行的重要条件，行星排100的主要润滑需求在于行星轮轴承171，一方面行星轮轴承171数量多，分布广，另一方面，由于行星轮轴承171的安装位置是位于行星架120所围区域中，并且位于行星轮140与行星轮轴123之间，因此受行星轮140、行星架120的阻挡，润滑油难以进入行星轮轴承171安装处，故而行星轮轴承171容易产生烧蚀，影响整个行星排100的使用。In the engine input shaft assembly 610, the planetary gear 100 is the main component for power distribution. The lubrication of the planetary gear 100 is an important condition for ensuring the normal operation of the engine input shaft assembly 610. The main lubrication requirement of the planetary gear 100 is the planetary gear bearing 171. On the one hand, the number of planetary gear bearings 171 is large and the distribution is wide. On the other hand, since the installation position of the planetary gear bearing 171 is located in the area surrounded by the planetary carrier 120 and between the planetary gear 140 and the planetary gear shaft 123, it is blocked by the planetary gear 140 and the planetary carrier 120, and it is difficult for lubricating oil to enter the installation position of the planetary gear bearing 171. Therefore, the planetary gear bearing 171 is prone to ablation, affecting the use of the entire planetary gear 100.
图5为图4的发动机输入轴总成的内部润滑通道的结构示意图。为了改善行星排100内部的润滑情况，如图5所示，在一些实施例中，行星排100设有润滑通道160，行星排100的太阳轮轴110设有沿轴向贯通的第一中空腔111，太阳轮轴110可以是与行星排100的太阳轮130一体成型，或者键连接，在一些实施例中太阳轮轴110与太阳轮130一体成型。行星排100的行星架120设有集油腔124，第一中空腔111、集油腔124和润滑通道160依次连通，并且润滑通道160的出口朝向行星排100的行星轮轴承171。为了方便润滑太阳轮轴110外部的结构，太阳轮轴110上设有与第一中空腔111相连通的若干第四导油孔112，若干第四导油孔112中的一个第四导油孔112的出口朝向太阳轮轴110与内齿圈轴200之间的轴承。FIG5 is a schematic diagram of the structure of the internal lubrication channel of the engine input shaft assembly of FIG4. In order to improve the lubrication condition inside the planetary gear 100, as shown in FIG5, in some embodiments, the planetary gear 100 is provided with a lubrication channel 160, and the sun gear shaft 110 of the planetary gear 100 is provided with a first hollow cavity 111 that penetrates along the axial direction, and the sun gear shaft 110 can be integrally formed with the sun gear 130 of the planetary gear 100, or key-connected. In some embodiments, the sun gear shaft 110 is integrally formed with the sun gear 130. The planet carrier 120 of the planetary gear 100 is provided with an oil collecting cavity 124, and the first hollow cavity 111, the oil collecting cavity 124 and the lubrication channel 160 are connected in sequence, and the outlet of the lubrication channel 160 faces the planetary gear bearing 171 of the planetary gear 100. In order to facilitate lubrication of the external structure of the sun gear shaft 110, the sun gear shaft 110 is provided with a plurality of fourth oil guide holes 112 connected to the first hollow cavity 111, and the outlet of a fourth oil guide hole 112 among the plurality of fourth oil guide holes 112 faces the bearing between the sun gear shaft 110 and the inner ring shaft 200.
在一些实施例中，行星架120的润滑通道160可以是开设于行星架120基材中的油道，也可以是由外部元件合围形成的油道，满足能够将润滑油送入行星轮轴承171的安装处即可。在一些实施例中，该行星轮轴承171为滚针轴承，具体可以是满滚针轴承或钢保持架滚针轴承。该行星轮轴承171采用双列滚针轴承，中间设置有垫片，垫片在径向上要与行星轮轴123形成间隙，保证润滑油可以进入滚针轴承中，润滑滚针轴承的滚子表面。In some embodiments, the lubrication channel 160 of the planetary carrier 120 may be an oil channel opened in the base material of the planetary carrier 120, or may be an oil channel formed by enclosing external components, as long as the lubricating oil can be delivered to the installation location of the planetary gear bearing 171. In some embodiments, the planetary gear bearing 171 is a needle bearing, specifically a full needle bearing or a steel cage needle bearing. The planetary gear bearing 171 adopts a double-row needle bearing with a gasket in the middle. The gasket should form a gap with the planetary gear shaft 123 in the radial direction to ensure that the lubricating oil can enter the needle bearing and lubricate the roller surface of the needle bearing.
如图5所示，在一些实施例中，行星架120可以包括依次连接的行星架轴121、连接板122和若干行星轮轴123，行星轮140套在行星轮轴123上，行星轮140与行星轮轴123之间安装有行星轮轴承171，行星轮140两侧分别通过齿轮与太阳轮130的齿轮和内齿圈150的齿轮进行啮合。行星架轴121位于连接板122的中心，行星轮轴123以行星架轴121为中心、沿周向均匀分布。行星架轴121与连接板122可以通过螺纹紧固件、卡扣结构等可拆卸连接，或者焊接固定，或者行星架轴121与连接板122为一体式结构，在一些实施例中，行星架轴121通过过盈压装在连接板122上。连接板122和行星轮轴123也可以通过螺纹紧固件、卡扣结构等可拆卸连接，或者焊接固定，或者连接板122和行星轮轴123为一体式结构，本公开不做限制。行星架120的整体外部形状、轮廓本公开同样不做限制，例如行星架120可以采用笼式结构。As shown in FIG5 , in some embodiments, the planet carrier 120 may include a planet carrier shaft 121, a connecting plate 122, and a plurality of planetary gear shafts 123 connected in sequence, the planetary gear 140 is sleeved on the planetary gear shaft 123, a planetary gear bearing 171 is installed between the planetary gear 140 and the planetary gear shaft 123, and the two sides of the planetary gear 140 are respectively meshed with the gear of the sun gear 130 and the gear of the inner gear ring 150 through gears. The planetary carrier shaft 121 is located at the center of the connecting plate 122, and the planetary gear shafts 123 are evenly distributed along the circumference with the planetary carrier shaft 121 as the center. The planetary carrier shaft 121 and the connecting plate 122 can be detachably connected by threaded fasteners, snap-fit structures, etc., or fixed by welding, or the planetary carrier shaft 121 and the connecting plate 122 are an integrated structure. In some embodiments, the planetary carrier shaft 121 is pressed onto the connecting plate 122 by interference fit. The connecting plate 122 and the planetary gear shaft 123 can also be detachably connected by threaded fasteners, snap-fit structures, etc., or welded and fixed, or the connecting plate 122 and the planetary gear shaft 123 are an integrated structure, which is not limited in the present disclosure. The overall external shape and profile of the planetary carrier 120 are also not limited in the present disclosure, for example, the planetary carrier 120 can adopt a cage structure.
如图5所示，行星架轴121设有连通的集油腔124和第一导油孔125，集油腔124位于行星架轴121的中心，优选与行星架轴121共轴线。行星轮轴123设有第二导油孔126，第二导油孔126的出口朝向行星排100的行星轮轴承171。连接板122外侧设有导油件20，第一导油孔125、导油件20与连接板122之间空隙、第二导油孔126依次连通，构成润滑通道160。导油件20与行星架120铆接，导油件20将集油腔124中在离心作用下由第一导油孔125中甩出的润滑油引导至第二导油孔126。As shown in FIG5 , the planet carrier shaft 121 is provided with a connected oil collecting chamber 124 and a first oil guide hole 125. The oil collecting chamber 124 is located at the center of the planet carrier shaft 121, preferably coaxial with the planet carrier shaft 121. The planetary gear shaft 123 is provided with a second oil guide hole 126, and the outlet of the second oil guide hole 126 faces the planetary gear bearing 171 of the planetary gear row 100. An oil guide member 20 is provided on the outer side of the connecting plate 122. The first oil guide hole 125, the gap between the oil guide member 20 and the connecting plate 122, and the second oil guide hole 126 are connected in sequence to form a lubrication channel 160. The oil guide member 20 is riveted to the planet carrier 120, and the oil guide member 20 guides the lubricating oil in the oil collecting chamber 124 that is thrown out from the first oil guide hole 125 under the action of centrifugation to the second oil guide hole 126.
在一些实施例中，行星架轴121与太阳轮轴110之间设有中间轴承174，中间轴承174采用推力轴承，能够承受较大的轴向力，太阳轮轴110的一端通过该推力轴承抵在行星架轴121上，推力轴承能够满足行星排100在某些工况下行星架120与太阳轮轴110之间存在转速差的工作需求。该中间轴承174具***于太阳轮轴110的端部，在一些实施例中，可在太 阳轮轴110的端部设置一个内凹的轴承安装槽113，该轴承安装槽113与第一中空腔111连通，由此使得中间轴承174的内部空隙与第一中空腔111连通，第一中空腔111中的润滑油能够进入中间轴承174。In some embodiments, an intermediate bearing 174 is provided between the planet carrier shaft 121 and the sun gear shaft 110. The intermediate bearing 174 is a thrust bearing that can withstand a large axial force. One end of the sun gear shaft 110 is against the planet carrier shaft 121 through the thrust bearing. The thrust bearing can meet the working requirements of the planetary gear 100 when there is a speed difference between the planet carrier 120 and the sun gear shaft 110 under certain working conditions. The intermediate bearing 174 is specifically located at the end of the sun gear shaft 110. In some embodiments, the intermediate bearing 174 can be located at the end of the sun gear shaft 110. An inwardly concave bearing mounting groove 113 is provided at the end of the male wheel shaft 110 , and the bearing mounting groove 113 is connected to the first hollow cavity 111 , thereby making the internal gap of the intermediate bearing 174 connected to the first hollow cavity 111 , and the lubricating oil in the first hollow cavity 111 can enter the intermediate bearing 174 .
第二导油孔126可以是沿行星轮轴123径向和/或轴向延伸的通道，也可以是沿行星轮轴123周向延伸的通道，也就是说，第二导油孔126可以是轴向直通道、径向直通道、斜向直通道、曲线通道等，本公开不做限制。如图5所示，在一些实施例中，第二导油孔126包括沿行星轮轴123轴向延伸的轴向导油孔1261和至少一个沿行星轮轴123径向延伸的径向导油孔1262，径向导油孔1262的出口构成润滑通道160的出口。径向导油孔1262的数量根据行星轮轴承171的尺寸而定，通常设置为两个以上，两个以上径向导油孔1262的出口沿行星轮轴123的周向表面间隔、均匀分布，例如第二导油孔126包括沿行星轮轴123轴向延伸的轴向导油孔1261和四个沿行星轮轴123径向延伸的径向导油孔1262，四个径向导油孔1262互呈90°分布，保证油品到达行星轮轴承171，避免由于行星轮轴承171润滑不充分导致整个行星排100烧结。在一些实施例中，轴向导油孔1261的入口设置为扩口，扩口优选圆扩口，降低流阻。沿沿行星轮轴123的轴向，该扩口的孔径自中部向端部逐渐增加，便于润滑油进入轴向导油孔1261。The second oil guide hole 126 may be a channel extending radially and/or axially along the planetary gear shaft 123, or may be a channel extending circumferentially along the planetary gear shaft 123, that is, the second oil guide hole 126 may be an axial straight channel, a radial straight channel, an oblique straight channel, a curved channel, etc., which is not limited in the present disclosure. As shown in FIG. 5 , in some embodiments, the second oil guide hole 126 includes an axial oil guide hole 1261 extending axially along the planetary gear shaft 123 and at least one radial oil guide hole 1262 extending radially along the planetary gear shaft 123, and the outlet of the radial oil guide hole 1262 constitutes the outlet of the lubrication channel 160. The number of radial oil guide holes 1262 is determined according to the size of the planetary gear bearing 171, and is usually set to more than two. The outlets of the more than two radial oil guide holes 1262 are spaced and evenly distributed along the circumferential surface of the planetary gear shaft 123. For example, the second oil guide hole 126 includes an axial oil guide hole 1261 extending axially along the planetary gear shaft 123 and four radial oil guide holes 1262 extending radially along the planetary gear shaft 123. The four radial oil guide holes 1262 are distributed at 90 degrees to each other to ensure that the oil reaches the planetary gear bearing 171 and avoid sintering of the entire planetary gear row 100 due to insufficient lubrication of the planetary gear bearing 171. In some embodiments, the inlet of the axial oil guide hole 1261 is set to be a flared port, and the flared port is preferably a circular flared port to reduce flow resistance. Along the axial direction of the planetary gear shaft 123, the aperture of the flared port gradually increases from the middle to the end, so as to facilitate the entry of lubricating oil into the axial oil guide hole 1261.
在一些实施例中，行星架120上安装有第一行星架轴承172，第一行星架轴承172设置于润滑通道160中，第一行星架轴承172的内部空隙与润滑通道160连通，供润滑油流通。如图5所示，该第一行星架轴承172安装于行星架轴121上，并且靠近行星架120的连接板122，该第一行星架轴承172为推力轴承，推力轴承的松环与连接板122接触，推力轴承的紧环与外部固定构件(例如用于安装行星排100的壳体总成300)连接和/或接触，使得行星排轴向稳定。在松环与紧环之间则可形成供润滑油流通的通道，润滑油在松环与紧环之间流通时还可对推力轴承的滚子进行润滑。当然，在一些实施例中，还可将第一行星架轴承172设置在行星架120的其他位置，与润滑通道160完全分离，避免第一行星架轴承172的内部结构产生流阻。In some embodiments, a first planetary carrier bearing 172 is mounted on the planetary carrier 120, and the first planetary carrier bearing 172 is arranged in the lubrication channel 160, and the internal gap of the first planetary carrier bearing 172 is connected to the lubrication channel 160 for the circulation of lubricating oil. As shown in FIG5 , the first planetary carrier bearing 172 is mounted on the planetary carrier shaft 121 and is close to the connecting plate 122 of the planetary carrier 120. The first planetary carrier bearing 172 is a thrust bearing, and the loose ring of the thrust bearing is in contact with the connecting plate 122, and the tight ring of the thrust bearing is connected and/or in contact with an external fixed member (for example, a housing assembly 300 for mounting the planetary gear 100), so that the planetary gear 100 is axially stable. A channel for the circulation of lubricating oil can be formed between the loose ring and the tight ring, and the roller of the thrust bearing can also be lubricated when the lubricating oil circulates between the loose ring and the tight ring. Of course, in some embodiments, the first planetary carrier bearing 172 can also be arranged at other positions of the planetary carrier 120, and completely separated from the lubrication channel 160, so as to avoid the internal structure of the first planetary carrier bearing 172 from generating flow resistance.
在一些实施例中，为了提高行星架120的转动稳定性，行星架轴121上还安装有第二行星架轴承173，第二行星架轴承173采用滚针轴承，例如行星架120通过第二行星架轴承173安装于壳体中。第二行星架轴承173在工作时同样需要润滑，为此，行星架轴121设有与集油腔124连通的第三导油孔127，第三导油孔127的出口朝向第二行星架轴承173。总的来说，集油腔124要求能够容纳导油管10的近行星排100端，并且存储一定油液以输送至第三导油孔127。考虑到第二行星架轴承173所需润滑油相较于行星轮轴承171少，为了保证行星轮轴承171供油充足，在一些实施例中，集油腔124呈阶梯孔的结构，其大孔段1241用于容纳导油管10的近行星排100端，小孔段1242与第三导油孔127连通。In some embodiments, in order to improve the rotation stability of the planet carrier 120, a second planet carrier bearing 173 is further installed on the planet carrier shaft 121, and the second planet carrier bearing 173 adopts a needle bearing. For example, the planet carrier 120 is installed in the housing through the second planet carrier bearing 173. The second planet carrier bearing 173 also needs lubrication during operation. For this purpose, the planet carrier shaft 121 is provided with a third oil guide hole 127 connected to the oil collecting chamber 124, and the outlet of the third oil guide hole 127 faces the second planet carrier bearing 173. In general, the oil collecting chamber 124 is required to accommodate the end of the oil guide pipe 10 near the planetary row 100, and store a certain amount of oil to be transported to the third oil guide hole 127. Taking into account that the second planetary carrier bearing 173 requires less lubricating oil than the planetary wheel bearing 171, in order to ensure that the planetary wheel bearing 171 is adequately supplied with oil, in some embodiments, the oil collecting chamber 124 has a stepped hole structure, wherein the large hole section 1241 is used to accommodate the end of the oil guide pipe 10 near the planetary row 100, and the small hole section 1242 is connected to the third oil guide hole 127.
由于行星排100的行星架120、太阳轮轴110等存在轴向的制造和加工误差，太阳轮轴110与行星架120之间通常会存在一定的间隙，在某些极限的情况流入此部位的润滑油会通过该间隙大量的泄漏出去。如图4和图5所示，为了解决上述问题，在一些实施例中，太阳轮轴110内嵌入导油管10，导油管10贯通安装于行星排100的太阳轮轴110内部，具体是贯通安装于第一中空腔111中，且导油管10的近行星排100端伸入于集油腔124，以将太阳轮轴110内的油导入到行星架的集油腔124中。通过设置导油管10，在轴向导油通道比较长的情况下，采用导油管10将润滑油从远行星排100端的润滑油入口将油品传递到行星排100的行星架120中，可以避免由于太阳轮轴110高速运转所形成的离心力将油甩出无法到达行星排100的情况，并且导油管10的近行星排端伸入于集油腔124中，能够降低太阳轮轴110与行星架120之间间隙处的润滑油的泄漏量。润滑油在润滑通道160中流通，并最终流动至行星轮轴承171处，润滑各个行星轮140的轴承，保证该轴承的充分油量，避免整个行星排100的烧蚀导致的整车安全问题。Since the planet carrier 120, the sun gear shaft 110, etc. of the planetary gear row 100 have axial manufacturing and processing errors, there is usually a certain gap between the sun gear shaft 110 and the planet carrier 120. In some extreme cases, the lubricating oil flowing into this part will leak out through the gap in large quantities. As shown in Figures 4 and 5, in order to solve the above problems, in some embodiments, the sun gear shaft 110 is embedded with an oil guide pipe 10, and the oil guide pipe 10 is installed through the sun gear shaft 110 of the planetary gear row 100, specifically, it is installed through the first hollow cavity 111, and the end of the oil guide pipe 10 near the planetary gear row 100 extends into the oil collecting cavity 124 to guide the oil in the sun gear shaft 110 into the oil collecting cavity 124 of the planetary gear row. By providing the oil guide pipe 10, when the axial oil guide channel is relatively long, the oil guide pipe 10 is used to transfer the lubricating oil from the lubricating oil inlet at the end of the far planetary gear 100 to the planetary carrier 120 of the planetary gear 100, so as to avoid the situation that the oil is thrown out and cannot reach the planetary gear 100 due to the centrifugal force formed by the high-speed operation of the sun gear shaft 110, and the near planetary gear end of the oil guide pipe 10 extends into the oil collecting chamber 124, which can reduce the leakage of the lubricating oil at the gap between the sun gear shaft 110 and the planetary carrier 120. The lubricating oil circulates in the lubrication channel 160 and finally flows to the planetary gear bearing 171 to lubricate the bearings of each planetary gear 140, ensure sufficient oil volume of the bearing, and avoid the safety problem of the whole vehicle caused by the ablation of the entire planetary gear 100.
导油管10上设有若干沿导油管10轴向和/或径向间隔分布的出油孔11。沿导游管的轴向，出油孔11通常设置有多个，并且各出油孔11的孔径、孔距均相同。位于同一轴向位置 的出油孔11也可设置为多个，多个位于同一轴向位置的出油孔11沿周向间隔分布，使得油液能够均匀的流动至太阳轮轴110的第一中空腔111中。在导油管10的与轴承的安装位置所对应的轴向位置处还可额外开设出油孔11。The oil guide pipe 10 is provided with a plurality of oil outlet holes 11 spaced apart along the axial direction and/or radial direction of the oil guide pipe 10. There are usually a plurality of oil outlet holes 11 along the axial direction of the oil guide pipe, and the diameter and hole spacing of each oil outlet hole 11 are the same. The oil outlet holes 11 may also be provided in a plurality, and the plurality of oil outlet holes 11 located at the same axial position are spaced apart along the circumferential direction, so that the oil can flow evenly into the first hollow cavity 111 of the sun gear shaft 110. An additional oil outlet hole 11 may be provided at the axial position of the oil guide pipe 10 corresponding to the installation position of the bearing.
在一些实施例中，导油管10的远行星排100端设有一个以上出油口12，由于出油口12开设于导油管10的管壁上，因此能够径向出油，降低阻力，便于油液进入润滑通道160。出油口12可以设置为具有开口的槽或者完整的孔，例如出油口12可以为U型槽或者圆孔。出油口12的数量本公开不做限制，例如出油口12的数量设置为3个，则3个出油口12的形状可以相同或者不同。In some embodiments, the distal planetary gear 100 end of the oil guide tube 10 is provided with more than one oil outlet 12. Since the oil outlet 12 is provided on the tube wall of the oil guide tube 10, oil can be discharged radially, reducing resistance and facilitating oil to enter the lubrication channel 160. The oil outlet 12 can be set as a slot with an opening or a complete hole, for example, the oil outlet 12 can be a U-shaped slot or a circular hole. The number of the oil outlets 12 is not limited in the present disclosure. For example, if the number of the oil outlets 12 is set to 3, the shapes of the 3 oil outlets 12 can be the same or different.
由于第一中空腔111的内径大于导油管10的外径，为了保证导油管10稳定安装于第一中空腔111中，在一些实施例中，导油管10上套设有至少一个衬套30，衬套30填充导油管10与第一中空腔111的腔壁之间的间隙。衬套30起支撑导油管10的作用，衬套30的材质为铜或复合塑料。Since the inner diameter of the first hollow cavity 111 is larger than the outer diameter of the oil guiding tube 10, in order to ensure that the oil guiding tube 10 is stably installed in the first hollow cavity 111, in some embodiments, at least one bushing 30 is sleeved on the oil guiding tube 10, and the bushing 30 fills the gap between the oil guiding tube 10 and the cavity wall of the first hollow cavity 111. The bushing 30 plays a role in supporting the oil guiding tube 10, and the material of the bushing 30 is copper or composite plastic.
发动机输入轴总成610的太阳轮轴110与发电机620的转子621转动连接，如图4所示，在一些实施例中，发电机620的转子621设有沿轴向贯通的第二中空腔622，第二中空腔622和第一中空腔111连通，发电机620的转子与行星排100同轴设置，壳体总成300的进油通道303引入的润滑油经第二中空腔622引入行星排100的第一中空腔111，行星排润滑结构的导油管10安装于第二中空腔622和第一中空腔111中，导油管10的远行星排100端与壳体总成300的进油通道303直接对接连通，导油管10的近行星排100端与行星架120的集油腔124直接对接连通。通过将发电机620的转子与行星排100内部油路连通，使得电机的转子充当润滑油的管路，使得润滑***结构简化，提高了混合动力电驱动***1000的集成度和整车搭载性。The sun gear shaft 110 of the engine input shaft assembly 610 is rotatably connected to the rotor 621 of the generator 620, as shown in Figure 4. In some embodiments, the rotor 621 of the generator 620 is provided with a second hollow cavity 622 that penetrates along the axial direction, and the second hollow cavity 622 is connected to the first hollow cavity 111. The rotor of the generator 620 is coaxially arranged with the planetary row 100. The lubricating oil introduced into the oil inlet channel 303 of the housing assembly 300 is introduced into the first hollow cavity 111 of the planetary row 100 through the second hollow cavity 622. The oil guide pipe 10 of the planetary row lubrication structure is installed in the second hollow cavity 622 and the first hollow cavity 111. The far planetary row 100 end of the oil guide pipe 10 is directly connected to the oil inlet channel 303 of the housing assembly 300, and the near planetary row 100 end of the oil guide pipe 10 is directly connected to the oil collecting chamber 124 of the planetary carrier 120. By connecting the rotor of the generator 620 to the internal oil circuit of the planetary gear 100, the rotor of the motor acts as a pipeline for lubricating oil, which simplifies the structure of the lubrication system and improves the integration and vehicle mountability of the hybrid electric drive system 1000.
基于同样的发明构思，依据本公开的第二方面提供一种混合动力电驱动***1000。Based on the same inventive concept, a hybrid electric drive system 1000 is provided according to a second aspect of the present disclosure.
图8为依据本公开一些实施例的混合动力电驱动***的整体结构图；图9为图8的混合动力电驱动***拆除端盖后的结构示意图；图10为图8的混合动力电驱动***拆除右壳体后的结构示意图。如图8至图10所示，混合动力电驱动***1000可以包括壳体总成300、换挡机构总成500和上述混合动力变速机构总成600，换挡机构总成500和混合动力变速机构总成600均安装于壳体总成300中。在一些实施例中，壳体总成300设有轴齿腔302和电机腔301，混合动力变速机构总成600的发电机620和驱动电机670均安装于电机腔301中，换挡机构总成500以及混合动力变速机构总成600的发动机输入轴总成610、驱动电机输入轴总成660、ICE中间轴总成630、EV中间轴总成650和差速器轴总成640均安装于轴齿腔302中。FIG8 is an overall structural diagram of a hybrid electric drive system according to some embodiments of the present disclosure; FIG9 is a structural schematic diagram of the hybrid electric drive system of FIG8 after removing the end cover; and FIG10 is a structural schematic diagram of the hybrid electric drive system of FIG8 after removing the right housing. As shown in FIG8 to FIG10, the hybrid electric drive system 1000 may include a housing assembly 300, a shift mechanism assembly 500, and the hybrid transmission mechanism assembly 600, and the shift mechanism assembly 500 and the hybrid transmission mechanism assembly 600 are both installed in the housing assembly 300. In some embodiments, the housing assembly 300 is provided with a shaft gear cavity 302 and a motor cavity 301, the generator 620 and the drive motor 670 of the hybrid transmission mechanism assembly 600 are both installed in the motor cavity 301, and the shift mechanism assembly 500 and the engine input shaft assembly 610, the drive motor input shaft assembly 660, the ICE intermediate shaft assembly 630, the EV intermediate shaft assembly 650 and the differential shaft assembly 640 of the hybrid transmission mechanism assembly 600 are all installed in the shaft gear cavity 302.
为方便换挡机构总成500和混合动力变速机构总成600的安装，壳体总成300采用分体式结构，具体划分方式本公开不做限制，例如壳体总成300可以以水平面进行分割，形成上下两个壳体，或者以竖直面进行分割，形成左中右三个壳体。如图8所示，壳体总成300包括依次连接的右壳体310、左壳体320和端盖330，右壳体310与左壳体320合围成轴齿腔302。左壳体320和端盖330合围成电机腔301，发电机620和驱动电机670均位于电机腔301中。In order to facilitate the installation of the shift mechanism assembly 500 and the hybrid transmission mechanism assembly 600, the housing assembly 300 adopts a split structure. The specific division method is not limited in this disclosure. For example, the housing assembly 300 can be divided in a horizontal plane to form two upper and lower housings, or divided in a vertical plane to form three left, middle and right housings. As shown in Figure 8, the housing assembly 300 includes a right housing 310, a left housing 320 and an end cover 330 connected in sequence. The right housing 310 and the left housing 320 enclose a shaft gear cavity 302. The left housing 320 and the end cover 330 enclose a motor cavity 301, and the generator 620 and the drive motor 670 are both located in the motor cavity 301.
由于发动机输入轴总成610中轴较多，发电机620的转子621、行星排100的太阳轮轴110、内齿圈轴200均需要设置轴承进行安装支撑。为了增加轴承安装孔，在一些实施例中，左壳体320设有中间板321，中间板321呈罩体，与左壳体320通过螺纹紧固件或焊接固定连接。中间板321安装有用于支撑发电机620的转子621的球轴承179，如图4所示。为了进一步提高集成度，第二执行机构S2的结合齿42与中间板321固定连接，具体可以是在中间板321上直接加工出第二执行机构S2的结合齿42。在一些实施例中，也可将第二执行机构S2的结合齿42焊接或者过盈压装在中间板321上。Since there are many shafts in the engine input shaft assembly 610, the rotor 621 of the generator 620, the sun gear shaft 110 of the planetary gear 100, and the inner ring gear shaft 200 all need to be provided with bearings for installation support. In order to increase the bearing mounting holes, in some embodiments, the left housing 320 is provided with an intermediate plate 321, and the intermediate plate 321 is a cover body, which is fixedly connected to the left housing 320 by threaded fasteners or welding. The intermediate plate 321 is installed with a ball bearing 179 for supporting the rotor 621 of the generator 620, as shown in FIG. 4. In order to further improve the integration, the coupling teeth 42 of the second actuator S2 are fixedly connected to the intermediate plate 321, and specifically, the coupling teeth 42 of the second actuator S2 can be directly processed on the intermediate plate 321. In some embodiments, the coupling teeth 42 of the second actuator S2 can also be welded or interference-pressed on the intermediate plate 321.
图11为图8的混合动力电驱动***的中间板的结构示意图。如图11所示，中间板321上开设有用于设置轴承的轴承孔3211和用于避让换挡机构总成500的换挡拨叉的避让区3212， 将中间板321设置在左壳体320后，中间板321既能设置轴承，又能在中间板321与左壳体320之间形成一定的安装空间，可在中间板321与左壳体320之间设置换挡拨叉安装位，而且换挡拨叉能够通过中间板321上的避让区3212装入换挡拨叉安装位，使换挡拨叉的安装更为方便。进一步地，中间板321上开设有轴承孔3211用于设置发电机620转子的轴承，增加左壳体320整体的轴承安装孔的数量。在一些实施例中，发电机620的转子621通过两个轴承支撑在中间板321和端盖330上，行星排100的行星架轴121通过第一行星架轴承172和第二行星架轴承173支撑在右壳体310上。FIG11 is a schematic diagram of the structure of the middle plate of the hybrid electric drive system of FIG8. As shown in FIG11, the middle plate 321 is provided with a bearing hole 3211 for setting a bearing and an avoidance area 3212 for avoiding the shift fork of the shift mechanism assembly 500. After the middle plate 321 is set on the left housing 320, the middle plate 321 can be provided with a bearing, and a certain installation space can be formed between the middle plate 321 and the left housing 320. A shift fork installation position can be set between the middle plate 321 and the left housing 320, and the shift fork can be installed in the shift fork installation position through the avoidance area 3212 on the middle plate 321, making the installation of the shift fork more convenient. Further, a bearing hole 3211 is provided on the middle plate 321 for setting the bearing of the rotor of the generator 620, increasing the number of bearing installation holes of the entire left housing 320. In some embodiments, the rotor 621 of the generator 620 is supported on the middle plate 321 and the end cover 330 by two bearings, and the planetary carrier shaft 121 of the planetary gear 100 is supported on the right housing 310 by the first planetary carrier bearing 172 and the second planetary carrier bearing 173.
在一些实施例中，左壳体320的底部形成油底壳，润滑油在润滑混合动力变速机构总成600后的润滑油落入油底壳中。端盖330中设有进油通道303，进油通道303与发电机620的转子621的第二中空腔622连通。润滑油由外设的油泵提供泵油动力，使得润滑油在油底壳、进油通道303、导油管10(或者第二中空腔622和第一中空腔111)、润滑通道160中循环流通。In some embodiments, the bottom of the left housing 320 forms an oil pan, and the lubricating oil falls into the oil pan after lubricating the hybrid transmission mechanism assembly 600. An oil inlet channel 303 is provided in the end cover 330, and the oil inlet channel 303 is connected to the second hollow cavity 622 of the rotor 621 of the generator 620. The lubricating oil is pumped by an external oil pump, so that the lubricating oil circulates in the oil pan, the oil inlet channel 303, the oil guide pipe 10 (or the second hollow cavity 622 and the first hollow cavity 111), and the lubrication channel 160.
混合动力电驱动***1000还包括控制器总成400，控制器总成400用于控制电机和换挡机构总成500工作，当然控制器总成400还可控制油泵以及该混合动力电驱动***1000内部设置的一些传感器(温度传感器、压力传感器等)等电子设备的工作。控制器总成400可以与壳体总成300分开设置，通过导线连接。如图8所示，在一些实施例中，控制器总成400安装在壳体总成300上，控制器总成400中设有用于控制发电机620和驱动电机670的控制板、驱动板和IGBT，控制器总成400具有三项输出铜排，用于与发电机620和驱动电机670的三相输入铜排电连接。控制器总成400还具有低压线束，用于连接壳体总成300上或者壳体总成300内部的低压设备(传感器、泵等)。控制器总成400的具体结构可参考现有技术的相关公开，本公开不做限制。The hybrid electric drive system 1000 also includes a controller assembly 400, which is used to control the operation of the motor and the shift mechanism assembly 500. Of course, the controller assembly 400 can also control the operation of electronic devices such as the oil pump and some sensors (temperature sensors, pressure sensors, etc.) set inside the hybrid electric drive system 1000. The controller assembly 400 can be set separately from the housing assembly 300 and connected by wires. As shown in Figure 8, in some embodiments, the controller assembly 400 is installed on the housing assembly 300, and the controller assembly 400 is provided with a control board, a drive board and an IGBT for controlling the generator 620 and the drive motor 670. The controller assembly 400 has three output copper bars for electrical connection with the three-phase input copper bars of the generator 620 and the drive motor 670. The controller assembly 400 also has a low-voltage wiring harness for connecting low-voltage equipment (sensors, pumps, etc.) on the housing assembly 300 or inside the housing assembly 300. The specific structure of the controller assembly 400 can refer to the relevant disclosure of the prior art, and the present disclosure is not limited.
基于同样的发明构思，依据本公开的第三方面提供一种车辆，可以包括上述混合动力电驱动***1000，也就是说，该车辆为混合动力车辆，由发动机和电机提供动力。由于该车辆配置有上述混合动力电驱动***1000，因此至少具有上述混合动力电驱动***1000的技术方案所带来的所有有益效果，混合动力电驱动***1000集成度高、体积小，可搭载于于不同车型车辆的发动机舱内。该车辆的其他未详述结构均可参照现有技术的相关公开，此处不展开说明。Based on the same inventive concept, a vehicle is provided according to the third aspect of the present disclosure, which may include the hybrid electric drive system 1000, that is, the vehicle is a hybrid vehicle, powered by an engine and a motor. Since the vehicle is equipped with the hybrid electric drive system 1000, it at least has all the beneficial effects brought by the technical solution of the hybrid electric drive system 1000. The hybrid electric drive system 1000 has high integration and small size, and can be installed in the engine compartment of vehicles of different models. Other undetailed structures of the vehicle can refer to the relevant disclosure of the prior art, and will not be described here.
由本公开一些实施例的技术方案可知，本公开提供的混合动力变速机构总成，包括传动连接的发动机输入轴总成、发电机、ICE中间轴总成、差速器轴总成、EV中间轴总成、驱动电机输入轴总成和驱动电机。在一些实施例中发动机输入轴总成与发动机传动连接，发动机输入轴总成设有行星排、执行机构和挡位齿轮，因此能够实现挡位变换。也即本公开的混合动力变速机构总成能实现发动机+电机的混合动力输入，以及混动发动机多挡化。It can be seen from the technical solutions of some embodiments of the present disclosure that the hybrid transmission mechanism assembly provided by the present disclosure includes an engine input shaft assembly, a generator, an ICE intermediate shaft assembly, a differential shaft assembly, an EV intermediate shaft assembly, a drive motor input shaft assembly and a drive motor that are transmission-connected. In some embodiments, the engine input shaft assembly is transmission-connected to the engine, and the engine input shaft assembly is provided with a planetary gear, an actuator and a gear gear, so that gear shifting can be achieved. That is, the hybrid transmission mechanism assembly of the present disclosure can achieve hybrid power input of the engine + motor, and multi-gearing of the hybrid engine.
在结构设计上，本公开提供的混合动力变速机构总成，发动机输入轴总成与发电机同轴设置，驱动电机输入轴总成和驱动电机同轴设置，并且发电机和驱动电机位于同侧，在布置时能够将电机总成和轴齿总成分开放置，从而便于冷却润滑***的设计以及高低压分区。相比于现有技术中通过锥齿轮实现电机动力的换向传递，本公开采用电机与输入轴同轴设置的技术方案，能够缩小混合动力变速机构总成的单向尺寸。并且，发动机输入轴总成的安装高度位于驱动电机与差速器轴总成之间，发动机输入轴总成在竖直面上的投影与驱动电机和差速器轴总成在竖直面上的投影具有重合部分，相比于现有技术中各个总成“一”字型顺序排开的技术方案，本公开提供的混合动力变速机构总成，发动机输入轴总成的轴心、驱动电机的轴心与差速器轴总成的轴心呈三角形分布，不仅能够缩小混合动力变速机构总成的单向尺寸，而且三角形分布结构稳定，并且三角形分布能够为ICE中间轴总成和EV中间轴总成提供安装空间。通过上述结构设计能够降低该混合动力变速机构总成在垂直于发动机输入轴轴线的平面上的尺寸。In terms of structural design, the hybrid transmission mechanism assembly provided by the present disclosure has an engine input shaft assembly coaxially arranged with the generator, a drive motor input shaft assembly coaxially arranged with the drive motor, and the generator and the drive motor are located on the same side. When arranged, the motor assembly and the shaft gear assembly can be placed separately, thereby facilitating the design of the cooling and lubrication system and the high and low pressure partitioning. Compared with the prior art that realizes the reversing transmission of motor power through bevel gears, the present disclosure adopts a technical solution of coaxially arranging the motor and the input shaft, which can reduce the one-way size of the hybrid transmission mechanism assembly. Moreover, the installation height of the engine input shaft assembly is located between the drive motor and the differential shaft assembly, and the projection of the engine input shaft assembly on the vertical plane overlaps with the projection of the drive motor and the differential shaft assembly on the vertical plane. Compared with the technical solution in the prior art in which each assembly is arranged in a straight line, the axis of the engine input shaft assembly, the axis of the drive motor and the axis of the differential shaft assembly of the hybrid transmission mechanism assembly provided by the present disclosure are distributed in a triangular shape, which can not only reduce the one-way size of the hybrid transmission mechanism assembly, but also the triangular distribution structure is stable, and the triangular distribution can provide installation space for the ICE intermediate shaft assembly and the EV intermediate shaft assembly. The above structural design can reduce the size of the hybrid transmission mechanism assembly on a plane perpendicular to the axis of the engine input shaft.
沿发动机输入轴的轴线方向，本公开提供的混合动力变速机构总成，发动机输入轴总成设置有内齿圈轴，内齿圈轴整体可套设于行星排外，并且与行星排的内齿圈传动连接，充 当行星排的一部分。该内齿圈轴通过支撑轴承安装于壳体总成上，其上可设置多个构件的安装位，执行机构、支撑轴承和挡位齿轮均通过内齿圈轴安装固定。Along the axial direction of the engine input shaft, the hybrid transmission mechanism assembly provided by the present disclosure has an inner gear ring shaft, which can be sleeved outside the planetary gear and is drivingly connected to the inner gear ring of the planetary gear. The inner gear ring shaft is installed on the housing assembly through a support bearing, and multiple component installation positions can be set on it. The actuator, support bearing and gear are all installed and fixed through the inner gear ring shaft.
综上，相比于现有混合动力变速器，本公开提供的混合动力变速机构总成，通过内部总成的位置设计，能够缩小在沿发动机输入轴的轴线方向以及垂直于发动机输入轴轴线的平面上的尺寸，并且通过在发动机输入轴总成设置有内齿圈轴，可以同时集成行星排传动功能、执行机构安装、挡位齿轮安装以及必要的轴向限位功能，从而极大的提高混合动力变速机构总成的集成度，缩减混合动力变速机构总成在轴线方向上的功能体积，使其具备更灵活的布置和搭载性能。In summary, compared with the existing hybrid transmission, the hybrid transmission mechanism assembly provided by the present invention can reduce the size along the axial direction of the engine input shaft and on the plane perpendicular to the axis of the engine input shaft through the position design of the internal assembly, and by providing an inner ring shaft on the engine input shaft assembly, the planetary gear transmission function, actuator installation, gear gear installation and necessary axial limit function can be integrated at the same time, thereby greatly improving the integration of the hybrid transmission mechanism assembly, reducing the functional volume of the hybrid transmission mechanism assembly in the axial direction, so that it has more flexible layout and mounting performance.
尽管已描述了本公开的优选实施例，但本领域内的普通技术人员一旦得知了基本创造性概念，则可对这些实施例作出另外的变更和修改。所以，所附权利要求意欲解释为包括优选实施例以及落入本公开范围的所有变更和修改。Although the preferred embodiments of the present disclosure have been described, those skilled in the art may make additional changes and modifications to these embodiments once they have learned the basic creative concept. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications that fall within the scope of the present disclosure.
显然，本领域的技术人员可以对本公开进行各种改动和变型而不脱离本公开的精神和范围。这样，倘若本公开的这些修改和变型属于本公开权利要求及其等同技术的范围之内，则本公开也意图包含这些改动和变型在内。 Obviously, those skilled in the art can make various changes and modifications to the present disclosure without departing from the spirit and scope of the present disclosure. Thus, if these modifications and variations of the present disclosure fall within the scope of the claims of the present disclosure and their equivalents, the present disclosure is also intended to include these modifications and variations.

Claims (20)

  1. 一种混合动力变速机构总成，包括：传动连接的发动机输入轴总成、发电机、ICE中间轴总成、差速器轴总成、EV中间轴总成、驱动电机输入轴总成和驱动电机；A hybrid power transmission mechanism assembly includes: an engine input shaft assembly, a generator, an ICE intermediate shaft assembly, a differential shaft assembly, an EV intermediate shaft assembly, a drive motor input shaft assembly and a drive motor in driving connection;
    其中，所述发动机输入轴总成与所述发电机同轴设置，所述驱动电机输入轴总成和所述驱动电机同轴设置；所述发电机和所述驱动电机位于同侧；所述发动机输入轴总成的安装高度位于所述驱动电机与所述差速器轴总成之间，且所述发动机输入轴总成在竖直面上的投影与所述驱动电机和所述差速器轴总成在竖直面上的投影具有重合部分；The engine input shaft assembly is coaxially arranged with the generator, and the drive motor input shaft assembly is coaxially arranged with the drive motor; the generator and the drive motor are located on the same side; the installation height of the engine input shaft assembly is located between the drive motor and the differential shaft assembly, and the projection of the engine input shaft assembly on the vertical plane has an overlapping portion with the projection of the drive motor and the differential shaft assembly on the vertical plane;
    所述发动机输入轴总成包括行星排、至少一个执行机构、至少一个支撑轴承、至少一个挡位齿轮和内齿圈轴；所述内齿圈轴套设于所述行星排外，且所述内齿圈轴与所述行星排的内齿圈传动连接；所述至少一个执行机构、所述至少一个支撑轴承、所述至少一个挡位齿轮均设置于所述内齿圈轴上。The engine input shaft assembly includes a planetary row, at least one actuator, at least one support bearing, at least one gear gear and an inner ring gear shaft; the inner ring gear shaft is sleeved outside the planetary row, and the inner ring gear shaft is transmission-connected to the inner ring gear of the planetary row; the at least one actuator, the at least one support bearing and the at least one gear gear are all arranged on the inner ring gear shaft.
  2. 如权利要求1所述的混合动力变速机构总成，其中，所述EV中间轴总成的轴心位于所述发动机输入轴总成、所述驱动电机和所述差速器轴总成的轴心所围的三角形区域中；所述ICE中间轴总成的轴心的高度最低。The hybrid transmission mechanism assembly as described in claim 1, wherein the axis of the EV intermediate shaft assembly is located in a triangular area surrounded by the axes of the engine input shaft assembly, the drive motor and the differential shaft assembly; and the axis of the ICE intermediate shaft assembly has the lowest height.
  3. 如权利要求2所述的混合动力变速机构总成，其中，所述EV中间轴总成包括EV中间轴和安装于所述EV中间轴上的第一EV中间齿轮和第二EV中间齿轮，所述EV中间轴总成通过所述第一EV中间齿轮与所述发动机输入轴总成和所述驱动电机输入轴总成传动连接，所述EV中间轴总成通过所述第二EV中间齿轮与所述差速器轴总成传动连接。The hybrid transmission mechanism assembly as described in claim 2, wherein the EV intermediate shaft assembly includes an EV intermediate shaft and a first EV intermediate gear and a second EV intermediate gear mounted on the EV intermediate shaft, the EV intermediate shaft assembly is transmission-connected to the engine input shaft assembly and the drive motor input shaft assembly via the first EV intermediate gear, and the EV intermediate shaft assembly is transmission-connected to the differential shaft assembly via the second EV intermediate gear.
  4. 如权利要求2所述的混合动力变速机构总成，其中，所述ICE中间轴总成包括ICE中间轴和安装于所述ICE中间轴上的第一ICE中间齿轮和第二ICE中间齿轮；所述ICE中间轴总成通过所述第一ICE中间齿轮与所述发动机输入轴总成传动连接；所述ICE中间轴总成通过所述第二ICE中间齿轮与所述差速器轴总成传动连接。The hybrid transmission mechanism assembly as claimed in claim 2, wherein the ICE intermediate shaft assembly includes an ICE intermediate shaft and a first ICE intermediate gear and a second ICE intermediate gear mounted on the ICE intermediate shaft; the ICE intermediate shaft assembly is drivingly connected to the engine input shaft assembly through the first ICE intermediate gear; and the ICE intermediate shaft assembly is drivingly connected to the differential shaft assembly through the second ICE intermediate gear.
  5. 如权利要求1-4中任一项所述的混合动力变速机构总成，其中，所述内齿圈轴通过支撑轴承安装；所述内齿圈轴包括：The hybrid transmission mechanism assembly according to any one of claims 1 to 4, wherein the inner gear ring shaft is installed through a support bearing; the inner gear ring shaft comprises:
    轴套部，用于套设于所述行星排的太阳轮轴或行星架轴上，所述轴套部上设有至少一个用于安装所述执行机构的第一安装位；A shaft sleeve portion, used for sleeve-mounting on the sun gear shaft or the planet carrier shaft of the planetary gear, and the shaft sleeve portion is provided with at least one first mounting position for mounting the actuator;
    罩部，连接于所述轴套部，且用于与所述行星排的内齿圈传动连接；A cover portion, connected to the shaft sleeve portion and used for driving connection with the inner gear ring of the planetary gear;
    其中，所述罩部和/或所述轴套部设有至少一个用于设置所述支撑轴承的装配位；所述罩部和/或所述轴套部设有至少一个用于设置所述挡位齿轮的第二安装位。Wherein, the cover portion and/or the shaft sleeve portion is provided with at least one assembly position for arranging the support bearing; the cover portion and/or the shaft sleeve portion is provided with at least one second installation position for arranging the gear.
  6. 如权利要求5所述的混合动力变速机构总成，其中，所述罩部包括齿套部和挡板部，所述挡板部的内环连接所述轴套部、外环连接于所述齿套部。The hybrid transmission mechanism assembly as claimed in claim 5, wherein the cover portion includes a gear sleeve portion and a baffle portion, an inner ring of the baffle portion is connected to the shaft sleeve portion, and an outer ring is connected to the gear sleeve portion.
  7. 如权利要求6所述的混合动力变速机构总成，其中，所述齿套部与所述内齿圈为一体式结构或者键连接；所述轴套部、所述挡板部、所述齿套部为一体式结构。The hybrid transmission mechanism assembly as described in claim 6, wherein the gear sleeve portion and the inner gear ring are an integral structure or key-connected; the shaft sleeve portion, the baffle portion, and the gear sleeve portion are an integral structure.
  8. 如权利要求6所述的混合动力变速机构总成，其中，所述齿套部和所述轴套部均设有所述装配位；所述齿套部的装配位为内孔壁，所述轴套部的装配位上设有用于安装所述支撑轴承的轴套；The hybrid transmission mechanism assembly according to claim 6, wherein the gear sleeve portion and the shaft sleeve portion are both provided with the assembly position; the assembly position of the gear sleeve portion is an inner hole wall, and the assembly position of the shaft sleeve portion is provided with a shaft sleeve for mounting the support bearing;
    所述齿套部的装配位与所述内齿圈的安装处之间设有用于对所述支撑轴承轴向限位的限位结构。A limiting structure for axially limiting the support bearing is provided between the assembly position of the gear sleeve portion and the installation position of the inner gear ring.
  9. 如权利要求5所述的混合动力变速机构总成，其中，所述轴套部和/或所述罩部上设有至少一个贯通的导油孔；所述轴套部的外型面设有连通于所述导油孔的导油槽。The hybrid transmission mechanism assembly as claimed in claim 5, wherein at least one through oil guide hole is provided on the shaft sleeve portion and/or the cover portion; and an outer surface of the shaft sleeve portion is provided with an oil guide groove connected to the oil guide hole.
  10. 如权利要求5所述的混合动力变速机构总成，其中，所述至少一个执行机构包括第一执行机构和第二执行机构；所述至少一个支撑轴承包括第一支撑轴承和第二支撑轴承；所述至少一个挡位齿轮包括第一挡位齿轮和第二挡位齿轮； The hybrid transmission assembly as claimed in claim 5, wherein the at least one actuator comprises a first actuator and a second actuator; the at least one support bearing comprises a first support bearing and a second support bearing; the at least one gear comprises a first gear gear and a second gear gear;
    所述第一安装位、所述装配位、所述第二安装位均设有两个；两个所述第一安装位分布于所述轴套部的两端；两个所述装配位和两个所述第二安装位均分别设于所述轴套部和所述罩部上。There are two of each of the first installation position, the assembly position and the second installation position; the two first installation positions are distributed at both ends of the shaft sleeve portion; the two assembly positions and the two second installation positions are respectively arranged on the shaft sleeve portion and the cover portion.
  11. 如权利要求10所述的混合动力变速机构总成，其中，所述第一执行机构和所述第二执行机构分布于所述轴套部的两端；所述第一支撑轴承设于所述罩部的内孔中，所述第二支撑轴承通过轴套设于所述第一执行机构和所述第二执行机构之间；所述第一挡位齿轮通过轴承空套于所述罩部上，所述第二挡位齿轮通过轴承空套于所述轴套部上、且位于所述第一执行机构与所述第二支撑轴承之间；The hybrid transmission mechanism assembly as claimed in claim 10, wherein the first actuator and the second actuator are distributed at both ends of the sleeve portion; the first support bearing is arranged in the inner hole of the cover portion, and the second support bearing is arranged between the first actuator and the second actuator through a sleeve; the first gear gear is sleeved on the cover portion through a bearing, and the second gear gear is sleeved on the sleeve portion through a bearing and is located between the first actuator and the second support bearing;
    所述发动机输入轴总成通过所述第一挡位齿轮与所述EV中间轴总成传动连接；所述发动机输入轴总成通过所述第二挡位齿轮与所述ICE中间轴总成传动连接。The engine input shaft assembly is transmission-connected to the EV intermediate shaft assembly via the first gear position gear; the engine input shaft assembly is transmission-connected to the ICE intermediate shaft assembly via the second gear position gear.
  12. 如权利要求11所述的混合动力变速机构总成，其中，所述第一挡位齿轮包括齿圈部和连接部，所述齿圈部通过轴承空套于所述罩部上，所述连接部与所述第一执行机构的一侧的结合齿固定连接；所述第一执行机构的齿毂与所述第一安装位传动连接；所述第一执行机构的另一侧的结合齿与所述第二挡位齿轮固定连接。The hybrid transmission mechanism assembly as described in claim 11, wherein the first gear gear includes a ring gear portion and a connecting portion, the ring gear portion is loosely sleeved on the cover portion through a bearing, the connecting portion is fixedly connected to the coupling tooth on one side of the first actuator; the gear hub of the first actuator is transmission-connected to the first mounting position; and the coupling tooth on the other side of the first actuator is fixedly connected to the second gear gear.
  13. 如权利要求12所述的混合动力变速机构总成，其中，所述第二执行机构的齿毂与所述行星排的太阳轮轴传动连接，所述第二执行机构的一侧的结合齿与所述轴套部传动连接，所述第二执行机构的另一侧的结合齿与壳体总成固定连接。The hybrid transmission mechanism assembly as described in claim 12, wherein the gear hub of the second actuator is drivingly connected to the sun gear shaft of the planetary gear row, the coupling teeth on one side of the second actuator are drivingly connected to the sleeve portion, and the coupling teeth on the other side of the second actuator are fixedly connected to the housing assembly.
  14. 如权利要求1-4中任一项所述的混合动力变速机构总成，其中，所述行星排设有润滑通道，所述润滑通道的出口朝向所述行星排的行星轮轴承；所述行星排的太阳轮轴设有沿轴向贯通的第一中空腔，所述行星排的行星架设有集油腔；所述发电机的转子中设有沿轴向贯通的第二中空腔，所述第二中空腔、所述第一中空腔、所述集油腔和所述润滑通道依次连通。A hybrid transmission mechanism assembly as claimed in any one of claims 1 to 4, wherein the planetary row is provided with a lubrication channel, the outlet of the lubrication channel is directed toward the planetary wheel bearings of the planetary row; the sun wheel shaft of the planetary row is provided with a first hollow cavity extending axially therethrough, and the planet carrier of the planetary row is provided with an oil collecting cavity; the rotor of the generator is provided with a second hollow cavity extending axially therethrough, and the second hollow cavity, the first hollow cavity, the oil collecting cavity and the lubrication channel are sequentially connected.
  15. 如权利要求14所述的混合动力变速机构总成，其中，所述行星架包括依次连接的行星架轴、连接板和行星轮轴，所述行星架轴设有连通的所述集油腔和第一导油孔，所述行星轮轴设有第二导油孔；The hybrid transmission mechanism assembly according to claim 14, wherein the planet carrier comprises a planet carrier shaft, a connecting plate and a planetary gear shaft connected in sequence, the planet carrier shaft is provided with the oil collecting chamber and the first oil guide hole in communication, and the planetary gear shaft is provided with a second oil guide hole;
    所述连接板外侧设有导油件；所述第一导油孔、所述导油件与所述连接板之间空隙和所述第二导油孔依次连通，构成所述润滑通道。An oil guide piece is disposed on the outer side of the connecting plate; the first oil guide hole, the gap between the oil guide piece and the connecting plate, and the second oil guide hole are sequentially connected to form the lubrication channel.
  16. 如权利要求15所述的混合动力变速机构总成，其中，所述输入轴总成还包括导油管，所述导油管安装于所述第二中空腔和所述第一中空腔中，且所述导油管的近行星排端伸入于所述集油腔。The hybrid transmission mechanism assembly as claimed in claim 15, wherein the input shaft assembly further comprises an oil guide pipe, the oil guide pipe is installed in the second hollow cavity and the first hollow cavity, and the end of the oil guide pipe near the planetary gear row extends into the oil collecting cavity.
  17. 一种混合动力电驱动***，包括：A hybrid electric drive system comprising:
    壳体总成，设有轴齿腔和电机腔；The housing assembly is provided with a shaft gear cavity and a motor cavity;
    权利要求1-16中任一项所述的混合动力变速机构总成，所述混合动力变速机构总成中，发动机输入轴总成、所述驱动电机输入轴总成、所述ICE中间轴总成、所述EV中间轴总成和所述差速器轴总成均安装于所述轴齿腔中，所述发电机和所述驱动电机均安装于所述电机腔中；The hybrid transmission mechanism assembly according to any one of claims 1 to 16, wherein the engine input shaft assembly, the drive motor input shaft assembly, the ICE intermediate shaft assembly, the EV intermediate shaft assembly and the differential shaft assembly are all installed in the shaft gear cavity, and the generator and the drive motor are both installed in the motor cavity;
    换挡机构总成，安装于所述轴齿腔中，且作用于所述执行机构。The shift mechanism assembly is installed in the shaft gear cavity and acts on the actuator.
  18. 如权利要求17所述的混合动力电驱动***，其中，所述壳体总成包括依次连接的右壳体、左壳体和端盖，所述右壳体与所述左壳体合围成所述轴齿腔，所述左壳体和所述端盖合围成所述电机腔；所述端盖中设有进油通道。The hybrid electric drive system as described in claim 17, wherein the housing assembly includes a right housing, a left housing and an end cover connected in sequence, the right housing and the left housing together form the shaft gear cavity, and the left housing and the end cover together form the motor cavity; and an oil inlet channel is provided in the end cover.
  19. 如权利要求17或18所述的混合动力电驱动***，其中，所述混合动力电驱动***还包括控制器总成，所述控制器总成安装于所述壳体总成上，所述控制器总成的三项输出铜排与所述发电机和所述驱动电机的三相输入铜排电连接。The hybrid electric drive system as described in claim 17 or 18, wherein the hybrid electric drive system also includes a controller assembly, the controller assembly is mounted on the housing assembly, and the three-phase output copper busbars of the controller assembly are electrically connected to the three-phase input copper busbars of the generator and the drive motor.
  20. 一种车辆，包括权利要求17-19中任一项所述的混合动力电驱动***。 A vehicle comprising the hybrid electric drive system according to any one of claims 17 to 19.
PCT/CN2023/095712 2022-10-24 2023-05-23 Hybrid power transmission assembly, hybrid electric drive system, and vehicle WO2024087600A1 (en)

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