CN114352691A - Planetary gear type transmission, automobile power system and automobile - Google Patents

Planetary gear type transmission, automobile power system and automobile Download PDF

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Publication number
CN114352691A
CN114352691A CN202210169913.0A CN202210169913A CN114352691A CN 114352691 A CN114352691 A CN 114352691A CN 202210169913 A CN202210169913 A CN 202210169913A CN 114352691 A CN114352691 A CN 114352691A
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CN
China
Prior art keywords
input
gear
output
brake
main shaft
Prior art date
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Pending
Application number
CN202210169913.0A
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Chinese (zh)
Inventor
傅灵玲
赵玉婷
孙峰
施悠笛
谭艳军
林霄喆
王瑞平
肖逸阁
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wuxi Xingqu Technology Co ltd
Zhejiang Geely Holding Group Co Ltd
Original Assignee
Wuxi Xingqu Technology Co ltd
Zhejiang Geely Holding Group Co Ltd
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Application filed by Wuxi Xingqu Technology Co ltd, Zhejiang Geely Holding Group Co Ltd filed Critical Wuxi Xingqu Technology Co ltd
Priority to CN202210169913.0A priority Critical patent/CN114352691A/en
Publication of CN114352691A publication Critical patent/CN114352691A/en
Pending legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/70—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion in which the central axis of the gearing lies inside the periphery of an orbital gear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft
    • F16H37/082—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft and additional planetary reduction gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion
    • F16H57/10—Braking arrangements
    • 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
    • F16H2057/02086—Measures for reducing size of gearbox, e.g. for creating a more compact transmission casing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/0021—Transmissions for multiple ratios specially adapted for electric vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/2002—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears
    • F16H2200/2007—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with two sets of orbital gears
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/20—Transmissions using gears with orbital motion
    • F16H2200/203—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes
    • F16H2200/2035—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with two engaging means

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Transportation (AREA)
  • Retarders (AREA)

Abstract

The invention discloses a planetary gear type transmission, an automobile power system and an automobile, wherein the planetary gear type transmission comprises a transmission shell, an input main shaft, an output main shaft, a secondary gear shifting brake assembly and a double-planet-row assembly, wherein the input main shaft and the output main shaft are arranged in the transmission shell; the double-planet-row component comprises a sun gear, a double-planet-wheel component and a transmission inner gear ring; two keep off the installation intracavity of gear shift brake subassembly including locating the derailleur casing, and be inside brake subassembly and the outside brake subassembly of inside and outside setting, outside brake subassembly's outside combines braking part fixed connection in derailleur casing, two adjacent combination braking parts of two brake subassemblies are connected with one of them of double planetary wheel subassembly and transmission ring gear, output main shaft is connected with another, the inboard combination braking part that inboard combines brake subassembly is connected with sun gear and input main shaft, combine the braking through the alternative of inside brake subassembly and outside brake subassembly, realize two fender variable speeds of derailleur, dynamic property has been promoted.

Description

Planetary gear type transmission, automobile power system and automobile
Technical Field
The invention relates to the technical field of automobile transmission systems, in particular to a planetary gear type transmission, an automobile power system and an automobile.
Background
At present, with the development of new energy automobile industry, automobiles become development trends, however, pure electric vehicles on the current market all adopt single-gear speed reducers, and the single-gear speed reducers generally have the problems of fixed speed ratio, high requirement on driving motors, insufficient dynamic property and poor economical efficiency.
Disclosure of Invention
The invention mainly aims to provide a planetary gear type transmission, an automobile power system and an automobile, and aims to solve the problem of insufficient power performance caused by fixed speed ratio of a single-gear speed reducer in the existing pure electric vehicle.
To achieve the above object, the present invention provides a planetary gear type transmission comprising:
a transmission case having a mounting cavity formed therein;
the input main shaft and the output main shaft are arranged on the transmission shell;
the second gear shifting brake assembly comprises an inner side brake assembly and an outer side brake assembly which are arranged in the installation cavity and are arranged inside and outside, the inner side brake assembly and the outer side brake assembly are alternately combined for braking, the inner side brake assembly and the outer side brake assembly respectively comprise an inner side combined brake part and an outer side combined brake part which are arranged inside and outside, the outer side combined brake part of the inner side brake assembly is fixedly connected with the inner side combined brake part of the outer side brake assembly, and the outer side combined brake part of the outer side brake assembly is fixedly connected with the transmission shell; and the number of the first and second groups,
the double-planet-row assembly comprises a sun gear, a double-planet-wheel assembly and a transmission inner gear ring, the double-planet-wheel assembly comprises a planet carrier, an inner planet wheel structure and an outer planet wheel structure, the inner planet wheel structure and the outer planet wheel structure are arranged on the planet carrier and are meshed with each other, the outer planet wheel structure is meshed with the transmission inner gear ring, the inner planet wheel structure is meshed with the sun gear, and the sun gear is connected with an inner side combination braking part of the inner side combination braking assembly and the input main shaft;
one of the planet carrier and the transmission ring gear is connected to the outer side combination braking part of the inner side braking component and the inner side combination braking part of the outer side braking component, and the other one of the planet carrier and the transmission ring gear is connected with the output main shaft.
Optionally, in the axial direction of the sun gear, the input end of the output main shaft and the output end of the output main shaft are disposed on the same side of the double-planet-row assembly or on both sides of the double-planet-row assembly.
Optionally, hub and fixed friction disc structure in the inboard braking portion of combining includes the braking, outside braking portion of combining includes hub and activity friction disc structure outside the braking, in the braking the hub with the hub is relative setting outside the braking, just in the braking the hub with form the braking chamber between the hub outside the braking, fixed friction disc structure is located braking intracavity and fixed connection to hub in the braking, activity friction disc structure is relative fixed friction disc structure is located the braking chamber, and follows the axial activity of the hub outside the braking is located on the hub outside the braking on the activity stroke of activity friction disc structure, activity friction disc structure can with correspond fixed friction disc structure butt each other or break away from, the outer hub fixed connection of the braking of inboard braking subassembly is in the hub of outside braking subassembly.
The invention further provides an automobile power system which comprises the planetary gear type transmission.
Optionally, the vehicle power system further comprises:
the driving motor comprises a motor main shaft, and the motor main shaft is connected with the input main shaft in a driving mode; and the number of the first and second groups,
a differential having an input end drivingly connected to the output spindle.
Optionally, the automotive power system further comprises an input speed reduction assembly, and the input speed reduction assembly is in driving connection with the driving motor and the input spindle.
Optionally, the input reduction assembly comprises an input primary input gear and an input primary output gear that are meshed with each other, the motor spindle is drivingly connected to the input primary input gear, and the input primary output gear is connected to the input spindle; alternatively, the first and second electrodes may be,
the input speed reduction subassembly includes intermeshing's input one-level input gear and input one-level output gear and intermeshing's input second grade input gear and input second grade output gear, motor spindle drive is connected to input one-level input gear, input one-level output gear with input second grade input gear coaxial arrangement and synchronous rotation, input second grade output gear is connected to the input main shaft.
Optionally, the automotive power system further comprises an output speed reduction assembly, and the output speed reduction assembly is in driving connection with the differential and the output main shaft.
Optionally, the output reduction assembly comprises an output primary input gear and an output primary output gear which are meshed with each other, the output spindle is drivingly connected to the output primary input gear, and the output primary output gear is connected to the input end of the differential; alternatively, the first and second electrodes may be,
the output speed reduction subassembly includes intermeshing's output one-level input gear and output one-level output gear and intermeshing's output second grade input gear and output second grade output gear, output main shaft drive is connected to output one-level input gear, output one-level output gear with output second grade input gear is coaxial to be set up and synchronous rotation, output second grade output gear is connected to differential mechanism's input end portion.
The invention further provides an automobile which comprises the automobile power system, and the power system comprises the planetary gear type transmission.
In the technical scheme provided by the invention, when the inner side brake component is combined for braking and the outer side brake component is not combined for braking, the transmission inner gear ring, the double planetary wheel component and the sun gear are relatively fixed, namely the input main shaft and the output main shaft are relatively fixed and have the same rotating speed; when the inner brake component is not braked in a combining mode and the outer brake component is braked in a combining mode, the outer brake component and the outer combining brake part of the inner brake component are fixed relative to the transmission shell, namely one of the planet carrier and the transmission inner gear ring is fixed relative to the transmission shell, the rotating speed is input into the double-planet-row component through the input gear and then output to the output main shaft in a variable speed mode, therefore, through the alternate combined braking of the inner brake component and the outer brake component, the two-gear variable speed of the planetary gear type transmission is achieved, different running conditions of a vehicle are adapted, the driving device is guaranteed to run in a high-efficiency region, and meanwhile, the high dynamic performance is provided.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the embodiments or the prior art will be briefly described below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to the structures shown in the drawings without creative efforts.
FIG. 1 is a schematic illustration of a first embodiment of an automotive powertrain according to the present invention;
FIG. 2 is a schematic illustration of a second embodiment of an automotive powertrain according to the present invention;
FIG. 3 is a schematic illustration of a third embodiment of an automotive powertrain according to the present invention;
FIG. 4 is a schematic illustration of a fourth embodiment of an automotive powertrain according to the present invention;
fig. 5 is a schematic structural diagram of a fifth embodiment of an automotive power system provided by the invention.
The reference numbers illustrate:
reference numerals Name (R) Reference numerals Name (R)
100 Automobile power system 15 Output spindle
1 Planetary gear type speed changer 2 Driving motor
11 Transmission housing 21 Motor spindle
12 Two keep off braking components that shifts 3 Differential gear
121 Inboard brake assembly 31 Output half shaft
122 Outboard brake assembly 4 Input speed reduction assembly
123 Inner side combined brake part 41 Input end primary input gear
124 Outside combined brake part 42 Input end primary output gear
13 Double-planet row assembly 43 Input end two-stage input gear
131 Sun wheel 44 Input end two-stage output gear
132 Double planetary wheel assembly 5 Output speed reduction assembly
1321 Inner planet wheel structure 51 Output end first-stage input gear
1322 Outer planet wheel structure 52 Output end primary output gear
1323 Planet carrier 53 Output end two-stage input gear
133 Transmission ring gear 54 Output end two-stage output gear
14 Input spindle
The implementation, functional features and advantages of the objects of the present invention will be further explained with reference to the accompanying drawings.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
It should be noted that, if directional indication is involved in the embodiment of the present invention, the directional indication is only used for explaining the relative positional relationship, the motion situation, and the like between the components in a certain posture, and if the certain posture is changed, the directional indication is changed accordingly.
In addition, if there is a description of "first", "second", etc. in an embodiment of the present invention, the description of "first", "second", etc. is for descriptive purposes only and is not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In addition, technical solutions between various embodiments may be combined with each other, but must be realized by a person skilled in the art, and when the technical solutions are contradictory or cannot be realized, such a combination should not be considered to exist, and is not within the protection scope of the present invention.
At present, with the development of new energy automobile industry, automobiles become development trends, however, pure electric vehicles on the current market all adopt single-gear speed reducers, and the single-gear speed reducers generally have the problems of fixed speed ratio, high requirement on driving motors, insufficient dynamic property and poor economical efficiency.
In view of this, the present invention provides an automobile power system, which includes a planetary gear type transmission, and aims to solve the problem of insufficient dynamic performance caused by the fixed speed ratio of a single-gear speed reducer in the existing pure electric vehicle, wherein fig. 1 to 5 are schematic structural diagrams of five embodiments of the automobile power system provided by the present invention.
Referring to fig. 1 to 5, the planetary gear type transmission 1 includes a transmission housing 11, an input main shaft 14, an output main shaft 15, a secondary gear shift brake assembly 12, and a double planetary gear set assembly 13, wherein a mounting cavity is formed inside the transmission housing 11; the input main shaft 14 and the output main shaft 15 are arranged on the transmission housing 11; the second gear shifting brake assembly 12 comprises an inner brake assembly 121 and an outer brake assembly 122 which are arranged inside and outside and are arranged in the mounting cavity, the inner brake assembly 121 and the outer brake assembly 122 are alternately combined for braking, both the inner brake assembly 121 and the outer brake assembly 122 comprise an inner combining brake part 123 and an outer combining brake part 124 which are arranged inside and outside, the outer combining brake part 124 of the inner brake assembly 121 is fixedly connected with the inner combining brake part 123 of the outer brake assembly 122, and the outer combining brake part 124 of the outer brake assembly 122 is fixedly connected to the transmission housing 11; the double-planet-row assembly 13 comprises a sun gear 131, a double-planet-wheel assembly 132 and a transmission ring gear 133, the double-planet-wheel assembly 132 comprises a planet carrier 1323, an inner planet gear structure 1321 and an outer planet gear structure 1322 which are arranged on the planet carrier 1323 and are meshed with each other, the outer planet gear structure 1322 is meshed with the transmission ring gear 133, the inner planet gear structure 1321 is meshed with the sun gear 131, and the sun gear 131 is connected with an inner combined brake part 123 of the inner combined brake assembly and the input spindle 14; one of the planet carrier 1323 and the transmission ring gear 133 is connected to the outer combination brake 124 of the inner brake assembly 121 and the inner combination brake 123 of the outer brake assembly 122, and the other is connected to the output shaft 15.
In the technical scheme provided by the present invention, when the inner brake assembly 121 is braked in a combined manner and the outer brake assembly 122 is braked in an unbound manner, the transmission ring gear 133, the double planetary gear assembly 132 and the sun gear 131 are relatively fixed, that is, the input spindle 14 and the output spindle 15 are relatively fixed and have the same rotation speed; when the inner brake assembly 121 is not braked and the outer brake assembly 122 is braked in a combined mode, the outer brake assembly 122 and the outer combined brake part 124 of the inner brake assembly 121 are fixed relative to the transmission housing 11, namely, one of the planet carrier 1323 and the transmission ring gear 133 is fixed relative to the transmission housing 11, power is input to the double-row planetary gear assembly 13 through the input main shaft 14 and then is output to the output main shaft 15 in a variable speed mode, so that two-gear variable speed of the planetary gear type transmission 1 is realized through alternate combined braking of the inner brake assembly 121 and the outer brake assembly 122, different running conditions of a vehicle are met, a driving device is guaranteed to run in a high-efficiency zone, and meanwhile, high dynamic performance is provided.
It will be appreciated that the inner planetary wheel arrangement 1321 comprises a plurality of inner planetary wheels and the outer planetary wheel arrangement 1322 comprises a plurality of outer planetary wheels, the inner planetary wheel arrangement 1321 being intermeshed with the outer planetary wheel arrangement 1322 in such a way that a plurality of said inner planetary wheels are respectively intermeshed with a plurality of said outer planetary wheels.
Referring to fig. 5, specifically, along the axial direction of the sun gear 131, the input end of the input main shaft 14 and the output end of the output main shaft 15 are disposed on the same side of the double planetary row assembly 13, it can be understood that the output main shaft 15 is a hollow shaft and is configured to be coaxial with the input main shaft 14, and at this time, the output end of the output main shaft 15 is disposed between the input end of the input main shaft 14 and the double planetary row assembly 13, and thus, the axial size of the planetary gear type transmission 1 can be shortened.
Referring to fig. 4, specifically, when the input end of the input main shaft 14 and the output end of the output main shaft 15 are respectively disposed at two sides of the double planetary row assembly 13 along the axial direction of the sun gear 131, the processing difficulty of the input main shaft 14 and the output main shaft 15 is reduced.
It should be noted that the two embodiments can be alternatively arranged according to different applications.
The setting forms of the inner side brake assembly 121 and the outer side brake assembly 122 are various, the braking can be realized in a way of mutually clamping and matching a brake clamping claw and a brake chuck, and the braking can also be realized in a way of mutually rubbing friction plates, in the embodiment, the inner side combined brake part 123 comprises an inner brake hub and a fixed friction plate structure, the outer side combined brake part 124 comprises an outer brake hub and a movable friction plate structure, the inner brake hub and the outer brake hub are oppositely arranged, a brake cavity is formed between the inner brake hub and the outer brake hub, the fixed friction plate structure is arranged in the brake cavity and fixedly connected to the inner brake hub, the movable friction plate structure is arranged in the brake cavity, and the fixed friction plate structure is arranged on the outer brake hub along the axial direction of the outer brake hub on the movable stroke of the movable friction plate structure, the movable friction plate structure can be mutually abutted or separated with the corresponding fixed friction plate structure, and the braking outer hub of the inner side braking assembly 121 is fixedly connected to the braking inner hub of the outer side braking assembly 122. The inner brake hub and the outer brake hub can be relatively fixed by driving the movable friction plate structure to be in frictional contact with the fixed friction plate structure, and it should be noted that there are various ways of driving the movable friction plate structure, which may be hydraulic drive or electromagnetic drive, and this embodiment is not described herein again; it should be understood that the rotational axial directions of the input spindle 14, the output spindle 15, the inner and outer brake hubs of the inboard brake assembly 121 and the inner and outer brake hubs of the outboard brake assembly 122 are the same.
Further, the activity friction disc structure includes follows the axial of the outer hub of braking is a plurality of activity friction discs of interval setting ground, fixed friction disc structure includes follows the axial of hub is a plurality of fixed friction discs of interval setting ground in the braking, and is a plurality of the activity friction disc is with a plurality of fixed friction disc one-to-one sets up, and is a plurality of when the drive the activity friction disc is when moving simultaneously, and is a plurality of the activity friction disc can with relative fixed friction disc butt each other or break away from, so set up, can improve the reliability and the stability of friction braking.
Referring to fig. 1 to fig. 5, in the present embodiment, the automotive power system 100 further includes a driving motor 2 and a differential 3, the driving motor 2 includes a motor spindle 21, and the motor spindle 21 is drivingly connected to the input spindle 14; the input end of the differential 3 is drivingly connected to the output shaft 15. The motor spindle 21 is connected to the input spindle 14 in a driving manner, which may be directly connected through a coupling or connected through a speed reduction assembly, and this embodiment is not limited thereto; the input end of the differential 3 is drivingly connected to the output main shaft 15, and the driving connection mode may be direct connection through a coupling or reduction connection through a reduction assembly, which is not limited in this embodiment, it is understood that the differential 3 has an input terminal for rotating input and two output half shafts, the input end is the input terminal for rotating the differential 3, the differential 3 has a disengaging mechanism and a locking mechanism to adjust the output rotation speed of the left and right output half shafts, the differential 3 may be a limited slip differential or a mechanical differential lock, which is not limited in this embodiment of the present invention.
Further, referring to fig. 3, in this embodiment, the automobile power system 100 further includes an input speed reduction assembly 4, and the input speed reduction assembly 4 is connected to the driving motor 2 and the input spindle 14 in a driving manner, so as to realize speed reduction and torque increase.
Specifically, in this embodiment, the input speed reduction assembly 4 includes an input end first-level input gear 41 and an input end first-level output gear 42 which are engaged with each other, the motor spindle 21 is drivingly connected to the input end first-level input gear 41, the input end first-level output gear 42 is connected to the input spindle 14, and through the meshing transmission of the input end first-level input gear 41 and the input end first-level output gear 42, the one-level speed reduction transmission of the motor spindle 21 and the input spindle 14 can be realized, so as to increase the torque.
In particular, in another embodiment, the input reduction assembly 4 comprises an input primary input gear 41 and an input primary output gear 42, which mesh with each other, and an input secondary input gear 43 and an input secondary output gear 44, which mesh with each other, the motor main shaft 21 is connected to the input end primary input gear 41 in a driving manner, the input end primary output gear 42 and the input end secondary input gear 43 are coaxially arranged and synchronously rotate, the input end secondary output gear 44 is connected to the input main shaft 14, through the meshing transmission of the input end primary input gear 41 and the input end primary output gear 42, and the meshed transmission of the input secondary input gear 43 and the input secondary output gear 44, two-stage reduction transmission of the motor main shaft 21 and the input main shaft 14 can be realized, so that the torque is increased.
The two embodiments can be alternatively arranged according to different working conditions.
Further, referring to fig. 5, in the axial direction of the sun gear 131, the input end of the input main shaft 14 and the output end of the output main shaft 15 are respectively disposed at two sides of the double planetary row assembly 13, the output end of the output main shaft 15 is coaxially connected to the input end of the differential mechanism 3, the input main shaft 14 and the output main shaft 15 are disposed in a hollow manner, the output half shaft 31 of the differential mechanism 3 facing one side of the double planetary row assembly 13 passes through the input main shaft 14, and thus, the output end of the output main shaft 15 is coaxially connected to the input end of the differential mechanism 3, so that the internal structure of the automotive power system 100 is more compact, and the occupied space is further saved.
Referring to fig. 4, in this embodiment, the automotive power system 100 further includes an output speed reduction assembly 5, and the output speed reduction assembly 5 is drivingly connected to the output main shaft 15 and the input end of the differential 3, so as to reduce speed and increase torque.
Specifically, in this embodiment, the output speed reduction assembly 5 includes an output end first-level input gear 51 and an output end first-level output gear 52 which are engaged with each other, the output main shaft 15 is drivingly connected to the output end first-level input gear 51, the output end first-level output gear 52 is connected to the input end of the differential mechanism 3, and through the meshing transmission of the output end first-level input gear 51 and the output end first-level output gear 52, the one-level speed reduction transmission of the motor main shaft 21 and the input main shaft 14 can be realized, so as to increase the torque.
In another embodiment, the output reduction assembly 5 includes an output primary input gear 51 and an output primary output gear 52 that intermesh and an output secondary input gear 53 and an output secondary output gear 54 that intermesh, the motor main shaft 21 is connected to the output end primary input gear 51 in a driving manner, the output end primary output gear 52 and the output end secondary input gear 53 are coaxially arranged and synchronously rotate, the output end secondary output gear 54 is connected to the input main shaft 14, through the meshing transmission of the output end primary input gear 51 and the output end primary output gear 52, and the meshed transmission of the output secondary input gear 53 and the output secondary output gear 54, a two-stage reduction of the output shaft 15 with the input end of the differential 3 is achieved, thereby increasing the torque.
The two embodiments can be alternatively arranged according to different working conditions.
Further, referring to fig. 1, fig. 2 and fig. 5, the automotive power system 100 includes an input speed reduction assembly 4 and an output speed reduction assembly 5, where the input speed reduction assembly 4 includes an input primary input gear 41 and an input primary output gear 42 that are engaged with each other, the motor spindle 21 is drivingly connected to the input primary input gear 41, and the input primary output gear 42 is connected to the input spindle 14; the output speed reducing assembly 5 comprises an output end first-level input gear 51 and an output end first-level output gear 52 which are meshed with each other, the output main shaft 15 is in driving connection with the output end first-level input gear 51, and the output end first-level output gear 52 is connected to the input end of the differential mechanism 3. With such an arrangement, the two primary speed reduction assemblies are respectively arranged on the two sides of the double-planet-row assembly 13, so that the automobile power system 100 can be more compact in structure, and an excessive useless space cannot be left on the automobile body.
In addition, the invention further provides an automobile, which includes the automobile power system 100 in the above scheme, and it should be noted that the structure of the automobile power system 100 in the automobile may refer to the embodiment of the automobile power system 100, which is not described herein again; since the automobile power system 100 is used in the automobile provided by the present invention, the embodiment of the automobile provided by the present invention includes all technical solutions of all embodiments of the automobile power system 100, and the achieved technical effects are also completely the same, and are not described herein again.
The above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention, and all modifications and equivalents made by the contents of the present specification and drawings, or directly/indirectly applied to other related technical fields, are included in the scope of the present invention.

Claims (10)

1. A planetary gear transmission, comprising:
a transmission case having a mounting cavity formed therein;
the input main shaft and the output main shaft are arranged on the transmission shell;
the second gear shifting brake assembly comprises an inner side brake assembly and an outer side brake assembly which are arranged in the installation cavity and are arranged inside and outside, the inner side brake assembly and the outer side brake assembly are alternately combined for braking, the inner side brake assembly and the outer side brake assembly respectively comprise an inner side combined brake part and an outer side combined brake part which are arranged inside and outside, the outer side combined brake part of the inner side brake assembly is fixedly connected with the inner side combined brake part of the outer side brake assembly, and the outer side combined brake part of the outer side brake assembly is fixedly connected with the transmission shell; and the number of the first and second groups,
the double-planet-row assembly comprises a sun gear, a double-planet-wheel assembly and a transmission inner gear ring, the double-planet-wheel assembly comprises a planet carrier, an inner planet wheel structure and an outer planet wheel structure, the inner planet wheel structure and the outer planet wheel structure are arranged on the planet carrier and are meshed with each other, the outer planet wheel structure is meshed with the transmission inner gear ring, the inner planet wheel structure is meshed with the sun gear, and the sun gear is connected with an inner side combination braking part of the inner side combination braking assembly and the input main shaft;
one of the planet carrier and the transmission ring gear is connected to the outer side combination braking part of the inner side braking component and the inner side combination braking part of the outer side braking component, and the other one of the planet carrier and the transmission ring gear is connected with the output main shaft.
2. The planetary gear transmission according to claim 1, wherein the input end of the input main shaft and the output end of the output main shaft are provided on the same side of the double planetary row assembly or on both sides of the double planetary row assembly in the axial direction of the sun gear.
3. The planetary gear transmission of claim 1, wherein said inboard coupling brake portion includes a brake inner hub and a fixed friction plate arrangement, the outer combined brake part comprises a brake outer hub and a movable friction plate structure, the brake inner hub and the brake outer hub are arranged oppositely, a brake cavity is formed between the brake inner hub and the brake outer hub, the fixed friction plate structure is arranged in the brake cavity and is fixedly connected to the brake inner hub, the movable friction plate structure is arranged in the brake cavity relative to the fixed friction plate structure and is movably arranged on the brake outer hub along the axial direction of the brake outer hub, on the movable stroke of the movable friction plate structure, the movable friction plate structure can be mutually abutted or separated with the corresponding fixed friction plate structure, the outer brake hub of the inboard brake assembly is fixedly connected to the inner brake hub of the outboard brake assembly.
4. A vehicle powertrain comprising a planetary gear transmission according to any one of claims 1 to 3.
5. The vehicle powertrain system of claim 4, further comprising:
the driving motor comprises a motor main shaft, and the motor main shaft is connected with the input main shaft in a driving mode; and the number of the first and second groups,
a differential having an input end drivingly connected to the output spindle.
6. The vehicle powertrain of claim 5, further comprising an input reduction assembly drivingly connecting the drive motor and the input spindle.
7. The automotive powertrain of claim 6, wherein the input reduction assembly includes an input primary input gear and an input primary output gear in meshing engagement with one another, the motor shaft being drivingly connected to the input primary input gear, the input primary output gear being connected to the input shaft; alternatively, the first and second electrodes may be,
the input speed reduction subassembly includes intermeshing's input one-level input gear and input one-level output gear and intermeshing's input second grade input gear and input second grade output gear, motor spindle drive is connected to input one-level input gear, input one-level output gear with input second grade input gear coaxial arrangement and synchronous rotation, input second grade output gear is connected to the input main shaft.
8. The automotive powertrain of claim 5, further comprising an output reduction assembly drivingly connecting the differential and the output spindle.
9. The automotive powertrain of claim 8, wherein the output reduction assembly includes an output primary input gear and an output primary output gear in meshing engagement with one another, the output spindle being drivingly connected to the output primary input gear, the output primary output gear being connected to the input end of the differential; alternatively, the first and second electrodes may be,
the output speed reduction subassembly includes intermeshing's output one-level input gear and output one-level output gear and intermeshing's output second grade input gear and output second grade output gear, output main shaft drive is connected to output one-level input gear, output one-level output gear with output second grade input gear is coaxial to be set up and synchronous rotation, output second grade output gear is connected to differential mechanism's input end portion.
10. A vehicle comprising a vehicle powertrain according to any one of claims 4 to 9.
CN202210169913.0A 2022-02-23 2022-02-23 Planetary gear type transmission, automobile power system and automobile Pending CN114352691A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN202210169913.0A CN114352691A (en) 2022-02-23 2022-02-23 Planetary gear type transmission, automobile power system and automobile

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202210169913.0A CN114352691A (en) 2022-02-23 2022-02-23 Planetary gear type transmission, automobile power system and automobile

Publications (1)

Publication Number Publication Date
CN114352691A true CN114352691A (en) 2022-04-15

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
CN202210169913.0A Pending CN114352691A (en) 2022-02-23 2022-02-23 Planetary gear type transmission, automobile power system and automobile

Country Status (1)

Country Link
CN (1) CN114352691A (en)

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