WO2024087635A1 - 一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆 - Google Patents

一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆 Download PDF

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Publication number
WO2024087635A1
WO2024087635A1 PCT/CN2023/098280 CN2023098280W WO2024087635A1 WO 2024087635 A1 WO2024087635 A1 WO 2024087635A1 CN 2023098280 W CN2023098280 W CN 2023098280W WO 2024087635 A1 WO2024087635 A1 WO 2024087635A1
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WO
WIPO (PCT)
Prior art keywords
gear
shaft
assembly
planetary
actuator
Prior art date
Application number
PCT/CN2023/098280
Other languages
English (en)
French (fr)
Inventor
刘宏
付丽
雷君
聂少文
刘欢
Original Assignee
东风汽车集团股份有限公司
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Application filed by 东风汽车集团股份有限公司 filed Critical 东风汽车集团股份有限公司
Publication of WO2024087635A1 publication Critical patent/WO2024087635A1/zh

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Classifications

    • 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
    • B60K6/365—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs characterised by apparatus, components or means specially adapted for HEVs characterised by the transmission gearings with the gears having orbital motion
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K6/00—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00
    • B60K6/20—Arrangement or mounting of plural diverse prime-movers for mutual or common propulsion, e.g. hybrid propulsion systems comprising electric motors and internal combustion engines ; Control systems therefor, i.e. systems controlling two or more prime movers, or controlling one of these prime movers and any of the transmission, drive or drive units Informative references: mechanical gearings with secondary electric drive F16H3/72; arrangements for handling mechanical energy structurally associated with the dynamo-electric machine H02K7/00; machines comprising structurally interrelated motor and generator parts H02K51/00; dynamo-electric machines not otherwise provided for in H02K see H02K99/00 the prime-movers consisting of electric motors and internal combustion engines, e.g. HEVs
    • B60K6/50—Architecture of the driveline characterised by arrangement or kind of transmission units
    • B60K6/54—Transmission for changing ratio
    • B60K6/547—Transmission for changing ratio the transmission being a stepped gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H55/00—Elements with teeth or friction surfaces for conveying motion; Worms, pulleys or sheaves for gearing mechanisms
    • F16H55/02—Toothed members; Worms
    • F16H55/17—Toothed wheels
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/021—Shaft support structures, e.g. partition walls, bearing eyes, casing walls or covers with bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H57/023—Mounting or installation of gears or shafts in the gearboxes, e.g. methods or means for assembly
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/04—Features relating to lubrication or cooling or heating
    • 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 planetary gear transmission devices, and in particular relates to an inner ring gear shaft, an input shaft assembly, a hybrid electric drive assembly and a vehicle.
  • the present invention provides an inner gear ring shaft, an input shaft assembly, a hybrid electric drive assembly and a vehicle.
  • an inner gear ring shaft By providing an inner gear ring shaft, multiple systems are highly integrated, the functional volume of the electric drive is reduced, and thus more flexible layout and loading performance are achieved.
  • an inner gear ring shaft which is used to be sleeved on the outside of a planetary gear row and installed on a housing assembly through a support bearing;
  • the inner gear ring shaft comprises: a sleeve portion, which is used to be sleeved on the sun gear shaft or the planetary carrier shaft of the planetary gear row, and the sleeve portion is provided with at least one first mounting position for installing an actuator; a cover portion, which is connected to the sleeve portion and is used for transmission connection with the inner gear ring of the planetary gear row; wherein the cover portion and/or the sleeve portion are provided with at least one assembly position for setting the support bearing; the cover portion and/or the sleeve portion are provided with at least one second mounting position for setting a gear.
  • an input shaft assembly comprising: a planetary gear for connecting to an engine, at least one actuator, at least one support bearing, at least one gear and the above-mentioned inner ring gear shaft; the inner ring gear shaft is sleeved on the sun gear shaft or the planetary carrier shaft of the planetary gear, and the cover portion of the inner ring gear shaft is transmission-connected to the inner ring gear of the planetary gear; the at least one actuator is installed on the at least one first installation position; the at least one support bearing is arranged on the at least one assembly position; and the at least one gear is arranged on the at least one second installation position.
  • a hybrid electric drive assembly comprising: a housing assembly; and the above-mentioned input shaft assembly, installed inside the housing assembly.
  • a vehicle comprising the hybrid electric drive assembly mentioned above; or, comprising the input shaft assembly mentioned above; or, comprising the inner gear ring shaft mentioned above.
  • FIG1 is a schematic diagram of the structure of an inner gear ring shaft according to some embodiments of the present disclosure
  • FIG2 is a full cross-sectional view of the inner gear ring shaft of FIG1 ;
  • FIG3 is a schematic structural diagram of an input shaft assembly according to some embodiments of the present disclosure.
  • FIG4 is a schematic structural diagram of an internal lubrication passage of the input shaft assembly of FIG3 ;
  • FIG5 is an overall structural diagram of a hybrid electric drive assembly according to some embodiments of the present disclosure.
  • FIG6 is a schematic diagram of the structure of the hybrid electric drive assembly of FIG5 after removing the end cover.
  • FIG. 7 is a schematic diagram of the structure of the hybrid electric drive assembly of FIG. 5 with the right housing removed.
  • 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.
  • 1000-hybrid electric drive assembly 300-housing assembly; 301-oil inlet channel; 302-shaft gear installation cavity; 303-motor installation cavity; 310-right housing; 320-left housing, 321-middle plate; 330-end cover.
  • an inner gear ring shaft 200 which can be sleeved outside the planetary gear row 100 as a whole and serve as a part of the planetary gear row 100.
  • the inner gear ring shaft 200 is installed on the housing assembly 300 through a support bearing, and multiple installation positions of components can be set on it.
  • FIG. 1 is a schematic structural diagram of the inner gear ring shaft according to some embodiments of the present disclosure
  • FIG. 2 is a full cross-sectional view of the inner gear ring shaft of FIG. 1.
  • 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 and can be sleeved on a shaft, such as the sun gear shaft 110 or the planet carrier shaft 121 of the planetary gear row 100.
  • the sleeve portion 210 has a relatively long axial dimension, and a plurality of first installation positions 230 for installing the actuator 40, or an assembly position 240 for setting the support bearing, and a second installation position 250 for setting the gear can be set on it along the axial direction.
  • the cover 220 is in transmission connection with the inner gear ring 150 of the planetary gear set 100, and participates in the operation of the planetary gear set 100 as a part of the planetary gear set 100.
  • the inner hole profile and the outer profile of the cover 220 can be used as the assembly position 240 for setting the support bearing or the second installation position 250 for setting the gear. Therefore, by setting the inner gear ring shaft 200, the transmission function of the planetary gear set 100, the installation of the actuator 40, the installation of the shift gear and the necessary axial limit function can be integrated at the same time, thereby greatly improving the integration of the electric drive system, reducing the functional volume of the electric drive, and making the electric drive system equipped with the inner gear ring shaft 200 have more flexible layout and loading performance.
  • 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 an integral 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 disposed on the main body of the planetary gear set 100.
  • the planetary gear 140 and the inner gear ring 150 are both located in the inner hole of the cover portion 220.
  • the cover portion 220 includes a gear sleeve portion 221 and a baffle portion 222, wherein 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, both of which are shaft sleeve structures, and 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, and the specific structural form of the baffle portion 222 is not limited in the present disclosure.
  • the shaft sleeve portion 210, the baffle portion 222, and the gear sleeve portion 221 may be an integrated structure, or may be fixedly connected by welding, bonding, screwing, or the like.
  • 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, and 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, and one side of the inner gear ring 150 is axially limited by the inner end face 262 of the baffle portion 222.
  • a retaining spring groove 261 is provided on the inner spline 223 of the gear sleeve 221.
  • 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.
  • 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 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.
  • a limiting structure 260 for axially limiting the actuator 40 is provided on the first installation position 230 to prevent axial relative rotation 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 coupling 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.
  • the retaining spring 70 is stuck in the retaining spring groove 261 after the gear hub 41 and/or the coupling tooth 42 of the actuator 40 are installed in place.
  • 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.
  • a shaft requires at least two bearings to be installed and fixed, so the number of assembly positions 240 is also more than two, and the more than two assembly positions 240 are distributed at intervals along the axial direction, that is, the gear sleeve part 221 and the sleeve part 210 are both provided with assembly positions 240.
  • the assembly position 240 of the cover part 220 is the inner hole wall 241 of the gear sleeve part 221, and the assembly position 240 of the sleeve part 210 is the polished rod section, and the support bearing is interference fit with the inner hole wall 241 and the polished rod section.
  • a limiting structure 260 for limiting the axial position of the corresponding support bearing is provided between the assembly position 240 of the gear sleeve 221 and the installation position of the inner gear ring 150.
  • the limiting structure 260 at this position can adopt end face limiting (such as shaft shoulder limiting, boss limiting) or retaining spring limiting. As shown in FIG.
  • a hole shoulder is formed between the inner hole wall 241 of the gear sleeve portion 221 and the inner spline 223 , and the support bearing installed on the inner hole wall 241 is axially limited by the hole shoulder.
  • a sleeve 80 is provided on the assembly position 240 of the sleeve portion 210, which can compensate for the diameter difference between the support bearing 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 support bearing 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 inner gear ring shaft 200 is suitable for a planetary gear transmission with gears, for example, a four-speed transmission requires at least two actuators 40 and at least two gears.
  • a hybrid power drive system realizes the engine's four gears through two synchronizers and two gears, and the two synchronizers and the two gears are respectively recorded as: the first actuator S1, the second actuator S2, the first gear 50 and the second gear 60.
  • the first actuator S1 and the second actuator S2 are both synchronizers, the first gear 50 is a large gear ring, which realizes the engine's third gear and the engine's fourth gear; the second gear 60 is a small gear ring, which realizes the engine's first gear and the engine's second gear.
  • FIG. 3 is a schematic diagram of the structure of the input shaft assembly according to some embodiments of the present disclosure. As shown in FIG. 3, in some embodiments, if the gear is connected to the inner gear ring shaft 200 in a transmission manner, no bearing is required.
  • the gear sleeve portion 221 and the shaft sleeve portion 210 are both provided with a second installation position 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 second mounting position 250 of the inner gear ring shaft 200 is provided with a limiting structure 260 for axially limiting the gear or the bearing of the gear, and the limiting structure 260 can be a limiting boss, a limiting step, or a groove for installing a retaining spring 70. If the limiting structure 260 is used to axially limit the bearing, a limiting boss, a limiting step, or a structural end face limiting is usually selected; if the limiting structure 260 is used to axially limit the gear, the gear is connected to the inner gear ring shaft 200 by transmission, such as a spline connection, and a retaining spring 70 is usually selected for axial limiting.
  • the outer surface of the sleeve part 210 is designed as a stepped shaft.
  • the outer diameter of the sleeve part 210 increases from the far planetary gear end to the near planetary gear end, and each structural part is mounted one by one on the sleeve part 210.
  • the stepped shaft itself can form a number of limiting steps for axial positioning.
  • a number of convex edges 263 are also provided on the stepped shaft to limit the sleeve 80, bearings and the like in the axial direction.
  • the inner gear ring shaft 200 is suitable for a planetary gear transmission with four gears, so there are 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.
  • 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.
  • the lubrication requirements of the multiple bearings and gears need to be guaranteed, so 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, an active lubrication solution is adopted.
  • 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 actual needs.
  • the oil guide groove 280 is an inwardly concave groove. By providing the oil guide groove 280, the lubricant flowing out of the oil guide hole 270 can be The oil is evenly distributed along the circumferential direction.
  • the oil guide groove 280 is a groove, the groove can also be used as a tool relief 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.
  • an input shaft assembly 900 is also provided, which can be applied to a hybrid electric drive assembly or a common gearbox, and the input shaft assembly 900 is connected to the output shaft of the engine.
  • FIG. 3 is a schematic structural diagram of an input shaft assembly according to some embodiments of the present disclosure
  • FIG. 4 is a schematic structural diagram of an internal lubrication channel of the input shaft assembly of FIG. 3 .
  • the input shaft assembly 900 may include a planetary gear 100, at least one actuator 40, at least one support bearing, at least one gear, and the inner ring gear shaft 200 of the first aspect of the present disclosure.
  • At least one actuator 40 of the input shaft assembly 900 is installed on at least one first mounting position 230 of the inner ring gear shaft 200; at least one support bearing of the input shaft assembly 900 is arranged on at least one assembly position 240 of the inner ring gear shaft 200; at least one gear of the input shaft assembly 900 is arranged on at least one second mounting position 250 of the inner ring gear shaft 200. That is to say, the number of the first installation position 230, the assembly position 240, and the second installation position 250 of the inner gear ring shaft 200 matches the number of the actuators 40, support bearings, and gears to be installed.
  • one shaft requires two support bearings for installation and support; the number of actuators 40 is positively correlated with the gear design, for example, one actuator 40 realizes two gears; the number of gears is related to the transmission design, and in some embodiments, the gears can be matched with the actuator 40 to achieve gear shifting, or can be used as transmission gears to cooperate with other gears to achieve speed ratio adjustment.
  • the input shaft assembly 900 integrates the actuator 40, the planetary gear 100 and the gear at the same time, and the above structure is integrated into one body through the inner gear ring shaft 200, so the integration is high and the axial size is small.
  • the planetary gear 100 is installed in the inner space of the inner gear ring shaft 200, and the actuator 40, the bearing and the gear are installed in the outer space, so that the input shaft assembly 900 can be assembled with the housing as an independent supply set during assembly, which reduces the assembly difficulty.
  • the input shaft assembly 900 is a sub-assembly of a single planetary gearbox 100 transmission mechanism that can realize the fourth gear of the engine.
  • the first actuator S1 and the second actuator S2 can use synchronizers (single or double) or clutches as needed.
  • the first support bearing 175 and the second support bearing 176 can use ball bearings, needle bearings, thrust bearings, etc. Some embodiments use ball bearings.
  • the first gear gear 50 and the second gear gear 60 both cooperate with the actuator 40 to achieve gear shifting.
  • the first actuator S1 and the second actuator S2 are distributed at both ends of the sleeve portion 210.
  • the first actuator S1/the second actuator S2 can be set to selectively connect the sun gear shaft 110 with the inner gear shaft 200, selectively connect the planetary carrier shaft 121 with the inner gear shaft 200, selectively connect the inner gear shaft 200 with the first gear position gear 50, or selectively connect the inner gear shaft 200 with the second gear position gear 60 according to actual needs.
  • the first actuator S1 adopts a synchronizer, having a gear hub 41 and coupling teeth 42 on both sides.
  • the gear hub 41 of the first actuator S1 is transmission-connected with the first mounting position 230; the coupling teeth 42 on one side of the first actuator S1 are fixedly connected with the first gear position gear 50; the coupling teeth 42 on the other side of the first actuator S1 are fixedly connected with the second gear position gear 60.
  • the first actuator S1 is used to selectively connect the inner gear shaft 200 with the first gear position gear 50 or the second gear position 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 support bearing 175 and the second support bearing 176 are respectively mounted on the sleeve portion 210 and the cover portion 220, the first support bearing 175 is disposed in the inner hole of the cover portion 220, and the second support bearing 176 is disposed in the first support bearing 175 through the sleeve 80.
  • the first actuator S1 and the second actuator S2 the first support bearing 175 and the second support bearing 176 mainly play the role of supporting the inner gear ring shaft 200, so both can use ball bearings.
  • the first support bearing 175 is axially limited by the end face 262 of the first mounting position 230, that is, the hole shoulder 264 formed by the first mounting position 230 of the cover part 220 and the supporting position; the second support bearing 176 is axially limited by the boss set 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 first gear gear 50 is loosely sleeved on the cover portion 220 through a needle bearing 177a
  • the second gear gear 60 is loosely 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.
  • the first gear gear 50 and the second gear gear 60 are both gear rings, and the bearings installed in their inner holes are needle bearings.
  • the first gear gear 50 and the second gear gear 60 can both rotate freely relative to the inner gear ring shaft 200.
  • the first gear 50 is a large gear ring.
  • the first gear 50 must not only meet the diameter requirement of being able to be mounted on the cover 220, but also meet the requirement of being connected to the first actuator S1 installed on the sleeve 210. Therefore, the first gear 50 can be configured to include a gear ring portion 51 and a connecting portion 52.
  • the gear ring portion 51 is similar in structure to the gear sleeve portion 221 of the inner gear ring shaft 200, both of which are sleeve structures.
  • the connecting portion 52 is similar in structure to the baffle portion 222 of the inner gear ring shaft 200, both of which are annular plate structures.
  • the gear ring portion 51 and the connecting portion 52 can be an integrally formed structure, or connected and fixed by welding or threaded fasteners.
  • the gear ring portion 51 is sleeved on the cover 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 220.
  • the connecting portion 52 is fixedly connected to the coupling tooth 42 on one side of the first actuator S1.
  • the connecting portion 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.
  • a thrust bearing 178 may be 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 sun gear shaft 110 or the planet carrier shaft 121 of the planetary row 100 is connected to the engine to realize the engine power input, and the inner gear ring shaft 200 is sleeved on the planet carrier shaft 121 or the sun gear shaft 110 of the planetary row 100 for output.
  • the inner gear ring shaft 200 and the planet carrier shaft 121 are used as outputs, and the inner gear ring shaft 200 is correspondingly sleeved on the planet carrier shaft 121.
  • the inner gear ring shaft 200 and the sun gear shaft 110 are used as outputs, and the inner gear ring shaft 200 is correspondingly sleeved on the sun gear shaft 110.
  • the cover portion 220 of the inner gear ring shaft 200 is transmission-connected to the inner gear ring 150 of the planetary row 100, and in some embodiments, it can be integrally formed, welded or keyed.
  • the inner gear ring shaft 200, the planet 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 a bearing needs to be installed between the inner gear ring shaft 200 and the sun gear shaft 110 or the planet carrier shaft 121.
  • the inner ring of the bearing is sleeved on the sun gear shaft 110 or the planet 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.
  • the input shaft assembly 900 is applied to a hybrid electric drive assembly and has a parallel mode of engine drive and motor drive.
  • the sun gear shaft 110 or the planetary carrier shaft 121 of the planetary row 100 of the input shaft assembly 900 is connected to the motor assembly 400.
  • the planetary row 100 adopts the planetary carrier shaft 121 as input, and the inner ring shaft 200 and the sun gear shaft 110 are used as outputs.
  • the inner ring shaft 200 is mounted on the sun gear shaft 110, and the sun gear shaft 110 is provided with a connection structure for transmission connection with the motor assembly 400; if the planetary row 100 adopts the sun gear shaft 110 as input, and the inner ring shaft 200 and the planetary carrier shaft 121 are used as outputs, then the inner ring shaft 200 is provided with a connection structure for transmission connection with the motor assembly 400.
  • the planetary gear row 100 of the input shaft assembly 900 adopts a technical solution in which the planetary carrier shaft 121 is input, and the inner ring gear shaft 200 and the sun gear shaft 110 are used as outputs, and the inner ring gear shaft 200 is sleeved on the sun gear shaft 110 .
  • the planetary gear 100 is the main part of the power distribution.
  • the lubrication of the planetary gear 100 is to ensure the normal operation of the input shaft assembly 900.
  • the main lubrication requirement of the planetary gear row 100 lies in the planetary gear bearings 171.
  • the planetary gear bearings 171 are numerous and widely distributed.
  • the installation position of the planetary gear bearings 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 difficult for the lubricating oil to enter the installation position of the planetary gear bearings 171 due to the obstruction of the planetary gear 140 and the planetary carrier 120. Therefore, the planetary gear bearings 171 are prone to ablation, affecting the use of the entire planetary gear row 100.
  • 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 in the axial direction.
  • 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 sequentially connected, 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 that are connected to the first hollow cavity 111, and the outlet of one of the plurality of fourth oil guide holes 112 faces the bearing between the sun gear shaft 110 and the inner gear ring shaft 200.
  • the lubrication channel 160 of the planet carrier 120 may be an oil channel opened in the base material of the planet 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, which may be 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 on 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 may be 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, and in other embodiments, may be coaxial with the planet carrier shaft 121.
  • the planetary wheel shaft 123 is provided with a second oil guide hole 126, and the outlet of the second oil guide hole 126 faces the planetary wheel bearing 171 of the planetary gear 100.
  • An oil guide member 20 is provided on the outer side of the connecting plate 122, and 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 guides the lubricating oil in the oil collecting chamber 124 that is thrown out of 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 and 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 under certain working conditions that there is a speed difference between the planet carrier 120 and the sun gear shaft 110.
  • the intermediate bearing 174 can be located at the end of the sun gear shaft 110.
  • a concave bearing mounting groove 113 can be provided at the end of the sun gear shaft 110.
  • the bearing mounting groove 113 is connected to the first hollow cavity 111, so that the internal gap of the intermediate bearing 174 is 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.
  • 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 number of the planetary gear bearings 171.
  • the diameter of the radial oil guide holes 1262 is determined by the size of the planetary gear shaft 123.
  • 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; the flared port can be 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 may be installed 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 FIG3 and FIG4, the first planetary carrier bearing 172 is installed 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 fixing member (for example, a housing assembly 300 for installing 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 also installed on the planet carrier shaft 121.
  • the second planet carrier bearing 173 adopts a needle bearing.
  • the planet carrier 120 is installed in the housing assembly 300 (for example, the right housing 310) 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 in the oil guide pipe 10, and the oil guide pipe 10 is installed through the sun gear shaft 110 of the planetary gear row 100, for example, 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 tube 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 tube 10.
  • a plurality of oil outlet holes 11 are usually provided along the axial direction of the oil guide tube, and the diameter and hole spacing of each oil outlet hole 11 are the same.
  • a plurality of oil outlet holes 11 located at the same axial position can also be provided, 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 can be provided at the axial position of the oil guide tube 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 structure of the input shaft assembly 900 can be set as follows:
  • the inner gear ring shaft 200 is supported on the right housing and the left housing of the housing assembly 300 by a ball bearing (first support bearing 175) and a ball bearing (second support bearing 176) mounted on the sleeve 80.
  • first support bearing 175 On the outer side of the inner gear ring shaft 200, the large gear ring (first gear 50) is welded to the coupling tooth 42 on one side of the first synchronizer (first actuator S1) and is sleeved on the inner gear ring shaft 200 by a needle bearing 177a and a thrust bearing 178 to freely rotate around the inner gear ring shaft 200.
  • the needle bearing 177a is axially limited by a shaft shoulder, and the thrust bearing 178 cooperates with the end face 262 of the inner gear ring shaft 200 for axial limitation.
  • the gear hub 41 of the first synchronizer is connected to the outer spline of the inner gear ring shaft 200 through the inner spline to transmit torque, and the gear hub 41 of the first synchronizer is axially limited by the end face 262 of the inner gear ring shaft 200 and the retaining spring 70 installed in the retaining spring groove 261; the small ring gear (second gear 60) is welded to the combined tooth 42 of the first synchronizer and then installed on the outer side of the sleeve part 210 of the inner gear ring shaft 200 through the needle bearing 177c, so as to rotate freely around the inner gear ring shaft 200.
  • the small ring gear (second gear 60) is axially limited by a sleeve 80 pressed onto the axial diameter of the inner ring gear shaft 200, and the needle bearing 177c is axially limited by the shoulders on both sides;
  • the coupling tooth 42 on one side of the second synchronizer (second actuator S2) is connected to the external spline of the inner ring gear shaft 200 through an internal spline for power transmission, and the coupling tooth 42 of the second synchronizer is axially limited by the end face 262 of the sleeve 80 and the retaining spring 70 installed in the retaining spring groove 261.
  • the sun gear shaft 110 is supported in the inner hole 201 of the inner gear ring shaft 200 through two needle bearings 177b.
  • the gear hub 41 of the first synchronizer is connected to the outer spline of the sun gear shaft 110 through the inner spline for torque transmission.
  • the outer spline at the end of the sun gear shaft 110 is connected to the inner spline of the motor shaft of the generator 401 for power transmission; the motor shaft is supported on the middle plate 321 of the left housing 320 through the ball bearing 179.
  • the inner gear ring 150 is matched with the inner spline of the inner gear ring shaft 200 through the outer spline, and is connected with the inner gear ring shaft 200 to rotate together.
  • the inner gear ring 150 is axially limited by the end face 262 of the inner gear ring shaft 200 and the retaining spring 70 installed in the retaining spring groove 261.
  • the inner gear ring 150 supports the entire planetary gear system on the inner gear ring shaft 200 by meshing with the planetary gears.
  • the planet carrier 120 is mounted on the right housing through a needle bearing (the second planet carrier shaft 121 bears 173), the planet carrier shaft 121 is pressed onto the connecting plates 122 on both sides of the planet carrier 120 by interference fit, and the planetary gear 140 is mounted on the planet carrier shaft 121 through a needle bearing (planetary gear bearing 171), and the planetary gear 140 is respectively meshed with the inner ring gear 150 and the sun gear 130.
  • the entire planetary gear system integrates the first actuator S1 and the second actuator S2, the 1/2 gear ring (the second gear 60) and the 3/4 gear ring (the first gear 50), and the planetary gear 100 through the inner gear ring shaft 200, and is connected to the motor through the inner side supporting sun gear shaft 110, and also integrates the lubrication system of the planetary gear bearing 171, the actuator 40, the gear gear and related bearings, and the cooling system of the motor.
  • the inner gear ring shaft 200 provides a support structure for each system through the inner and outer surfaces, and is installed on the left and right shells of the shell assembly through the first support bearing 175 and the second support bearing 176 on both sides, so that the input shaft assembly 900 can be highly integrated, reducing the arrangement and installation positions and interfaces of other parts, so that the axial and radial dimensions of the electric drive system equipped with the input shaft assembly 900 can be reduced, reducing the functional volume of the electric drive system, reducing costs and enhancing its carrying capacity, making the product more competitive.
  • FIG. 5 is an overall structural diagram of the hybrid electric drive assembly according to the third aspect of the present disclosure
  • FIG. 6 is a structural schematic diagram of the hybrid electric drive assembly of FIG. 5 after the end cover is removed
  • FIG. 7 is a structural schematic diagram of the hybrid electric drive assembly of FIG. 5 after the right shell is removed.
  • the hybrid electric drive assembly 1000 may include a shell assembly 300 and the input shaft assembly 900 of the second aspect of the present disclosure, and the input shaft assembly 900 is installed inside the shell assembly 300.
  • the structure of the shell assembly 300 is designed according to the structure of the input shaft assembly 900, and it only needs to meet the installation requirements of the input shaft assembly 900, and the specific structure is not limited by the present disclosure.
  • the hybrid electric drive assembly 1000 may further include a motor assembly 400 connected to the housing assembly 300.
  • the motor assembly 400 may be configured to include only one motor, or more than two motors.
  • the motor assembly 400 is connected to the sun gear shaft 110 of the planetary gear row 100 to achieve power transmission between the motor and the planetary gear row 100.
  • the motor assembly 400 may include a generator 401 and a drive motor 402, and the rotor of the generator 401 is connected to the sun gear shaft 110 of the planetary gear row 100 by a transmission connection, for example, the rotor of the generator 401 is connected to the sun gear shaft 110 of the planetary gear row 100 by a spline.
  • the motor assembly 400 may be set to be integrated inside the housing assembly 300, or the motor assembly 400 may be external. In order to improve the integration of the hybrid electric drive assembly 1000, some embodiments adopt a solution in which the motor is built in.
  • the housing assembly 300 may include 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 installation cavity 302.
  • the planetary gear row 100 is located in the shaft gear installation cavity 302.
  • the planetary carrier shaft 121 is supported on the right housing 310 through the first planetary carrier bearing 172 and the second planetary carrier bearing 173.
  • the left housing 320 and the end cover 330 enclose a motor installation cavity 303, and the motor assembly 400 is located in the motor installation cavity 303.
  • the rotor 410 of the generator 401 is supported on the left housing 320 and the end cover 330 through two bearings.
  • the rotor 410 of the generator 401 is provided with a second hollow cavity 411 which penetrates axially, the oil inlet channel 301, the second hollow cavity 411 and the first hollow cavity 111 are connected in sequence, the rotor 410 of the motor assembly 400 is coaxially arranged with the planetary row 100, the lubricating oil introduced into the oil inlet channel 301 of the housing assembly 300 is introduced into the first hollow cavity 111 of the planetary row 100 through the second hollow cavity 411, the oil guide pipe 10 of the planetary row lubrication structure is installed in the second hollow cavity 411 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 301 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 cavity 124 of the planetary carrier 120.
  • the rotor 410 of the motor assembly 400 By connecting the rotor 410 of the motor assembly 400 in series with 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 assembly 1000.
  • An oil inlet channel 301 is provided in the end cover 330, and an oil pan is formed at the bottom of the left housing 320.
  • the lubricating oil after lubricating the planetary gear 100 falls into the oil pan, and the external oil pump provides oil pumping power, so that the lubricating oil circulates in the oil pan, the oil inlet channel 301, the oil guide pipe 10, and the lubrication channel 160.
  • 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 410 of the generator 401, as shown in FIG3.
  • the coupling teeth 42 of the actuator (specifically the second actuator S2) close to the generator 401 are fixedly connected to the intermediate plate 321, and specifically, the coupling teeth of the actuator can be directly processed on the intermediate plate 321.
  • the hybrid electric drive assembly 1000 may further include a shift mechanism assembly 500, an intermediate shaft gear assembly 600, a differential assembly 700 and a controller assembly 800; the shift mechanism assembly 500, the intermediate shaft gear assembly 600 and the differential assembly 700 are all located in the shaft gear installation cavity 302; the shift mechanism assembly 500 and the intermediate shaft gear assembly 600 cooperate with the planetary gear 100 to realize the speed change and shifting functions, and the power is output to the wheel shaft system by the differential assembly 700.
  • the controller assembly 800 is installed outside the housing assembly 300 and is used to control the operation of the motor assembly 400 and/or the shift mechanism assembly 500.
  • controller assembly 800 can also control the operation of the oil pump and some sensors (temperature sensors, pressure sensors, etc.) and other electronic devices set inside the hybrid electric drive assembly 1000.
  • the specific contents of the shift mechanism assembly 500, the intermediate shaft gear assembly 600, and the controller assembly 800 may refer to the relevant disclosures of the prior art and will not be elaborated here.
  • a vehicle is provided according to the fourth aspect of the present disclosure, including the hybrid electric drive assembly 1000 of the third aspect of the present disclosure, 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 assembly 1000 of the third aspect of the present disclosure, it has at least all the beneficial effects brought by the technical solution of the third aspect of the present disclosure.
  • the hybrid electric drive assembly 1000 has high integration and small size, and can be installed in the engine compartment of vehicles of different models. Other structures of the vehicle that are not described in detail can refer to the relevant disclosure of the prior art, and will not be described in detail here.
  • a vehicle including the input shaft assembly 900 of the second aspect of the present disclosure, that is, the vehicle can be a hybrid vehicle or a pure electric vehicle or a common fuel vehicle, powered by an engine and/or a motor, and the input shaft assembly 900 of the second aspect of the present disclosure can achieve the effect of shifting and changing speed.
  • the vehicle can be a hybrid vehicle or a pure electric vehicle or a common fuel vehicle, powered by an engine and/or a motor
  • the input shaft assembly 900 of the second aspect of the present disclosure can achieve the effect of shifting and changing speed.
  • Other structures of the vehicle not described in detail can refer to the relevant disclosure of the prior art, and will not be described here.
  • a vehicle including the inner gear ring shaft of the first aspect of the present disclosure, that is, the vehicle can be a hybrid vehicle or a pure electric vehicle or a common fuel vehicle, powered by an engine and/or a motor, and the inner gear ring shaft of the first aspect of the present disclosure can be applied to the gearbox of the vehicle, or the wheel hub motor system.
  • the inner gear ring shaft of the first aspect of the present disclosure can be applied to the gearbox of the vehicle, or the wheel hub motor system.
  • Other undetailed structures of the vehicle can refer to the relevant disclosure of the prior art, and will not be described here.
  • the inner gear ring shaft provided in the embodiments of the present disclosure can be sleeved outside the planetary gear row as a whole and serve as a part of the planetary gear row.
  • the inner gear ring shaft is installed on the housing assembly through a support bearing, and multiple installation positions of components can be set on it.
  • the inner gear ring shaft includes a sleeve portion and a cover portion, and the sleeve portion is used to be sleeved on the sun gear shaft or the planetary carrier shaft of the planetary gear row.
  • a number of first installation positions for installing the actuator can be set axially thereon, or a mounting position for setting the support bearing, and a second mounting position for setting the gear.
  • the cover portion is connected to the inner gear ring of the planetary gear row in a transmission manner, and participates in the operation of the planetary gear row as a part of the planetary gear row.
  • the inner hole profile and the outer profile of the cover portion can be used as the mounting position for setting the support bearing or the second mounting position for setting the gear. Therefore, by setting the inner gear ring shaft, the planetary gear transmission function, the actuator installation, the shift gear installation and the necessary axial limit function can be integrated at the same time, thereby greatly improving the integration of the electric drive system, reducing the functional volume of the electric drive, and making the electric drive system provided with the inner gear ring shaft have more flexible layout and loading performance.
  • the disclosed embodiment provides a highly integrated planetary gear input shaft assembly, which arranges and supports various systems through an inner ring gear shaft, effectively reducing the layout space of the assembly, reducing costs, making the structure more compact and more mountable, and making the product more competitive.

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Abstract

一种内齿圈轴(200)、输入轴总成(900)、混合动力电驱动总成(1000)及车辆。该内齿圈轴(200)，整体可套设于行星排(100)外，充当行星排(100)的一部分，该内齿圈轴(200)通过支撑轴承安装于壳体总成(300)上，其上可设置多个构件的安装位，并且该内齿圈轴(200)与行星排(100)的内齿圈传动连接，作为行星排(100)的一部分参与行星排的运行。

Description

一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆
相关申请的交叉引用
本申请要求于2022年10月24日提交的申请号为202211306028.9的中国专利申请的优先权，其全部内容通过引用并入本文。
技术领域
本公开属于行星排传动装置技术领域，具体涉及一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆。
背景技术
随着电驱动***的发展，多合一逐渐成为一大趋势，高度集成可以减小零部件重量、降低成本、减小整车负载、增强电驱动总成的搭载性。对于负载的混动***来说，除了高度集成外，紧凑的结构布置也是其减小体积，增强搭载性的一个重要维度。
现有技术中混合动力电驱动总成的相关研究多集中于功率分流传动架构、动力分配模式等角度，例如公开号为CN110303865A中国发明申请“串联双电机差速功率分流的无级变速传动***”，公开了一种功率分流传动架构。而针对混合动力电驱动高集成度、低功能体积的研究罕见记载。
发明内容
为解决上述技术问题，本公开提供一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆。通过设置内齿圈轴将多个***进行高度集成，缩减电驱动的功能体积，从而具备更灵活的布置和搭载性能。
依据本公开的第一方面，提供了一种内齿圈轴，用于套设于行星排外、且通过支撑轴承安装于壳体总成上；所述内齿圈轴包括：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执行机构的第一安装位；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；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齿轮的第二安装位。
依据本公开的第二方面提供了一种输入轴总成，包括：用于连接发动机的行星排、至少一个执行机构、至少一个支撑轴承、至少一个齿轮和上述的内齿圈轴；所述内齿圈轴套设于所述行星排的太阳轮轴或行星架轴上，且所述内齿圈轴的罩部与所述行星排的内齿圈传动连接；所述至少一个执行机构安装于所述至少一个第一安装位上；所述至少一个支撑轴承设置于所述至少一个装配位上；所述至少一个齿轮设置于所述至少一个第二安装位上。
依据本公开的第三方面提供了一种混合动力电驱动总成，包括：壳体总成；上述的输入轴总成，安装于所述壳体总成内部。
依据本公开的第四方面提供了一种车辆，包括上述的混合动力电驱动总成；或者，包括上述的输入轴总成；或者，包括上述的内齿圈轴。
附图说明
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。
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。
图1为依据本公开一些实施例的内齿圈轴的结构示意图；
图2为图1的内齿圈轴的全剖图；
图3为依据本公开一些实施例的输入轴总成的结构示意图；
图4为图3的输入轴总成的内部润滑通道的结构示意图；
图5为依据本公开一些实施例的混合动力电驱动总成的整体结构图；
图6为图5的混合动力电驱动总成拆除端盖后的结构示意图；以及
图7为图5的混合动力电驱动总成拆除右壳体后的结构示意图。
附图标记说明：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。
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。
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。
1000-混合动力电驱动总成；300-壳体总成；301-进油通道；302-轴齿安装腔；303-电机安装腔；310-右壳体；320-左壳体，321-中间板；330-端盖。400-电机总成，401-发电机，402-驱动电机；410-转子，411-第二中空腔；500-换挡机构总成；600-中间轴齿总成；700-差速器总成；800-控制器总成；900-输入轴总成。
具体实施方式
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。
依据本公开的第一方面提供一种内齿圈轴200，该内齿圈轴200整体可套设于行星排100外，充当行星排100的一部分，该内齿圈轴200通过支撑轴承安装于壳体总成300上，其上可设置多个构件的安装位。图1为依据本公开一些实施例的内齿圈轴的结构示意图；图2为图1的内齿圈轴的全剖图。如图1和图2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、换挡齿轮安装以及必要的轴向限位功能，从而极大的提供电驱动***的集成度，缩减电驱动的功能体积，使得设备有该内齿圈轴200的电驱动***具备更灵活的布置和搭载性能。
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。
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。
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。
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。
上述构件安装位中，第一安装位230均设于轴套部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。
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。
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。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。
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。通常，一根轴需要至少两个轴承安装固定，因此装配位240的数量同样为两个以上，两个以上装配位240沿轴向间隔分布，也即齿套部221和轴套部210均设有装配位240。在一些实施例中，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，支撑轴承与内孔壁241以及光杆段均过盈配合。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对应的支撑轴承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2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，通过孔肩对内孔壁241上安装的支撑轴承进行轴向限位。
在一些实施例中，轴套部210的装配位240上设有轴套80，一方面可以弥补支撑轴承与光杆段的直径差，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，支撑轴承过盈安装与轴套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。
在一些实施例中，内齿圈轴200适用于具有挡位的行星齿轮变速器中，例如四挡变速器至少需要两个执行机构40和至少两个挡位齿轮。以公开号CN113232501A的中国发明申请“一种混合动力驱动***”为例，该混合动力驱动***通过两个同步器和两个挡位齿轮实现发动机四挡，两个同步器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。
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。图3为依据本公开一些实施例的输入轴总成的结构示意图。如图3所示，在一些实施例中，若齿轮与内齿圈轴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。
该内齿圈轴200的第二安装位250设有用于对齿轮或齿轮的轴承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、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，在一些实施例中可以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。
在一些实施例中，内齿圈轴200适用于具有四挡的行星齿轮变速器中，因此第一安装位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。
在一些实施例中，由于内齿圈轴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，因此可以采用飞溅润滑或主动润滑的方式，又由于内齿圈轴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，采用了主动润滑方案。
在一些实施例中，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。
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。
基于同样的发明构思，依据本公开第二方面还提供了一种输入轴总成900，该输入轴总成900可应用于混合动力电驱动总成或者普通的变速箱中，该输入轴总成900与发动机的输出轴连接。图3为依据本公开一些实施例的输入轴总成的结构示意图；图4为图3的输入轴总成的内部润滑通道的结构示意图。如图3和图4所示，输入轴总成900可以包括行星排100、至少一个执行机构40、至少一个支撑轴承、至少一个齿轮和上述本公开第一方面的内齿圈轴200。该输入轴总成900的至少一个执行机构40安装于内齿圈轴200的至少一个第一安装位230上；该输入轴总成900的至少一个支撑轴承设置于内齿圈轴200的至少一个装配位240上；该输入轴总成900的至少一个齿轮设置于内齿圈轴200的至少一个第二安装位250上。也就是说，内齿圈轴200的第一安装位230、装配位240和第二安装位250的数量与待安装的执行机构40、支撑轴承、齿轮的数量相匹配。通常，一根轴需要两个支撑轴承安装支撑；执行机构40的数量与挡位设计正相关，例如一个执行机构40实现两个挡位；齿轮的数量与变速器设计有关，在一些实施例中齿轮可以是与执行机构40相配合实现换挡，也可以是作为传动齿轮与其他齿轮相配合实现速比调整。
该输入轴总成900由于同时集成了执行机构40、行星排100和齿轮，并且上述结构通过内齿圈轴200集成为一体，集成度高，并且轴向尺寸小。内齿圈轴200内部空间安装行星排100、外部空间安装执行机构40、轴承和齿轮，使得该输入轴总成900在装配时能够作为一个独立的供货集与壳体进行装配，降低了装配难度。
在一些实施例中，该输入轴总成900为可实现发动机四挡的单行星排100变速机构分总成。执行机构40设置有两个，分别为第一执行机构S1和第二执行机构S2，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。支撑轴承同样设置两个，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。齿轮同样设置两个，分别为第一挡位齿轮50和第二挡位齿轮60，第一挡位齿轮50和第二挡位齿轮60均与执行机构40配合，实现换挡。
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/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。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。为了提高该输入轴总成900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。
在一些实施例中，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。
在一些实施例中，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均为齿圈，其内孔中安装的轴承为滚针轴承，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可以设置为包括齿圈部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。
为了进一步提高该输入轴总成900的轴向承载能力，如图3所示，连接部52与罩部220之间设有推力轴承178。在一些实施例中连接部52与挡板部222之间可以设有推力轴承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。
如图3所示，该输入轴总成900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，内齿圈轴200套设于行星排100的用于输出的行星架轴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。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。内齿圈轴200的罩部220与行星排100的内齿圈150传动连接，在一些实施例中可采用一体成型、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。
在一些实施例中，该输入轴总成900应用于混合动力电驱动总成、且具有发动机驱动和电机驱动的并联模式，该输入轴总成900的行星排100的太阳轮轴110或行星架轴121与电机总成400连接，例如行星排100采用行星架轴121输入，内齿圈轴200和太阳轮轴110作为输出，内齿圈轴200套装于太阳轮轴110上，则太阳轮轴110上设有用于与电机总成400传动连接的连接结构；若行星排100采用太阳轮轴110输入，内齿圈轴200和行星架轴121作为输出，则内齿圈轴200上设有用于与电机总成400传动连接的连接结构。在一些实施例中，该输入轴总成900的行星排100采用行星架轴121输入，内齿圈轴200和太阳轮轴110作为输出的技术方案，内齿圈轴200套设于太阳轮轴110上。
行星排100是功率分流的主要零件，行星排100的润滑是保证该输入轴总成900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。
为了改善行星排100的润滑情况，如图4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。
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，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。
如图4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。
在一些实施例中，行星架轴121可以设有连通的集油腔124和第一导油孔125，集油腔124位于行星架轴121的中心，在另一些实施例中可以与行星架轴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。
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可以位于太阳轮轴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。
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。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；扩口可以为圆扩口，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。
在一些实施例中，行星架120上可以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3和图4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。
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安装于壳体总成300(例如是右壳体310)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。
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。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，例如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。
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。
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。
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。
在一些实施例中，以公开号CN113232501A的中国发明申请“一种混合动力驱动***”()的输入轴总成900为例，输入轴总成900的结构可以如下设置：
内齿圈轴200通过球轴承(第一支撑轴承175)以及安装于轴套80上的球轴承(第二支撑轴承176)分别支撑在壳体总成300的右壳体和左壳体上。在内齿圈轴200的外侧，大齿圈(第一挡位齿轮50)与第一同步器(第一执行机构S1)一侧的结合齿42焊接为一体，并通过滚针轴承177a以及推力轴承178套在内齿圈轴200上，以绕内齿圈轴200进行自由旋转，滚针轴承177a通过轴肩进行轴向限位，推力轴承178与内齿圈轴200端面262配合进行轴向限位。第一同步器的齿毂41通过内花键与内齿圈轴200的外花键相连进行扭矩的传递，并通过内齿圈轴200端面262以及安装于卡簧槽261中的卡簧70对第一同步器的齿毂41进行轴向限位；小齿圈(第二挡位齿轮60)与第一同步器的结合齿42焊接一体后通过滚针轴承177c安装于内齿圈轴200的轴套部210外侧，以绕内齿圈轴200自由旋转，小齿圈(第二挡位齿轮60)通过压装在内齿圈轴200轴径上的轴套80进行轴向限位，滚针轴承177c通过两侧轴肩进行轴向限位；第二同步器(第二执行机构S2)一侧的结合齿42通过内花键与内齿圈轴200的外花键连接，进行动力的传递，通过轴套80端面262以及安装于卡簧槽261内的卡簧70对第二同步器的结合齿42进行轴向限位。
在内齿圈轴200内部，太阳轮轴110通过两个滚针轴承177b支撑在内齿圈轴200的内孔201中。第一同步器的齿毂41通过内花键与太阳轮轴110的外花键连接进行扭矩传递。太阳轮轴110的端部外花键与发电机401的电机轴的内花键连接，进行动力传递；电机轴通过球轴承179支撑在左壳体320的中间板321上。内齿圈150通过外花键与内齿圈轴200的内花键进行配合，与内齿圈轴200连成一体共同转动，内齿圈150通过内齿圈轴200端面262以及安装于卡簧槽261中的卡簧70进行轴向限位。内齿圈150通过与行星齿轮啮合将整个行星齿轮***支撑在内齿圈轴200上。行星架120通过滚针轴承(第二行星架轴121承173)安装在右壳体上，行星架轴121通过过盈压装在行星架120两侧的连接板122上，行星轮140通过滚针轴承(行星轮轴承171)安装在行星架轴121上，行星轮140分别与内齿圈150和太阳轮130进行啮合。
一些实施例提供的输入轴总成900，整个行星排***通过内齿圈轴200集成了第一执行机构S1和第二执行机构S2，1/2挡齿圈(第二挡位齿轮60)和3/4挡齿圈(第一挡位齿轮50)，以及行星排100，并通过内侧支撑太阳轮轴110与电机相连，同时还集成了行星轮轴承171、执行机构40以及挡位齿轮及相关轴承等的润滑***和电机的冷却***。内齿圈轴200通过内外型面对各个***提供支撑结构，并通过两侧第一支撑轴承175和第二支撑轴承176安装在壳体总成的左右壳体上，从而使得输入轴总成900能高度集成在一起，缩减了其他零件的布置安装位置和接口，使得搭载该输入轴总成900的电驱动***的轴向和径向尺寸得以缩减，降低了该电驱动***的功能体积，缩减成本并增强了其搭载性，使得产品更具竞争力。
基于同样的发明构思，依据本公开的第三方面提供了一种混合动力电驱动总成1000。图5为依据本公开第三方面的混合动力电驱动总成的整体结构图；图6为图5的混合动力电驱动总成拆除端盖后的结构示意图；以及图7为图5的混合动力电驱动总成拆除右壳体后的结构示意图。如图5至图7所述，混合动力电驱动总成1000可以包括壳体总成300和上述本公开第二方面的输入轴总成900，输入轴总成900安装于壳体总成300内部。壳体总成300的结构根据输入轴总成900的结构而设计，满足输入轴总成900的安装需求即可，具体结构本公开不做限制。
该混合动力电驱动总成1000还可以包括与壳体总成300连接的电机总成400，电机总成400可设置为仅包含一个电机，或者两个以上电机。电机总成400的至少一个电机的转子 与行星排100的太阳轮轴110传动连接，实现动力在电机和行星排100之间的传递。在一些实施例中，电机总成400可以包括发电机401和驱动电机402，发电机401的转子与行星排100的太阳轮轴110传动连接，例如，发电机401的转子与行星排100的太阳轮轴110花键连接。
电机总成400可设置为集成及壳体总成300内部，或者电机总成400外置。为了提高混合动力电驱动总成1000的集成度，一些实施例采用电机内置的方案，壳体总成300可以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合围成轴齿安装腔302，行星排100位于轴齿安装腔302中，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。左壳体320和端盖330合围成电机安装腔303，电机总成400位于电机安装腔303中。发电机401的转子410通过两个轴承支撑在左壳体320和端盖330上。
在一些实施例中，发电机401的转子410设有沿轴向贯通的第二中空腔411，进油通道301、第二中空腔411和第一中空腔111依次连通，电机总成400的转子410与行星排100同轴设置，壳体总成300的进油通道301引入的润滑油经第二中空腔411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411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301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。通过将电机总成400的转子410与行星排100内部油路串联，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总成1000的集成度和整车搭载性。
端盖330中设有进油通道301，左壳体320的底部形成油底壳，润滑行星排100后的润滑油落入油底壳中，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301、导油管10、润滑通道160中循环流通。
由于发电机401的转子、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401的转子410的球轴承179，如图3所示。为了进一步提高集成度，靠近发电机401的执行机构(具体为第二执行机构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上直接加工出该执行机构的结合齿。
如图7所示，在一些实施例中，该混合动力电驱动总成1000还可以包括换挡机构总成500、中间轴齿总成600、差速器总成700和控制器总成800；换挡机构总成500、中间轴齿总成600和差速器总成700均位于轴齿安装腔302中；换挡机构总成500和中间轴齿总成600与行星排100配合，实现变速和换挡功能，动力由差速器总成700输出至车轮轴系。控制器总成800安装于壳体总成300外部，用于控制电机总成400和/或换挡机构总成500工作，当然控制器总成800还可控制油泵以及该混合动力电驱动总成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。换挡机构总成500、中间轴齿总成600、控制器总成800的具体内容可参照现有技术的相关公开，此处不展开说明。
基于同样的发明构思，依据本公开的第四方面提供了一种车辆，包括上述本公开第三方面的混合动力电驱动总成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本公开第三方面的混合动力电驱动总成1000，因此至少具有上述本公开第三方面的技术方案所带来的所有有益效果，混合动力电驱动总成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。
基于同样的发明构思，依据本公开的第五方面又提供了一种车辆，包括上述本公开第二方面的输入轴总成900，也就是说，该车辆可以为混合动力车辆或者纯电动车辆或者普通燃油车辆，由发动机和/或电机提供动力，上述本公开第二方面的输入轴总成900能够实现换挡、变速的效果。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。
基于同样的发明构思，依据本公开的第六方面还提供一种车辆，包括上述本公开第一方面的内齿圈轴，也就是说，该车辆可以为混合动力车辆或者纯电动车辆或者普通燃油车辆，由发动机和/或电机提供动力，上述本公开第一方面的内齿圈轴可以应用于该车辆的变速箱中，或者轮毂电机***中。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。
根据本公开的一些实施方式可知，本公开实施例提供的内齿圈轴，整体可套设于行星排外，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。在一些实施例中，该内齿圈轴包括轴套部和罩部，轴套部用于套设于行星排的太阳轮轴或行星架轴上，其上可沿轴向设置若干用于安装执行机构的第一安装位，或者用于设置支撑轴承的装配位、用于设置齿轮的第二安装位，罩部与行星排的内齿圈传动连接，作为行星排的一部分参与行星排的运行，罩部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或用于设置齿轮的第二安装位。由此，通过设置该内齿圈轴，可以同时集成行星排传动功能、执行机构安装、换挡齿轮安装以及必要的轴向限位功能，从而极大的提高电驱动***的集成度，缩减电驱动的功能体积，使得设置有该内齿圈轴的电驱动***具备更灵活的布置和搭载性能。
本公开实施例提供了一个高度集成的行星排输入轴总成，通过内齿圈轴将各***进行布置和支撑，有效的缩减了总成的布置空间，降低成本，使得结构更加紧凑、搭载性更好，使产品竞争力更强。
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。
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。

Claims (28)

  1. 一种内齿圈轴，用于套设于行星排外、且通过支撑轴承安装于壳体总成上，所述内齿圈轴包括：
    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执行机构的第一安装位；以及
    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；
    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齿轮的第二安装位。
  2. 如权利要求1所述的内齿圈轴，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。
  3. 如权利要求2所述的内齿圈轴，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。
  4. 如权利要求3所述的内齿圈轴，其中：所述齿套部与所述内齿圈通过花键连接；所述齿套部的内花键设有卡簧槽。
  5. 如权利要求2所述的内齿圈轴，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。
  6. 如权利要求5所述的内齿圈轴，其中：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。
  7. 如权利要求2所述的内齿圈轴，其中：所述齿套部和所述轴套部均设有所述第二安装位；所述第二安装位设有用于对所述齿轮或所述齿轮的轴承轴向限位的限位结构。
  8. 如权利要求1所述的内齿圈轴，其中：所述第一安装位为键连接结构；所述第一安装位上设有用于对所述执行机构轴向限位的限位结构。
  9. 如权利要求1-8中任一项所述的内齿圈轴，其中：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。
  10. 如权利要求1-8中任一项所述的内齿圈轴，其中：所述轴套部和/或所述罩部上设有至少一个贯通所述轴套部套壁的导油孔；所述轴套部的外型面设有连通于所述导油孔的导油槽。
  11. 一种输入轴总成，包括：用于连接发动机的行星排、至少一个执行机构、至少一个支撑轴承、至少一个齿轮和权利要求1-10中任一项所述的内齿圈轴；所述内齿圈轴套设于所述行星排的太阳轮轴或行星架轴上，且所述内齿圈轴的罩部与所述行星排的内齿圈传动连接；所述至少一个执行机构安装于所述至少一个第一安装位上；所述至少一个支撑轴承设置于所述至少一个装配位上；所述至少一个齿轮设置于所述至少一个第二安装位上。
  12. 如权利要求11所述的输入轴总成，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；所述至少一个齿轮包括第一挡位齿轮和第二挡位齿轮。
  13. 如权利要求12所述的输入轴总成，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。
  14. 如权利要求13所述的输入轴总成，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，所述第二挡位齿轮通过所述轴套轴向限位。
  15. 如权利要求13所述的输入轴总成，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。
  16. 如权利要求11-15中任一项所述的输入轴总成，其中：所述行星排的太阳轮轴或行星架轴设有用于与电机总成传动连接的连接结构。
  17. 如权利要求11-15中任一项所述的输入轴总成，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，所述第一中空腔、所述集油腔和所述润滑通道依次连通。
  18. 如权利要求17所述的输入轴总成，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；
    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。
  19. 如权利要求17所述的输入轴总成，其中：所述太阳轮轴与所述内齿圈轴之间安装有支撑轴承；所述太阳轮轴上设有至少一个连通于所述第一中空腔的第四导油孔，其中一个所述第四导油孔的出口朝向所述支撑轴承。
  20. 如权利要求17所述的输入轴总成，其中：所述输入轴总成还包括导油管，所述导油管贯通安装于所述第一中空腔中，且近行星排端伸入于所述集油腔。
  21. 如权利要求20所述的输入轴总成，其中：所述导油管上设有若干沿所述导油管轴向和/或径向间隔分布的出油孔；所述导油管的远行星排端设有出油口；所述出油口为U型槽和/或圆孔。
  22. 一种混合动力电驱动总成，其中，包括：
    壳体总成；以及
    权利要求11-21中任一项所述的输入轴总成，安装于所述壳体总成内部。
  23. 如权利要求22所述的混合动力电驱动总成，还包括与所述壳体总成连接的电机总成，所述电机总成的转子与所述行星排的太阳轮轴传动连接。
  24. 如权利要求23所述的混合动力电驱动总成，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轴齿安装腔，所述左壳体和所述端盖合围成电机安装腔；所述输入轴总成位于所述轴齿安装腔中，所述电机总成位于所述电机安装腔中。
  25. 如权利要求24所述的混合动力电驱动总成，其中：所述左壳体设有中间板，所述中间板安装有用于支撑所述电机总成的转子的第三支撑轴承；其中一个所述执行机构的结合齿与所述中间板固定连接。
  26. 如权利要求23所述的混合动力电驱动总成，其中：所述电机总成包括发电机和驱动电机，所述发电机的转子与所述行星排的太阳轮轴传动连接。
  27. 如权利要求26所述的混合动力电驱动总成，其中：所述发电机的转子内部设置有第二中空腔，所述第二中空腔连通于所述行星排的太阳轮轴的第一中空腔。
  28. 一种车辆，包括权利要求22-27中任一项所述的混合动力电驱动总成；或者，包括权利要求11-21中任一项所述的输入轴总成；或者，包括权利要求1-10中任一项所述的内齿圈轴。
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CN115750752A (zh) * 2022-10-24 2023-03-07 东风汽车集团股份有限公司 一种混合动力电驱动***以及混合动力车辆
CN115638239A (zh) * 2022-10-24 2023-01-24 东风汽车集团股份有限公司 一种行星排润滑结构、混合动力电驱动总成及车辆
CN115875425B (zh) * 2022-10-24 2024-04-16 东风汽车集团股份有限公司 一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆
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Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104728402A (zh) * 2015-02-11 2015-06-24 徐新生 一种可用于电池式电动工具的变速齿轮箱
CN206159454U (zh) * 2016-10-27 2017-05-10 陕西工业职业技术学院 新型多档齿轮箱行星排固定及润滑结构
CN208515357U (zh) * 2018-04-28 2019-02-19 长城汽车股份有限公司 用于驱动桥的动力输入轴安装总成、电驱动桥以及车辆
DE102019007683A1 (de) * 2019-11-06 2021-05-06 Daimler Ag Planetengetriebe für einen Antriebsstrang eines Kraftfahrzeugs
CN215487547U (zh) * 2021-05-19 2022-01-11 一汽解放汽车有限公司 汽车及其变速器后副箱行星轮结构
CN115875425A (zh) * 2022-10-24 2023-03-31 东风汽车集团股份有限公司 一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104728402A (zh) * 2015-02-11 2015-06-24 徐新生 一种可用于电池式电动工具的变速齿轮箱
CN206159454U (zh) * 2016-10-27 2017-05-10 陕西工业职业技术学院 新型多档齿轮箱行星排固定及润滑结构
CN208515357U (zh) * 2018-04-28 2019-02-19 长城汽车股份有限公司 用于驱动桥的动力输入轴安装总成、电驱动桥以及车辆
DE102019007683A1 (de) * 2019-11-06 2021-05-06 Daimler Ag Planetengetriebe für einen Antriebsstrang eines Kraftfahrzeugs
CN215487547U (zh) * 2021-05-19 2022-01-11 一汽解放汽车有限公司 汽车及其变速器后副箱行星轮结构
CN115875425A (zh) * 2022-10-24 2023-03-31 东风汽车集团股份有限公司 一种内齿圈轴、输入轴总成、混合动力电驱动总成及车辆

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