WO2020001589A1 - Transmission, power drive system and vehicle - Google Patents

Transmission, power drive system and vehicle Download PDF

Info

Publication number
WO2020001589A1
WO2020001589A1 PCT/CN2019/093561 CN2019093561W WO2020001589A1 WO 2020001589 A1 WO2020001589 A1 WO 2020001589A1 CN 2019093561 W CN2019093561 W CN 2019093561W WO 2020001589 A1 WO2020001589 A1 WO 2020001589A1
Authority
WO
WIPO (PCT)
Prior art keywords
transmission
gear
synchronizer
planetary gear
planet carrier
Prior art date
Application number
PCT/CN2019/093561
Other languages
French (fr)
Chinese (zh)
Inventor
杨鹏
陈记龙
付才林
Original Assignee
比亚迪股份有限公司
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 比亚迪股份有限公司 filed Critical 比亚迪股份有限公司
Publication of WO2020001589A1 publication Critical patent/WO2020001589A1/en

Links

Images

Classifications

    • 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
    • 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
    • F16H57/02—Gearboxes; Mounting gearing therein
    • F16H2057/02039—Gearboxes for particular applications
    • F16H2057/02043—Gearboxes for particular applications for vehicle transmissions
    • 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
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0043—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising four forward speeds
    • 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

Definitions

  • the present application belongs to the technical field of vehicle manufacturing, and in particular, relates to a transmission, a power drive system, and a vehicle.
  • Hybrid-drive vehicles, electric vehicles, and extended-range electric vehicles are the future development direction of vehicles and the main form of new energy vehicles.
  • the power transmission system has a complicated structure, a complicated working mode, and a complicated control strategy.
  • the energy conversion efficiency needs to be improved.
  • the engine ’s kinetic energy and battery power cannot be fully utilized.
  • an object of the present application is to propose a transmission with high efficiency, simple structure, and smooth shifting.
  • the transmission according to the present application includes: a first planetary gear mechanism including a first sun gear, a first planet gear, a first planet carrier, and a first ring gear; and a second planetary gear mechanism, the The second planetary gear mechanism includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear, and the second ring gear is connected to an output end of the transmission; an input shaft, and the input shaft and The first sun gear is connected; an intermediate shaft, the first planet carrier is connected to the intermediate shaft, the intermediate shaft is connected to the second sun gear; a first synchronizer, and the first synchronizer connects the A first ring gear is fixed to the transmission housing or the first ring gear is connected to the first sun gear; a second synchronizer, the second synchronizer connects the second planet carrier with the transmission The casing is fixed or connects the second planet carrier with the second sun gear.
  • the power drive system includes a drive motor and a transmission according to the present application, and the drive motor is dynamically coupled to the input shaft.
  • the power driving system according to the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission according to the embodiment of the present application, and the structure of the power driving system is simple.
  • the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet vehicle requirements for transmission durability, power transmission efficiency, size, and cost.
  • a vehicle according to the present application includes a power drive system described in the present application.
  • the vehicle according to the present application is provided with the above-mentioned power drive system, so that the vehicle has the advantages of smooth shifting, rapid shifting and high torque transmission efficiency, and can make the vehicle's output torque range large, load stable, and can cope with complicated road conditions. It has the advantage of saving energy.
  • the vehicle according to the present application may be an electric vehicle, a hybrid vehicle, or the like.
  • FIG. 1 is a schematic structural diagram of a transmission according to an embodiment of the present application.
  • Input shaft 4 intermediate shaft 5; output shaft 6;
  • a transmission 100 according to an embodiment of the present application is described below with reference to FIG. 1.
  • a transmission 100 includes a first planetary gear mechanism, a second planetary gear mechanism, an input shaft 4, an intermediate shaft 5, a first synchronizer 7, and a second synchronizer 8.
  • the torque of the vehicle can be input to the transmission 100 through the input shaft 4, and the torque in the transmission 100 can be finally output by the output of the transmission through the first planetary gear mechanism and the second planetary gear mechanism.
  • the synchronizer is used to connect various components in the transmission 100 to realize gear shifting.
  • the first planetary gear mechanism may include a plurality of first planetary gears 14, and the plurality of first planetary gears 14 are connected to the first planet carrier 13.
  • the second planetary gear mechanism may include a plurality of second planetary gears 24 and a plurality of second planetary gears.
  • the wheel 24 is connected to the second planet carrier 23.
  • the first planetary gear mechanism includes a first sun gear 11, a first planet gear 14, a first planet carrier 13, and a first ring gear 12, so that when torque is transmitted in the first planetary gear mechanism, the torque can be transmitted by the first sun gear 11 and / or the first ring gear 12 are input and output to the intermediate shaft 5 by the first planet carrier 13.
  • the second planetary gear mechanism includes a second sun gear 21, a second planet gear 24, a second planet carrier 23, and a second ring gear 22.
  • the output end of the transmission 100 includes an output shaft 6.
  • the second ring gear 22 and the output of the transmission 100 The shaft 6 is connected, so that the torque can be input to the second planetary gear structure by the second sun gear 21 and / or the second planet carrier 23 and output to the output shaft 6 by the second ring gear 22.
  • the input shaft 4 is connected to the first sun gear 11, the first planet carrier 13 is connected to the intermediate shaft 5, and the intermediate shaft 5 is connected to the second sun gear 21.
  • Torque can be transmitted from the first planetary gear mechanism by the first planet carrier 13. To the intermediate shaft 5 and transmitted to the second sun gear 21 of the second planetary gear mechanism through the intermediate shaft 5.
  • the output end of the transmission 100 may further include an output gear, the output gear is idler and the intermediate shaft 5, the torque may be transmitted out of the transmission 100 through the output gear, and the setting of the output gear may change the transmission direction of the output torque, Therefore, the size of the transmission 100 in the axial direction of the input shaft 4 can be reduced, so that the transmission 100 can be more conveniently arranged on the vehicle.
  • the first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100 or connects the first ring gear 12 to the first sun gear 11:
  • the torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and output by the first planet carrier 13;
  • the first synchronizer 7 connects the first ring gear 12 with the first The sun gear 11 is connected, and the torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and the first ring gear 12 and output by the first planet carrier 13.
  • This structure enables the first planetary gear mechanism to output Two speed ratios.
  • the second synchronizer 8 fixes the second planet carrier 23 to the housing 10 of the transmission 100 or connects the second planet carrier 23 to the second sun gear 21: when the second synchronizer 8 connects the second planet carrier 23 to the transmission 100
  • the torque can be input to the second planetary gear mechanism by the intermediate shaft 5 through the second sun gear 21 and output by the second ring gear 22; when the second synchronizer 8 will connect the second planet carrier 23 with the first
  • the torque can be input from the intermediate shaft 5 to the second planetary gear mechanism through the second sun gear 21 and the second planet carrier 23 and output to the output shaft 6 by the second ring gear 22.
  • This structure makes the first The two planetary gear mechanism can output two speed ratios.
  • the first synchronizer 7 and the second synchronizer 8 are provided, so that the transmission 100 can have a four-speed gear shifting structure.
  • the torque demand range is large, the load is uncertain, The situation is complicated, and the four-stage structure is adopted to ensure that the motor runs in the high-efficiency zone and saves energy.
  • the synchronizer is used to shift gears without using a clutch to simplify the structure.
  • the transmission 100 is provided with a first planetary synchronizer 7 and a second synchronizer 8 such as a dual planetary double synchronizer structure, and the shifting mode thereof allows the motor-controlled synchronizer to shift gears.
  • the structure is simple, the shifting speed is fast, High efficiency, there is no drag torque problem of multi-plate clutch and multi-plate brake. At the same time, the cost is lower, the maintenance is simpler, and the synchronizer is used to shift gears without using a clutch to simplify the structure of the transmission 100.
  • the transmission 100 by providing a double planetary row and double synchronizer structure, fast, smooth, and reliable shifting can be achieved, and the structure of the transmission 100 is simple and convenient for maintenance.
  • the axis of the input shaft 4, the axis of the intermediate shaft 5, and the axis of the output shaft 6 are co-linear, and the first planetary gear mechanism and the second planetary gear mechanism are sequentially arranged in the axial direction. In this way, the arrangement of the input shaft 4, the output shaft 6, and the intermediate shaft 5 can be facilitated, and the transmission direction of the torque from the input shaft 4 to the output shaft 6 remains unchanged.
  • the intermediate shaft 5 is arranged between the input shaft 4 and the output shaft 6, and the first synchronizer 7 is arranged on the side of the first planetary gear mechanism facing away from the second planetary gear mechanism.
  • the two synchronizers 8 are arranged between the first planetary gear mechanism and the second planetary gear mechanism. This facilitates the arrangement of the first synchronizer 7 and the second synchronizer 8 and the arrangement of the first synchronizer 7 and the second synchronizer 8
  • the position can make the distance between the first planetary gear mechanism and the second planetary gear mechanism relatively short, thereby making the length of the intermediate shaft 5 shorter, improving the stability of the transmission 100, and saving the length of the transmission 100 in the axial direction. Furthermore, the structure of the transmission 100 is made more compact.
  • one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism
  • the other of the first planetary gear mechanism and the second planetary gear mechanism is a two-stage planetary gear mechanism, that is, When the first planetary gear mechanism is a single-stage planetary gear mechanism, the second planetary gear mechanism is a two-stage planetary gear mechanism, or when the first planetary gear mechanism is a two-stage planetary gear mechanism, the second planetary gear mechanism is a single stage Planetary gear mechanism.
  • the single-stage planetary gear mechanism is a planetary gear mechanism that can drive the ring gear when the sun gear reaches one planetary gear.
  • the single-stage planetary gear mechanism has a simple structure and can effectively enhance the torque transmission efficiency of the transmission 100.
  • the two-stage planetary gear mechanism has two stages.
  • the planetary gear mechanism of the planetary gear, the sun gear can reach the two-stage planetary gear to drive the ring gear.
  • the planetary gears of the two-stage planetary gear mechanism have fewer teeth, and when the planetary carrier is fixed, the rotation directions of the sun gear and the ring gear are the same.
  • first planetary gear mechanism as a single-stage planetary gear mechanism and a second planetary gear mechanism as a two-stage planetary gear mechanism as an example.
  • the transmission 100 may have one gear, that is, the first gear, the second gear, the third gear, and the fourth gear, wherein the speed ratio of the first gear to the fourth gear The speed ratio decreases sequentially, that is, the speed ratio of the first gear u1> the speed ratio of the second gear u2> the speed ratio of the third gear u3> the speed ratio of the fourth gear u4.
  • the following describes the operating states of the first synchronizer 7 and the second synchronizer 8 of each gear of the transmission 100 and the torque transmission path during the transmission of the torque from the input shaft 4 to the output shaft 6 in the transmission 100 with reference to FIG. 1.
  • each synchronizer in the gear change described below is described with reference to FIG. 1, of course, the arrangement direction and position of each synchronizer are not limited to this.
  • the first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100
  • the second synchronizer 8 fixes the second planet carrier 23 to the housing 10 of the transmission 100 .
  • the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11.
  • the torque transmitted to the first planetary gear mechanism is input by the first sun gear 11 and Output from the first planet carrier 13, the first planet carrier 13 transmits torque to the intermediate shaft 5, and then the torque is transmitted to the second sun gear 21 through the intermediate shaft 5, and in the second planetary gear mechanism, to the second planetary gear mechanism
  • the torque is input by the second sun gear 21 and output by the second ring gear 22, which transmits the torque to the output shaft 6.
  • the transmission 100 when the transmission 100 is in the first gear, in the first planetary gear mechanism, the torque is input by the first sun gear 11 and output by the first planet carrier 13 to the intermediate shaft 5. At this time, the torque is relative to the input shaft 4 The rotation direction is the same and the rotation speed is reduced. The torque is transmitted to the second planetary gear mechanism through the intermediate shaft 5 and is input by the second sun gear 21. The second ring gear 22 is output to the output shaft 6. The torque is relative to the second planetary gear mechanism through the second planetary gear mechanism. The input shaft 4 rotates in the same direction and decelerates again. In the first gear, after the torque is transmitted from the input shaft 4 to the transmission 100, it is transmitted through the two-stage reduction of the first planetary gear mechanism and the second planetary gear mechanism. In the transmission 100, torque transmission directions of the input shaft 4 and the output shaft 6 are unchanged.
  • the first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100
  • the second synchronizer 8 connects the first planetary carrier 13 and the second planetary carrier 23.
  • the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11.
  • the torque transmitted to the first planetary gear mechanism is input by the first sun gear 11 and Output from the first planet carrier 13, the first planet carrier 13 transmits the torque to the intermediate shaft 5, and the torque is transmitted to the second sun gear 21 through the intermediate shaft 5.
  • the second synchronizer 8 since the second synchronizer 8 transmits the first A planet carrier 13 is connected to the second planet carrier 23, and torque is transmitted to the second planet carrier 23 through the first planet carrier 13, and the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second planet carrier 23 and It is output by the second ring gear 22, which transmits the torque to the output shaft 6.
  • the two-stage reduction of the mechanism and the second planetary gear mechanism transmits the transmission 100, and the torque transmission direction of the input shaft 4 and the output shaft 6 is unchanged.
  • the input end of the second planetary gear mechanism is the second sun.
  • the input ends of the second planetary gear mechanism are the second sun gear 21 and the second planet carrier 23, so relative to the first gear, when the rotation speed of the input shaft 4 is constant, the second gear is The output rotation of the second planet carrier 23 Greater, so that the first gear ratio u1> second gear ratio u2.
  • the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 fixes the second planet carrier 23 with the casing 10 of the transmission 100.
  • the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11.
  • the first ring gear 12 and the first sun gear 11 are input.
  • the planet carrier 13 outputs and transmits the torque to the intermediate shaft 5.
  • the second synchronizer 8 since the second synchronizer 8 connects the first planet carrier 13 and the second planet carrier 23, the torque is transmitted to the intermediate shaft 5.
  • the second sun gear 21, in the second planetary gear mechanism the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and output by the second ring gear 22, and the second ring gear 22 transmits the torque to the output shaft 6.
  • the first planetary gear mechanism is input by the first ring gear 12 and the first sun gear 11, is output from the first planet carrier 13, and transmits torque to the intermediate shaft 5.
  • the torque is the same as the rotation direction of the input shaft 4 and the rotation speed is reduced.
  • the torque is transmitted to the second sun gear 21 of the second planetary gear mechanism through the intermediate shaft 5.
  • the torque is transmitted by the second sun gear 21 Input and output from the second planet carrier 23 to the output shaft 6, at this time the torque is the same as the rotation direction of the input shaft 4 and the speed is reduced.
  • the first planetary gear when the transmission 100 is in the third gear, the first planetary gear
  • the mechanism and the second planetary gear mechanism can be designed such that when the rotation speed of the input shaft 4 is constant, the rotation speed of the output shaft 6 in the third gear is faster than the rotation speed of the output shaft 6 in the second gear, so that the speed ratio u2 of the second gear> Third gear speed ratio u3.
  • the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 connects the first planet carrier 13 with the second planet carrier 23.
  • the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11.
  • the first ring gear 12 and the first sun gear 11 are input.
  • the planet carrier 13 is output and transmits torque to the intermediate shaft 5.
  • the second synchronizer 8 since the second synchronizer 8 connects the first planet carrier 13 and the second planet carrier 23, the torque is transmitted through the first planet carrier 13.
  • the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second planet carrier 23 and output by the second ring gear 22, and the second ring gear 22 transmits the torque to the output shaft 6. .
  • the first planetary gear mechanism is input by the first ring gear 12 and the first sun gear 11, is output from the first planet carrier 13, and transmits torque to the intermediate shaft 5.
  • the torque is the same as the rotation direction of the input shaft 4 and the speed is reduced.
  • the torque is transmitted to the second sun gear 21 through the intermediate shaft 5 and is input to the second planetary gear mechanism by the second sun gear 21 and the second planet carrier 23.
  • the torque is output to the output shaft 6 by the second ring gear 22, and the torque passes through the second planetary gear mechanism in the same rotation direction with respect to the input shaft 4 and is decelerated again.
  • the torque is transmitted from the input shaft 4 to the transmission 100
  • the transmission 100 is transmitted, and the torque transmission direction of the input shaft 4 and the output shaft 6 is unchanged.
  • the second planetary gear The input of the mechanism is the second sun gear 21, and in the fourth gear, the input of the second planetary gear mechanism is the second sun gear 21 and the second planet carrier 23, so relative to the third gear, when the input shaft 4 When the speed is constant, the fourth gear Output rotational speed of the carrier 23 more, so that the third gear ratio u3> the fourth gear ratio u4.
  • the transmission 100 of the present application belongs to a horizontal transmission 100, which adopts a dual planetary double synchronizer structure.
  • the shifting method can be a motor-controlled synchronizer shift, which has a simple structure, fast shifting, and torque transmission.
  • the transmission 100 has lower manufacturing costs and easier maintenance.
  • the synchronizer is used to shift gears without using a clutch to simplify the structure, and the transmission 100 adopts a four-speed gear shift structure, which can ensure that the motor can save electricity when it is running in the high-efficiency zone.
  • the power driving system according to the embodiment of the present application includes: a driving motor and the transmission 100 of any one of the foregoing embodiments, wherein the driving motor is dynamically coupled to the input shaft 4.
  • the power driving system according to the embodiment of the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission 100 according to the embodiment of the present application, and the structure of the power driving system is simple.
  • the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet the vehicle's requirements for the durability, power transmission efficiency, size, and cost of the transmission 100.
  • the drive motor is arranged coaxially with the input shaft 4, and the drive motor is arranged on the side of the first planetary gear mechanism facing away from the second planetary gear mechanism. In this way, various components of the power drive system can be along the input shaft 4.
  • the axis arrangement further facilitates the arrangement of the power drive system, and does not require extra gears to change the route of torque transmission, thereby improving the torque transmission efficiency of the power drive system.
  • the vehicle according to the embodiment of the present application includes the power driving system of the foregoing embodiment.
  • the vehicle is provided with the power driving system, so that the vehicle has the advantages of smooth shifting, rapid shifting, and high torque transmission efficiency.
  • the output torque range is large, the load is stable, it can cope with complicated road conditions, and has the advantage of saving energy.
  • the vehicle according to the present application may be an electric vehicle or a hybrid vehicle.
  • an object of the present application is to propose a transmission with high efficiency, simple structure, and smooth shifting.
  • the present application also proposes a power drive system having the above transmission.
  • the present application also proposes a vehicle having the above-mentioned power drive system.
  • the transmission according to the present application includes: a first planetary gear mechanism including a first sun gear, a first planet gear, a first planet carrier, and a first ring gear; and a second planetary gear mechanism, the The second planetary gear mechanism includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear, and the second ring gear is connected to an output end of the transmission; an input shaft, and the input shaft and The first sun gear is connected; an intermediate shaft, the first planet carrier is connected to the intermediate shaft, the intermediate shaft is connected to the second sun gear; a first synchronizer, and the first synchronizer connects the A first ring gear is fixed to the transmission housing or the first ring gear is connected to the first sun gear; a second synchronizer, the second synchronizer connects the second planet carrier with the transmission The casing is fixed or connects the second planet carrier with the second sun gear.
  • the output of the transmission includes an output shaft, an axis of the input shaft, an axis of the intermediate shaft, and an axis of the output shaft are collinear.
  • the output of the transmission includes an output shaft, the intermediate shaft is disposed between the input shaft and the output shaft, and the first synchronizer is disposed away from the first planetary gear mechanism. On one side of the second planetary gear mechanism, the second synchronizer is disposed between the first planetary gear mechanism and the second planetary gear mechanism.
  • one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism, and the other of the first planetary gear mechanism and the second planetary gear mechanism It is a two-stage planetary gear mechanism.
  • the transmission is engaged in a first gear
  • the first synchronizer secures the first ring gear to a housing of the transmission
  • the second synchronizer secures the second planet
  • the frame is fixed to the casing of the transmission.
  • the transmission is engaged in a second gear
  • the first synchronizer secures the first ring gear to a housing of the transmission
  • the second synchronizer secures the first planet A carrier is connected to the second planet carrier.
  • the transmission is engaged in a third gear
  • the first synchronizer connects the first sun gear with the first ring gear
  • a second synchronizer connects the second planet carrier with The casing of the transmission is fixed.
  • the transmission is engaged in a fourth gear
  • the first synchronizer connects the first sun gear with the first ring gear
  • a second synchronizer connects the first planet carrier with The second planet carrier is connected.
  • the power drive system includes a drive motor and a transmission according to the present application, and the drive motor is dynamically coupled to the input shaft.
  • the power driving system according to the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission according to the embodiment of the present application, and the structure of the power driving system is simple.
  • the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet vehicle requirements for transmission durability, power transmission efficiency, size, and cost.
  • a vehicle according to the present application includes a power drive system described in the present application.
  • the vehicle according to the present application is provided with the above-mentioned power drive system, so that the vehicle has the advantages of smooth shifting, rapid shifting and high torque transmission efficiency, and can make the vehicle's output torque range large, load stable, and can cope with complicated road conditions. It has the advantage of saving energy.
  • the vehicle according to the present application may be an electric vehicle, a hybrid vehicle, or the like. Additional aspects and advantages of the present application will be partially given in the following description, and some will become apparent from the description of the present application, or be learned through practice of the present application.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)

Abstract

Disclosed are a transmission (100), a power drive system and a vehicle. The transmission (100) comprises: a first planetary gear mechanism, a second planetary gear mechanism, an input shaft (4), an intermediate shaft (5), a first synchronizer (7) and a second synchronizer (8). The first planetary gear mechanism comprises a first sun gear (11), a first planetary gear (14), a first planetary carrier (13) and a first gear ring (12). The second planetary gear mechanism comprises a second sun gear (21), a second planetary gear (24), a second planetary carrier (23) and a second gear ring (22). The second gear ring (22) is connected to an output end of the transmission (100). By means of the first synchronizer (7), the first gear ring (12) is fixed to a housing (10) of the transmission (100), or the first gear ring (12) is connected to the first sun gear (11). By means of the second synchronizer (8), the second planetary carrier (23) is fixed to the housing (10) of the transmission (100), or the second planetary carrier (23) is connected to the second sun gear (21).

Description

变速器、动力驱动***及车辆Transmission, power drive system and vehicle
本申请要求于2018年6月29日提交中国专利局、申请号为201810713252.7，申请名称为“变速器、动力驱动***及车辆”的中国专利申请的优先权，其全部内容通过引用结合在本申请中。This application claims priority from a Chinese patent application filed with the Chinese Patent Office on June 29, 2018, with application number 201810713252.7, and entitled "Transmission, Power Drive System, and Vehicle", the entire contents of which are incorporated herein by reference. .
技术领域Technical field
本申请属于车辆制造技术领域，具体而言，涉及一种变速器、动力驱动***及车辆。The present application belongs to the technical field of vehicle manufacturing, and in particular, relates to a transmission, a power drive system, and a vehicle.
背景技术Background technique
混合驱动汽车、电动汽车、增程式电动汽车是未来汽车发展方向，也是新能源汽车主要形式。相关技术中，动力传动***的结构复杂、工作模式复杂且控制策略繁琐，能量转换效率有待提高，不能充分利用发动机动能和电池电能，存在能量二次转换、控制复杂，效率低的问题。具体而言，相关技术中，车辆的片式离合器和片式制动器控制换挡，但当这两个部件不工作时，因为润滑的缘故，会存在拖曳力矩，造成整个变速器的效率不高。Hybrid-drive vehicles, electric vehicles, and extended-range electric vehicles are the future development direction of vehicles and the main form of new energy vehicles. In the related art, the power transmission system has a complicated structure, a complicated working mode, and a complicated control strategy. The energy conversion efficiency needs to be improved. The engine ’s kinetic energy and battery power cannot be fully utilized. There are problems of secondary energy conversion, complicated control, and low efficiency. Specifically, in the related art, a vehicle's plate clutch and plate brake control shifting, but when these two components are not in operation, drag torque exists due to lubrication, resulting in low efficiency of the entire transmission.
另外，相关技术中的多挡变速器中，多数是通过拨叉、滑套在离合器切断动力时来选择挡位，齿轮对数较多，占用空间大，结构复杂，由此存在改进空间。In addition, in the multi-speed transmissions in the related art, most of them select gears by shifting forks and sliding sleeves when the clutch cuts off power. There are a large number of gear pairs, a large occupied space, and a complicated structure, so there is room for improvement.
发明内容Summary of the invention
本申请旨在至少解决现有技术中存在的技术问题之一。为此，本申请的一个目的在于提出一种效率高且结构简单，换挡平稳的变速器。This application aims to solve at least one of the technical problems existing in the prior art. For this reason, an object of the present application is to propose a transmission with high efficiency, simple structure, and smooth shifting.
根据本申请的变速器，包括：第一行星齿轮机构，所述第一行星齿轮机构包括第一太阳轮、第一行星轮、第一行星架和第一齿圈；第二行星齿轮机构，所述第二行星齿轮机构包括第二太阳轮、第二行星轮、第二行星架和第二齿圈，所述第二齿圈与所述变速器的输出端相连；输入轴，所述输入轴与所述第一太阳轮相连；中间轴，所述第一行星架与所述中间轴相连，所述中间轴与所述第二太阳轮相连；第一同步器，所述第一同步器将所述第一齿圈与变速器的壳体固定或者将所述第一齿圈与所述第一太阳轮连接；第二同步器，所述第二同步器将所述第二行星架与所述变速器的壳体固定或者将所述第二行星架与所述第二太阳轮连接。The transmission according to the present application includes: a first planetary gear mechanism including a first sun gear, a first planet gear, a first planet carrier, and a first ring gear; and a second planetary gear mechanism, the The second planetary gear mechanism includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear, and the second ring gear is connected to an output end of the transmission; an input shaft, and the input shaft and The first sun gear is connected; an intermediate shaft, the first planet carrier is connected to the intermediate shaft, the intermediate shaft is connected to the second sun gear; a first synchronizer, and the first synchronizer connects the A first ring gear is fixed to the transmission housing or the first ring gear is connected to the first sun gear; a second synchronizer, the second synchronizer connects the second planet carrier with the transmission The casing is fixed or connects the second planet carrier with the second sun gear.
根据本申请的变速器，通过设置双行星排双同步器结构，可以实现快速、平顺、可靠地换挡，且变速器的结构简单，便于维护。According to the transmission of the present application, by setting a double planetary row and double synchronizer structure, fast, smooth, and reliable shifting can be achieved, and the structure of the transmission is simple and easy to maintain.
根据本申请的动力驱动***，包括：驱动电机和根据本申请的变速器，所述驱动电机与所述输入轴动力耦合连接。The power drive system according to the present application includes a drive motor and a transmission according to the present application, and the drive motor is dynamically coupled to the input shaft.
根据本申请的动力驱动***通过设置根据本申请实施例的变速器从而具有换挡快、扭矩传递效率高、换挡平顺的优点，且动力驱动***的结构简单。此外，两个同步器合理利用行星排之间的空间，整体上设计更加紧凑，可以很好的满足车辆对变速器耐久性、动力传递效率、尺寸、成本等方面的要求。The power driving system according to the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission according to the embodiment of the present application, and the structure of the power driving system is simple. In addition, the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet vehicle requirements for transmission durability, power transmission efficiency, size, and cost.
根据本申请的车辆包括本申请所述的动力驱动***。A vehicle according to the present application includes a power drive system described in the present application.
根据本申请的车辆通过设置上述动力驱动***，从而使车辆具有换挡平稳、换挡迅速且扭矩传递效率高的优点，且可以使车辆的输出扭矩范围大，载荷稳定，可以应对复杂的路况，具有节省能源的优点，在一些示例中，根据本申请的车辆可以为电动车辆或混合动力车辆等。The vehicle according to the present application is provided with the above-mentioned power drive system, so that the vehicle has the advantages of smooth shifting, rapid shifting and high torque transmission efficiency, and can make the vehicle's output torque range large, load stable, and can cope with complicated road conditions. It has the advantage of saving energy. In some examples, the vehicle according to the present application may be an electric vehicle, a hybrid vehicle, or the like.
本申请的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本申请的实践了解到。Additional aspects and advantages of the present application will be given in part in the following description, part of which will become apparent from the following description, or be learned through practice of the present application.
附图说明BRIEF DESCRIPTION OF THE DRAWINGS
本申请的上述和/或附加的方面和优点从结合下面附图对实施例的描述中将变得明显和容易理解，其中：The above and / or additional aspects and advantages of the present application will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:
图1是根据本申请实施例的变速器的结构示意图。FIG. 1 is a schematic structural diagram of a transmission according to an embodiment of the present application.
附图标记：Reference signs:
变速器100；壳体10； Transmission 100; housing 10;
第一太阳轮11；第一齿圈12；第一行星架13；第一行星轮14； First sun gear 11; first ring gear 12; first planet carrier 13; first planet gear 14;
第二太阳轮21；第二齿圈22；第二行星架23；第二行星轮24； Second sun gear 21; second ring gear 22; second planet carrier 23; second planet gear 24;
输入轴4；中间轴5；输出轴6； Input shaft 4; intermediate shaft 5; output shaft 6;
第一同步器7；第二同步器8。First synchronizer 7; second synchronizer 8.
具体实施方式detailed description
下面详细描述本申请的实施例，所述实施例的示例在附图中示出，其中自始至终相同或类似的标号表示相同或类似的元件或具有相同或类似功能的元件。下面通过参考附图描述的实施例是示例性的，仅用于解释本申请，而不能理解为对本申请的限制。The embodiments of the present application are described in detail below. Examples of the embodiments are shown in the drawings, wherein the same or similar reference numerals represent the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary and are only used to explain the present application, and should not be construed as limiting the present application.
下面参考图1描述根据本申请实施例的变速器100。A transmission 100 according to an embodiment of the present application is described below with reference to FIG. 1.
如图1所示，根据本申请实施例的变速器100包括：第一行星齿轮机构、第二行星齿 轮机构、输入轴4、中间轴5、第一同步器7和第二同步器8。As shown in FIG. 1, a transmission 100 according to an embodiment of the present application includes a first planetary gear mechanism, a second planetary gear mechanism, an input shaft 4, an intermediate shaft 5, a first synchronizer 7, and a second synchronizer 8.
车辆的扭矩可以通过输入轴4输入到变速器100中，在变速器100中扭矩可以经过第一行星齿轮机构和第二行星齿轮机构最终由变速器的输出端输出。同步器用于将变速器100内各部件的连接以实现挡位切换。The torque of the vehicle can be input to the transmission 100 through the input shaft 4, and the torque in the transmission 100 can be finally output by the output of the transmission through the first planetary gear mechanism and the second planetary gear mechanism. The synchronizer is used to connect various components in the transmission 100 to realize gear shifting.
第一行星齿轮机构可以包括多个第一行星轮14，多个第一行星轮14与第一行星架13相连，第二行星齿轮机构可以包括多个第二行星轮24，多个第二行星轮24与第二行星架23相连。当各个行星齿轮机构的太阳轮转动时，各个太阳轮可以带动与之相对应的行星轮转动，与行星轮所对应的行星架可以选择性的转动。如当齿圈固定，行星架不固定时，太阳轮输入，行星轮转动并带动行星架输出；当行星架固定，齿圈不固定时，太阳轮输入，行星轮转动并带动齿圈输出；当行星架和齿圈都不固定时，太阳轮和齿圈输入，行星轮转动并带动行星架输出；当行星架和齿圈都不固定时，太阳轮和行星架输入，行星轮转动并带动齿圈输出。The first planetary gear mechanism may include a plurality of first planetary gears 14, and the plurality of first planetary gears 14 are connected to the first planet carrier 13. The second planetary gear mechanism may include a plurality of second planetary gears 24 and a plurality of second planetary gears. The wheel 24 is connected to the second planet carrier 23. When the sun gear of each planetary gear mechanism rotates, each sun gear can drive the corresponding planet gear to rotate, and the planet carrier corresponding to the planet gear can be selectively rotated. For example, when the ring gear is fixed and the planet carrier is not fixed, the sun gear is input, the planet gear rotates and drives the planet carrier output; when the planet carrier is fixed, the ring gear is not fixed, the sun gear is input, the planet gear rotates and drives the ring gear output; when When the planet carrier and the ring gear are not fixed, the sun gear and the ring gear are input, the planet gear rotates and drives the planet carrier output; when the planet carrier and the ring gear are not fixed, the sun gear and the planet gear are input, the planet gear rotates and drives the tooth Circle output.
第一行星齿轮机构包括第一太阳轮11、第一行星轮14、第一行星架13和第一齿圈12，这样，扭矩在第一行星齿轮机构内传递时，扭矩可以由第一太阳轮11和/或第一齿圈12输入，并由第一行星架13输出到中间轴5。The first planetary gear mechanism includes a first sun gear 11, a first planet gear 14, a first planet carrier 13, and a first ring gear 12, so that when torque is transmitted in the first planetary gear mechanism, the torque can be transmitted by the first sun gear 11 and / or the first ring gear 12 are input and output to the intermediate shaft 5 by the first planet carrier 13.
第二行星齿轮机构包括第二太阳轮21、第二行星轮24、第二行星架23和第二齿圈22，变速器100的输出端包括输出轴6，第二齿圈22与变速器100的输出轴6相连，这样，扭矩可以由第二太阳轮21和/或第二行星架23输入到第二行星齿轮结构，并由第二齿圈22输出到输出轴6。The second planetary gear mechanism includes a second sun gear 21, a second planet gear 24, a second planet carrier 23, and a second ring gear 22. The output end of the transmission 100 includes an output shaft 6. The second ring gear 22 and the output of the transmission 100 The shaft 6 is connected, so that the torque can be input to the second planetary gear structure by the second sun gear 21 and / or the second planet carrier 23 and output to the output shaft 6 by the second ring gear 22.
输入轴4与第一太阳轮11相连，第一行星架13与中间轴5相连，且中间轴5与第二太阳轮21相连，扭矩可以从第一行星齿轮机构内由第一行星架13传递到中间轴5，并经过中间轴5传递到第二行星齿轮机构的第二太阳轮21。The input shaft 4 is connected to the first sun gear 11, the first planet carrier 13 is connected to the intermediate shaft 5, and the intermediate shaft 5 is connected to the second sun gear 21. Torque can be transmitted from the first planetary gear mechanism by the first planet carrier 13. To the intermediate shaft 5 and transmitted to the second sun gear 21 of the second planetary gear mechanism through the intermediate shaft 5.
在一些实施例中，变速器100的输出端还可以包括输出齿轮，输出齿轮空套与中间轴5外，扭矩可以经输出齿轮传递出变速器100，输出齿轮的设置可以改变输出的扭矩的传递方向，从而可以缩小变速器100在输入轴4的轴线方向的尺寸，从而使变速器100可以更方便的布置在车辆上。In some embodiments, the output end of the transmission 100 may further include an output gear, the output gear is idler and the intermediate shaft 5, the torque may be transmitted out of the transmission 100 through the output gear, and the setting of the output gear may change the transmission direction of the output torque, Therefore, the size of the transmission 100 in the axial direction of the input shaft 4 can be reduced, so that the transmission 100 can be more conveniently arranged on the vehicle.
第一同步器7将第一齿圈12与变速器100的壳体10固定或者将第一齿圈12与第一太阳轮11连接：当第一同步器7将第一齿圈12与变速器100的壳体10固定时，扭矩可以由输入轴4通过第一太阳轮11输入到第一行星齿轮机构，并由第一行星架13输出；当第一同步器7将第一齿圈12与第一太阳轮11连接，扭矩可以由输入轴4通过第一太阳轮11和第一齿圈12输入到第一行星齿轮机构并由第一行星架13输出，这样的构造使得第一行星齿轮机构可以输出两种速比。The first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100 or connects the first ring gear 12 to the first sun gear 11: When the first synchronizer 7 connects the first ring gear 12 to the transmission 100 When the casing 10 is fixed, the torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and output by the first planet carrier 13; when the first synchronizer 7 connects the first ring gear 12 with the first The sun gear 11 is connected, and the torque can be input to the first planetary gear mechanism by the input shaft 4 through the first sun gear 11 and the first ring gear 12 and output by the first planet carrier 13. This structure enables the first planetary gear mechanism to output Two speed ratios.
第二同步器8将第二行星架23与变速器100的壳体10固定或者将第二行星架23与第二太阳轮21连接：当第二同步器8将第二行星架23与变速器100的壳体10固定时，扭矩可以由中间轴5通过第二太阳轮21输入到第二行星齿轮机构，并由第二齿圈22输出；当第二同步器8将将第二行星架23与第二太阳轮21连接时，扭矩可以由中间轴5通过第二太阳轮21和第二行星架23输入到第二行星齿轮机构并由第二齿圈22输出到输出轴6，这样的构造使得第二行星齿轮机构可以输出两种速比。The second synchronizer 8 fixes the second planet carrier 23 to the housing 10 of the transmission 100 or connects the second planet carrier 23 to the second sun gear 21: when the second synchronizer 8 connects the second planet carrier 23 to the transmission 100 When the housing 10 is fixed, the torque can be input to the second planetary gear mechanism by the intermediate shaft 5 through the second sun gear 21 and output by the second ring gear 22; when the second synchronizer 8 will connect the second planet carrier 23 with the first When the two sun gears 21 are connected, the torque can be input from the intermediate shaft 5 to the second planetary gear mechanism through the second sun gear 21 and the second planet carrier 23 and output to the output shaft 6 by the second ring gear 22. This structure makes the first The two planetary gear mechanism can output two speed ratios.
本申请实施例的变速器100，通过设置第一同步器7和第二同步器8，使得变速器100可以有四档的换挡结构，对于中、重型卡车，因扭矩需求范围大，载荷不定，工况复杂，采用四档结构，保证了电机在高效区运转，节省电能。采用同步器换挡，不用离合器使得结构简化。In the transmission 100 of the embodiment of the present application, the first synchronizer 7 and the second synchronizer 8 are provided, so that the transmission 100 can have a four-speed gear shifting structure. For medium and heavy trucks, the torque demand range is large, the load is uncertain, The situation is complicated, and the four-stage structure is adopted to ensure that the motor runs in the high-efficiency zone and saves energy. The synchronizer is used to shift gears without using a clutch to simplify the structure.
根据本申请实施例的变速器100通过设置第一同步器7和第二同步器8这种双行星排双同步器结构，其换挡方式使电机控制同步器换挡，结构简单、换挡快、效率高，不存在多片式离合器和多片式制动器的拖曳力矩问题。同时，成本更低、维护更简便，且采用同步器换挡，不用离合器使得变速器100的结构简化。The transmission 100 according to the embodiment of the present application is provided with a first planetary synchronizer 7 and a second synchronizer 8 such as a dual planetary double synchronizer structure, and the shifting mode thereof allows the motor-controlled synchronizer to shift gears. The structure is simple, the shifting speed is fast, High efficiency, there is no drag torque problem of multi-plate clutch and multi-plate brake. At the same time, the cost is lower, the maintenance is simpler, and the synchronizer is used to shift gears without using a clutch to simplify the structure of the transmission 100.
根据本申请实施例的变速器100，通过设置双行星排双同步器结构，可以实现快速、平顺、可靠地换挡，且变速器100的结构简单，便于维护。According to the transmission 100 according to the embodiment of the present application, by providing a double planetary row and double synchronizer structure, fast, smooth, and reliable shifting can be achieved, and the structure of the transmission 100 is simple and convenient for maintenance.
下面根据图1所示，描述根据本申请的变速器100的一些实施例。Hereinafter, some embodiments of the transmission 100 according to the present application will be described based on FIG. 1.
在一些实施例中，如图1所示，输入轴4的轴线、中间轴5的轴线、输出轴6的轴线共线，第一行星齿轮机构和第二行星齿轮机构沿轴向顺次布置，这样，可以方便输入轴4、输出轴6和中间轴5的布置，且使扭矩从输入轴4到输出轴6的传递方向不变。In some embodiments, as shown in FIG. 1, the axis of the input shaft 4, the axis of the intermediate shaft 5, and the axis of the output shaft 6 are co-linear, and the first planetary gear mechanism and the second planetary gear mechanism are sequentially arranged in the axial direction. In this way, the arrangement of the input shaft 4, the output shaft 6, and the intermediate shaft 5 can be facilitated, and the transmission direction of the torque from the input shaft 4 to the output shaft 6 remains unchanged.
在一些实施例中，如图1所示，中间轴5布置在输入轴4与输出轴6之间，第一同步器7布置在第一行星齿轮机构背离第二行星齿轮机构的一侧，第二同步器8布置在第一行星齿轮机构与第二行星齿轮机构之间这样，方便第一同步器7和第二同步器8的布置，且第一同步器7和第二同步器8的布置位置可以使第一行星齿轮机构和第二行星齿轮机构的距离较近，进而可以使中间轴5的长度可以较短，提升变速器100的稳定性，也可以节省变速器100在轴向上的长度，进而使变速器100的结构更紧凑。In some embodiments, as shown in FIG. 1, the intermediate shaft 5 is arranged between the input shaft 4 and the output shaft 6, and the first synchronizer 7 is arranged on the side of the first planetary gear mechanism facing away from the second planetary gear mechanism. The two synchronizers 8 are arranged between the first planetary gear mechanism and the second planetary gear mechanism. This facilitates the arrangement of the first synchronizer 7 and the second synchronizer 8 and the arrangement of the first synchronizer 7 and the second synchronizer 8 The position can make the distance between the first planetary gear mechanism and the second planetary gear mechanism relatively short, thereby making the length of the intermediate shaft 5 shorter, improving the stability of the transmission 100, and saving the length of the transmission 100 in the axial direction. Furthermore, the structure of the transmission 100 is made more compact.
在一些实施例中，第一行星齿轮机构和第二行星齿轮机构中的一个为单级行星齿轮机构，第一行星齿轮机构和第二行星齿轮机构中的另一个为双级行星齿轮机构，即当第一行星齿轮机构为单级行星齿轮机构时，第二行星齿轮机构为双级行星齿轮机构，或者，当第一行星齿轮机构为双级行星齿轮机构时，第二行星齿轮机构为单级行星齿轮机构。In some embodiments, one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism, and the other of the first planetary gear mechanism and the second planetary gear mechanism is a two-stage planetary gear mechanism, that is, When the first planetary gear mechanism is a single-stage planetary gear mechanism, the second planetary gear mechanism is a two-stage planetary gear mechanism, or when the first planetary gear mechanism is a two-stage planetary gear mechanism, the second planetary gear mechanism is a single stage Planetary gear mechanism.
单级行星齿轮机构即太阳轮通达一级行星轮即可驱动齿圈的行星齿轮机构，单级行星齿轮机构结构简单，可以有效增强变速器100的扭矩传递效率，双级行星齿轮机构即具有 双级行星轮的行星齿轮机构，太阳轮通达两级行星轮即可驱动齿圈。双级行星齿轮机构的行星架齿数较少，且当固定行星架时太阳轮和齿圈的转动方向相同。The single-stage planetary gear mechanism is a planetary gear mechanism that can drive the ring gear when the sun gear reaches one planetary gear. The single-stage planetary gear mechanism has a simple structure and can effectively enhance the torque transmission efficiency of the transmission 100. The two-stage planetary gear mechanism has two stages. The planetary gear mechanism of the planetary gear, the sun gear can reach the two-stage planetary gear to drive the ring gear. The planetary gears of the two-stage planetary gear mechanism have fewer teeth, and when the planetary carrier is fixed, the rotation directions of the sun gear and the ring gear are the same.
下面的实施例参照图1以第一行星齿轮机构为单级行星齿轮机构，第二行星齿轮机构为双级行星齿轮机构为例描述。The following embodiment is described with reference to FIG. 1 by taking a first planetary gear mechanism as a single-stage planetary gear mechanism and a second planetary gear mechanism as a two-stage planetary gear mechanism as an example.
在一些实施例中，根据本申请的实施例的变速器100可以具有个挡位，即第一挡、第二挡、第三挡和第四挡，其中，第一挡的速比到第四挡的速比依次减小，即第一挡的速比u1＞第二挡的速比u2＞第三挡的速比u3＞第四挡的速比u4，在一些示例中，第一挡的速比u1＝8、第二挡的速比u2＝4、第三挡的速比u3＝2、第四挡的速比u4＝1。In some embodiments, the transmission 100 according to the embodiment of the present application may have one gear, that is, the first gear, the second gear, the third gear, and the fourth gear, wherein the speed ratio of the first gear to the fourth gear The speed ratio decreases sequentially, that is, the speed ratio of the first gear u1> the speed ratio of the second gear u2> the speed ratio of the third gear u3> the speed ratio of the fourth gear u4. In some examples, the speed of the first gear The ratio u1 = 8, the second speed ratio u2 = 4, the third speed ratio u3 = 2, and the fourth speed ratio u4 = 1.
下面参照图1描述变速器100的各挡位的第一同步器7和第二同步器8的工作状态，及扭矩在变速器100中由输入轴4传递到输出轴6过程中的扭矩传递路径。The following describes the operating states of the first synchronizer 7 and the second synchronizer 8 of each gear of the transmission 100 and the torque transmission path during the transmission of the torque from the input shaft 4 to the output shaft 6 in the transmission 100 with reference to FIG. 1.
下文所述的挡位变化中的各个同步器的位置参照图1描述，当然，各个同步器的布置方向和布置位置不限于此。The position of each synchronizer in the gear change described below is described with reference to FIG. 1, of course, the arrangement direction and position of each synchronizer are not limited to this.
当变速器100挂入第一挡时，第一同步器7将第一齿圈12与变速器100的壳体10固定，且第二同步器8将第二行星架23与变速器100的壳体10固定。When the transmission 100 is in the first gear, the first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100, and the second synchronizer 8 fixes the second planet carrier 23 to the housing 10 of the transmission 100 .
这样，扭矩由输入轴4传入变速器100，输入轴4将扭矩传递到第一太阳轮11，在第一行星齿轮机构中，传递到第一行星齿轮机构的扭矩由第一太阳轮11输入并由第一行星架13输出，第一行星架13将扭矩传递到中间轴5，扭矩再通过中间轴5传递给第二太阳轮21，在第二行星齿轮机构中，传递到第二行星齿轮机构的扭矩由第二太阳轮21输入并由第二齿圈22输出，第二齿圈22将扭矩传递到输出轴6。In this way, the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11. In the first planetary gear mechanism, the torque transmitted to the first planetary gear mechanism is input by the first sun gear 11 and Output from the first planet carrier 13, the first planet carrier 13 transmits torque to the intermediate shaft 5, and then the torque is transmitted to the second sun gear 21 through the intermediate shaft 5, and in the second planetary gear mechanism, to the second planetary gear mechanism The torque is input by the second sun gear 21 and output by the second ring gear 22, which transmits the torque to the output shaft 6.
由此，变速器100在第一挡位时，在第一行星齿轮机构中，扭矩由第一太阳轮11输入，并由第一行星架13输出到中间轴5，此时扭矩相对于输入轴4的转动方向相同、转速降低，扭矩经过中间轴5传递到第二行星齿轮机构，并由第二太阳轮21输入，第二齿圈22输出到输出轴6，扭矩经过第二行星齿轮机构相对于输入轴4的转动方向相同，并再次减速，在第一挡位时，扭矩从输入轴4传递到变速器100中后，经过第一行星齿轮机构和第二行星齿轮机构的二级减速，传递出变速器100，且输入轴4与输出轴6的扭矩传递方向不变。Therefore, when the transmission 100 is in the first gear, in the first planetary gear mechanism, the torque is input by the first sun gear 11 and output by the first planet carrier 13 to the intermediate shaft 5. At this time, the torque is relative to the input shaft 4 The rotation direction is the same and the rotation speed is reduced. The torque is transmitted to the second planetary gear mechanism through the intermediate shaft 5 and is input by the second sun gear 21. The second ring gear 22 is output to the output shaft 6. The torque is relative to the second planetary gear mechanism through the second planetary gear mechanism. The input shaft 4 rotates in the same direction and decelerates again. In the first gear, after the torque is transmitted from the input shaft 4 to the transmission 100, it is transmitted through the two-stage reduction of the first planetary gear mechanism and the second planetary gear mechanism. In the transmission 100, torque transmission directions of the input shaft 4 and the output shaft 6 are unchanged.
当变速器100挂入第二挡时，第一同步器7将第一齿圈12与变速器100的壳体10固定，且第二同步器8将第一行星架13与第二行星架23连接。When the transmission 100 is in the second gear, the first synchronizer 7 fixes the first ring gear 12 to the housing 10 of the transmission 100, and the second synchronizer 8 connects the first planetary carrier 13 and the second planetary carrier 23.
这样，扭矩由输入轴4传入变速器100，输入轴4将扭矩传递到第一太阳轮11，在第一行星齿轮机构中，传递到第一行星齿轮机构的扭矩由第一太阳轮11输入并由第一行星架13输出，第一行星架13将扭矩传递到中间轴5，扭矩通过中间轴5传递给第二太阳轮21，在第二行星齿轮机构中，由于第二同步器8将第一行星架13与第二行星架23连接，扭矩通过第一行星架13传递给第二行星架23，传递到第二行星齿轮机构的扭矩由第二太阳轮 21和第二行星架23输入并由第二齿圈22输出，第二齿圈22将扭矩传递到输出轴6。In this way, the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11. In the first planetary gear mechanism, the torque transmitted to the first planetary gear mechanism is input by the first sun gear 11 and Output from the first planet carrier 13, the first planet carrier 13 transmits the torque to the intermediate shaft 5, and the torque is transmitted to the second sun gear 21 through the intermediate shaft 5. In the second planetary gear mechanism, since the second synchronizer 8 transmits the first A planet carrier 13 is connected to the second planet carrier 23, and torque is transmitted to the second planet carrier 23 through the first planet carrier 13, and the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second planet carrier 23 and It is output by the second ring gear 22, which transmits the torque to the output shaft 6.
由此，变速器100在第二挡位时，在第一行星齿轮机构中，扭矩由第一太阳轮11输入，并由第一行星架13输出到中间轴5，此时扭矩相对于输入轴4的转动方向相同、转速降低，扭矩经过中间轴5传递到第二太阳轮21，并由第二太阳轮21和第二行星架23输入到第二行星齿轮机构，扭矩由第二齿圈22输出到输出轴6，扭矩经过第二行星齿轮机构相对于输入轴4的转动方向相同，并再次减速，在第一挡位时，扭矩从输入轴4传递到变速器100中后，经过第一行星齿轮机构和第二行星齿轮机构的二级减速，传递出变速器100，且输入轴4与输出轴6的扭矩传递方向不变，在第一挡时，第二行星齿轮机构的输入端为第二太阳轮21，而第二挡时，第二行星齿轮机构的输入端为第二太阳轮21和第二行星架23，所以相对于第一挡，当输入轴4的转速一定时，第二挡时第二行星架23的输出转速更大，从而使第一挡的速比u1＞第二挡的速比u2。Therefore, when the transmission 100 is in the second gear, in the first planetary gear mechanism, torque is input by the first sun gear 11 and output by the first planet carrier 13 to the intermediate shaft 5. At this time, the torque is relative to the input shaft 4 The rotation direction is the same and the rotation speed is reduced. The torque is transmitted to the second sun gear 21 through the intermediate shaft 5 and is input to the second planetary gear mechanism by the second sun gear 21 and the second planet carrier 23. The torque is output by the second ring gear 22 To the output shaft 6, the torque passes through the second planetary gear mechanism in the same direction of rotation relative to the input shaft 4, and decelerates again. In the first gear, the torque is transmitted from the input shaft 4 to the transmission 100, and then passes through the first planetary gear. The two-stage reduction of the mechanism and the second planetary gear mechanism transmits the transmission 100, and the torque transmission direction of the input shaft 4 and the output shaft 6 is unchanged. In the first gear, the input end of the second planetary gear mechanism is the second sun. In the second gear, in the second gear, the input ends of the second planetary gear mechanism are the second sun gear 21 and the second planet carrier 23, so relative to the first gear, when the rotation speed of the input shaft 4 is constant, the second gear is The output rotation of the second planet carrier 23 Greater, so that the first gear ratio u1> second gear ratio u2.
当变速器100挂入第三挡时，第一同步器7将第一太阳轮11与第一齿圈12连接，且第二同步器8将第二行星架23与变速器100的壳体10固定。When the transmission 100 is in the third gear, the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 fixes the second planet carrier 23 with the casing 10 of the transmission 100.
这样，扭矩由输入轴4传入变速器100，输入轴4将扭矩传递到第一太阳轮11，在第一行星齿轮机构中，由第一齿圈12和第一太阳轮11输入，从第一行星架13输出，并将扭矩传递到中间轴5，在第二行星齿轮机构中，由于第二同步器8将第一行星架13与第二行星架23连接，扭矩再通过中间轴5传递给第二太阳轮21，在第二行星齿轮机构中，传递到第二行星齿轮机构的扭矩由第二太阳轮21输入并由第二齿圈22输出，第二齿圈22将扭矩传递到输出轴6。In this way, the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11. In the first planetary gear mechanism, the first ring gear 12 and the first sun gear 11 are input. The planet carrier 13 outputs and transmits the torque to the intermediate shaft 5. In the second planetary gear mechanism, since the second synchronizer 8 connects the first planet carrier 13 and the second planet carrier 23, the torque is transmitted to the intermediate shaft 5. The second sun gear 21, in the second planetary gear mechanism, the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and output by the second ring gear 22, and the second ring gear 22 transmits the torque to the output shaft 6.
由此，变速器100在第三挡位时，第一行星齿轮机构中，由第一齿圈12和第一太阳轮11输入，从第一行星架13输出，并将扭矩传递到中间轴5，此时扭矩相对于输入轴4的转动方向相同、转速降低，扭矩经过中间轴5传递到第二行星齿轮机构的第二太阳轮21，在第二行星齿轮机构中，扭矩由第二太阳轮21输入，并由第二行星架23输出到输出轴6，此时扭矩相对于输入轴4的转动方向相同、转速降低，相对于第二挡，当变速器100在第三挡时，第一行星齿轮机构和第二行星齿轮机构可以设计为当输入轴4转速一定时，第三挡的输出轴6的转速比第二挡的输出轴6的转速快，从而使第二挡的速比u2＞第三挡的速比u3。Therefore, when the transmission 100 is in the third gear, the first planetary gear mechanism is input by the first ring gear 12 and the first sun gear 11, is output from the first planet carrier 13, and transmits torque to the intermediate shaft 5. At this time, the torque is the same as the rotation direction of the input shaft 4 and the rotation speed is reduced. The torque is transmitted to the second sun gear 21 of the second planetary gear mechanism through the intermediate shaft 5. In the second planetary gear mechanism, the torque is transmitted by the second sun gear 21 Input and output from the second planet carrier 23 to the output shaft 6, at this time the torque is the same as the rotation direction of the input shaft 4 and the speed is reduced. Compared with the second gear, when the transmission 100 is in the third gear, the first planetary gear The mechanism and the second planetary gear mechanism can be designed such that when the rotation speed of the input shaft 4 is constant, the rotation speed of the output shaft 6 in the third gear is faster than the rotation speed of the output shaft 6 in the second gear, so that the speed ratio u2 of the second gear> Third gear speed ratio u3.
当变速器100挂入第四挡时，第一同步器7将第一太阳轮11与第一齿圈12连接，且第二同步器8将第一行星架13与第二行星架23连接。When the transmission 100 is in the fourth gear, the first synchronizer 7 connects the first sun gear 11 with the first ring gear 12, and the second synchronizer 8 connects the first planet carrier 13 with the second planet carrier 23.
这样，扭矩由输入轴4传入变速器100，输入轴4将扭矩传递到第一太阳轮11，在第一行星齿轮机构中，由第一齿圈12和第一太阳轮11输入，从第一行星架13输出，并将扭矩传递到中间轴5，在第二行星齿轮机构中，由于第二同步器8将第一行星架13与第二行 星架23连接，扭矩通过第一行星架13传递给第二行星架23，传递到第二行星齿轮机构的扭矩由第二太阳轮21和第二行星架23输入并由第二齿圈22输出，第二齿圈22将扭矩传递到输出轴6。In this way, the torque is transmitted to the transmission 100 through the input shaft 4, and the input shaft 4 transmits the torque to the first sun gear 11. In the first planetary gear mechanism, the first ring gear 12 and the first sun gear 11 are input. The planet carrier 13 is output and transmits torque to the intermediate shaft 5. In the second planetary gear mechanism, since the second synchronizer 8 connects the first planet carrier 13 and the second planet carrier 23, the torque is transmitted through the first planet carrier 13. To the second planet carrier 23, the torque transmitted to the second planetary gear mechanism is input by the second sun gear 21 and the second planet carrier 23 and output by the second ring gear 22, and the second ring gear 22 transmits the torque to the output shaft 6. .
由此，变速器100在第四挡位时，第一行星齿轮机构中，由第一齿圈12和第一太阳轮11输入，从第一行星架13输出，并将扭矩传递到中间轴5，此时扭矩相对于输入轴4的转动方向相同、转速降低，扭矩经过中间轴5传递到第二太阳轮21，并由第二太阳轮21和第二行星架23输入到第二行星齿轮机构，扭矩由第二齿圈22输出到输出轴6，扭矩经过第二行星齿轮机构相对于输入轴4的转动方向相同，并再次减速，在第一挡位时，扭矩从输入轴4传递到变速器100中后，经过第一行星齿轮机构和第二行星齿轮机构的二级减速，传递出变速器100，且输入轴4与输出轴6的扭矩传递方向不变，在第三挡时，第二行星齿轮机构的输入端为第二太阳轮21，而第四挡时，第二行星齿轮机构的输入端为第二太阳轮21和第二行星架23，所以相对于第三挡，当输入轴4的转速一定时，第四挡时第二行星架23的输出转速更大，从而使第三挡的速比u3＞第四挡的速比u4。Therefore, when the transmission 100 is in the fourth gear, the first planetary gear mechanism is input by the first ring gear 12 and the first sun gear 11, is output from the first planet carrier 13, and transmits torque to the intermediate shaft 5. At this time, the torque is the same as the rotation direction of the input shaft 4 and the speed is reduced. The torque is transmitted to the second sun gear 21 through the intermediate shaft 5 and is input to the second planetary gear mechanism by the second sun gear 21 and the second planet carrier 23. The torque is output to the output shaft 6 by the second ring gear 22, and the torque passes through the second planetary gear mechanism in the same rotation direction with respect to the input shaft 4 and is decelerated again. In the first gear, the torque is transmitted from the input shaft 4 to the transmission 100 After middle, after the two-stage reduction of the first planetary gear mechanism and the second planetary gear mechanism, the transmission 100 is transmitted, and the torque transmission direction of the input shaft 4 and the output shaft 6 is unchanged. In the third gear, the second planetary gear The input of the mechanism is the second sun gear 21, and in the fourth gear, the input of the second planetary gear mechanism is the second sun gear 21 and the second planet carrier 23, so relative to the third gear, when the input shaft 4 When the speed is constant, the fourth gear Output rotational speed of the carrier 23 more, so that the third gear ratio u3> the fourth gear ratio u4.
综上所述，本申请的变速器100属于一种横置式变速器100，采用双行星排双同步器结构，其换挡方式可以是电机控制同步器换挡，具有结构简单、换挡快、扭矩传递效率高的优点，且不存在多片式离合器和多片式制动器的拖曳力矩问题。同时，变速器100的制造成本更低、维护更简便。To sum up, the transmission 100 of the present application belongs to a horizontal transmission 100, which adopts a dual planetary double synchronizer structure. The shifting method can be a motor-controlled synchronizer shift, which has a simple structure, fast shifting, and torque transmission. The advantage of high efficiency, and there is no drag torque problem of multi-plate clutches and multi-plate brakes. At the same time, the transmission 100 has lower manufacturing costs and easier maintenance.
采用同步器换挡，不用离合器使得结构简化，且变速器100采用四挡变速的结构，可以保证电机在高效区运转时，节省电能。The synchronizer is used to shift gears without using a clutch to simplify the structure, and the transmission 100 adopts a four-speed gear shift structure, which can ensure that the motor can save electricity when it is running in the high-efficiency zone.
根据本申请实施例的动力驱动***包括：驱动电机和上述任一种实施例的变速器100，其中驱动电机与输入轴4动力耦合连接。这样，根据本申请实施例的动力驱动***通过设置根据本申请实施例的变速器100从而具有换挡快、扭矩传递效率高、换挡平顺的优点，且动力驱动***的结构简单。此外，两个同步器合理利用行星排之间的空间，整体上设计更加紧凑，可以很好的满足车辆对变速器100耐久性、动力传递效率、尺寸、成本等方面的要求。The power driving system according to the embodiment of the present application includes: a driving motor and the transmission 100 of any one of the foregoing embodiments, wherein the driving motor is dynamically coupled to the input shaft 4. In this way, the power driving system according to the embodiment of the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission 100 according to the embodiment of the present application, and the structure of the power driving system is simple. In addition, the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet the vehicle's requirements for the durability, power transmission efficiency, size, and cost of the transmission 100.
在一些实施例中，驱动电机与输入轴4同轴布置，且驱动电机布置在第一行星齿轮机构背离第二行星齿轮机构的一侧，这样，动力驱动***的各个部件可以沿输入轴4的轴线布置，进而方便动力驱动***的布置，且不需要多余的齿轮等改变扭矩传递的路线，从而提高动力驱动***的扭矩传递效率。In some embodiments, the drive motor is arranged coaxially with the input shaft 4, and the drive motor is arranged on the side of the first planetary gear mechanism facing away from the second planetary gear mechanism. In this way, various components of the power drive system can be along the input shaft 4. The axis arrangement further facilitates the arrangement of the power drive system, and does not require extra gears to change the route of torque transmission, thereby improving the torque transmission efficiency of the power drive system.
根据本申请实施例的车辆，包括：上述实施例的动力驱动***，车辆通过设置上述动力驱动***，从而使车辆具有换挡平稳、换挡迅速且扭矩传递效率高的优点，且可以使车辆的输出扭矩范围大，载荷稳定，可以应对复杂的路况，具有节省能源的优点，在一些示 例中，根据本申请的车辆可以为电动车辆或混合动力车辆等。The vehicle according to the embodiment of the present application includes the power driving system of the foregoing embodiment. The vehicle is provided with the power driving system, so that the vehicle has the advantages of smooth shifting, rapid shifting, and high torque transmission efficiency. The output torque range is large, the load is stable, it can cope with complicated road conditions, and has the advantage of saving energy. In some examples, the vehicle according to the present application may be an electric vehicle or a hybrid vehicle.
在本申请的描述中，需要理解的是，术语“中心”、“纵向”、“横向”、“长度”、“宽度”、“厚度”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”、“顺时针”、“逆时针”、“轴向”、“径向”、“周向”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请的限制。In the description of this application, it should be understood that the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", " Rear "," left "," right "," vertical "," horizontal "," top "," bottom "," inside "," outside "," clockwise "," counterclockwise "," axial " The azimuth or position relationship indicated by ", radial", "circumferential", etc. is based on the azimuth or position relationship shown in the drawings, and is only for the convenience of describing this application and simplifying the description, rather than indicating or suggesting the device or The element must have a specific orientation, be constructed and operate in a specific orientation, and therefore cannot be understood as a limitation on this application.
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示意性实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不一定指的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任何的一个或多个实施例或示例中以合适的方式结合。In the description of this specification, the description with reference to the terms “one embodiment”, “some embodiments”, “exemplary embodiments”, “examples”, “specific examples”, or “some examples”, etc., means that the implementation is combined The specific features, structures, materials, or characteristics described in the examples or examples are included in at least one embodiment or example of the present application. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.
尽管已经示出和描述了本申请的实施例，本领域的普通技术人员可以理解：在不脱离本申请的原理和宗旨的情况下可以对这些实施例进行多种变化、修改、替换和变型，本申请的范围由权利要求及其等同物限定。Although the embodiments of the present application have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, replacements, and variations can be made to these embodiments without departing from the principles and spirit of the present application, The scope of the application is defined by the claims and their equivalents.
本申请旨在至少解决现有技术中存在的技术问题之一。为此，本申请的一个目的在于提出一种效率高且结构简单，换挡平稳的变速器。This application aims to solve at least one of the technical problems existing in the prior art. For this reason, an object of the present application is to propose a transmission with high efficiency, simple structure, and smooth shifting.
本申请还提出一种具有上述变速器的动力驱动***。The present application also proposes a power drive system having the above transmission.
本申请还提出一种具有上述动力驱动***的车辆。The present application also proposes a vehicle having the above-mentioned power drive system.
根据本申请的变速器，包括：第一行星齿轮机构，所述第一行星齿轮机构包括第一太阳轮、第一行星轮、第一行星架和第一齿圈；第二行星齿轮机构，所述第二行星齿轮机构包括第二太阳轮、第二行星轮、第二行星架和第二齿圈，所述第二齿圈与所述变速器的输出端相连；输入轴，所述输入轴与所述第一太阳轮相连；中间轴，所述第一行星架与所述中间轴相连，所述中间轴与所述第二太阳轮相连；第一同步器，所述第一同步器将所述第一齿圈与变速器的壳体固定或者将所述第一齿圈与所述第一太阳轮连接；第二同步器，所述第二同步器将所述第二行星架与所述变速器的壳体固定或者将所述第二行星架与所述第二太阳轮连接。The transmission according to the present application includes: a first planetary gear mechanism including a first sun gear, a first planet gear, a first planet carrier, and a first ring gear; and a second planetary gear mechanism, the The second planetary gear mechanism includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear, and the second ring gear is connected to an output end of the transmission; an input shaft, and the input shaft and The first sun gear is connected; an intermediate shaft, the first planet carrier is connected to the intermediate shaft, the intermediate shaft is connected to the second sun gear; a first synchronizer, and the first synchronizer connects the A first ring gear is fixed to the transmission housing or the first ring gear is connected to the first sun gear; a second synchronizer, the second synchronizer connects the second planet carrier with the transmission The casing is fixed or connects the second planet carrier with the second sun gear.
根据本申请的变速器，通过设置双行星排双同步器结构，可以实现快速、平顺、可靠地换挡，且变速器的结构简单，便于维护。According to the transmission of the present application, by setting a double planetary row and double synchronizer structure, fast, smooth, and reliable shifting can be achieved, and the structure of the transmission is simple and easy to maintain.
在一些实施例中，所述变速器的输出端包括输出轴，所述输入轴的轴线、所述中间轴的轴线、所述输出轴的轴线共线。In some embodiments, the output of the transmission includes an output shaft, an axis of the input shaft, an axis of the intermediate shaft, and an axis of the output shaft are collinear.
在一些实施例中，所述变速器的输出端包括输出轴，所述中间轴布置在所述输入轴与 所述输出轴之间，所述第一同步器布置在所述第一行星齿轮机构背离所述第二行星齿轮机构的一侧，所述第二同步器布置在所述第一行星齿轮机构与所述第二行星齿轮机构之间。In some embodiments, the output of the transmission includes an output shaft, the intermediate shaft is disposed between the input shaft and the output shaft, and the first synchronizer is disposed away from the first planetary gear mechanism. On one side of the second planetary gear mechanism, the second synchronizer is disposed between the first planetary gear mechanism and the second planetary gear mechanism.
在一些实施例中，所述第一行星齿轮机构和所述第二行星齿轮机构中的一个为单级行星齿轮机构，所述第一行星齿轮机构和所述第二行星齿轮机构中的另一个为双级行星齿轮机构。In some embodiments, one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism, and the other of the first planetary gear mechanism and the second planetary gear mechanism It is a two-stage planetary gear mechanism.
在一些实施例中，所述变速器挂入第一挡，所述第一同步器将所述第一齿圈与所述变速器的壳体固定，且所述第二同步器将所述第二行星架与所述变速器的壳体固定。In some embodiments, the transmission is engaged in a first gear, the first synchronizer secures the first ring gear to a housing of the transmission, and the second synchronizer secures the second planet The frame is fixed to the casing of the transmission.
在一些实施例中，所述变速器挂入第二挡，所述第一同步器将所述第一齿圈与所述变速器的壳体固定，且所述第二同步器将所述第一行星架与所述第二行星架连接。In some embodiments, the transmission is engaged in a second gear, the first synchronizer secures the first ring gear to a housing of the transmission, and the second synchronizer secures the first planet A carrier is connected to the second planet carrier.
在一些实施例中，所述变速器挂入第三挡，所述第一同步器将所述第一太阳轮与所述第一齿圈连接，且第二同步器将所述第二行星架与所述变速器的壳体固定。In some embodiments, the transmission is engaged in a third gear, the first synchronizer connects the first sun gear with the first ring gear, and a second synchronizer connects the second planet carrier with The casing of the transmission is fixed.
在一些实施例中，所述变速器挂入第四挡，所述第一同步器将所述第一太阳轮与所述第一齿圈连接，且第二同步器将所述第一行星架与所述第二行星架连接。In some embodiments, the transmission is engaged in a fourth gear, the first synchronizer connects the first sun gear with the first ring gear, and a second synchronizer connects the first planet carrier with The second planet carrier is connected.
根据本申请的动力驱动***，包括：驱动电机和根据本申请的变速器，所述驱动电机与所述输入轴动力耦合连接。The power drive system according to the present application includes a drive motor and a transmission according to the present application, and the drive motor is dynamically coupled to the input shaft.
根据本申请的动力驱动***通过设置根据本申请实施例的变速器从而具有换挡快、扭矩传递效率高、换挡平顺的优点，且动力驱动***的结构简单。此外，两个同步器合理利用行星排之间的空间，整体上设计更加紧凑，可以很好的满足车辆对变速器耐久性、动力传递效率、尺寸、成本等方面的要求。The power driving system according to the present application has the advantages of fast shifting, high torque transmission efficiency, and smooth shifting by providing the transmission according to the embodiment of the present application, and the structure of the power driving system is simple. In addition, the two synchronizers make reasonable use of the space between the planetary rows, and the overall design is more compact, which can well meet vehicle requirements for transmission durability, power transmission efficiency, size, and cost.
根据本申请的车辆包括本申请所述的动力驱动***。A vehicle according to the present application includes a power drive system described in the present application.
根据本申请的车辆通过设置上述动力驱动***，从而使车辆具有换挡平稳、换挡迅速且扭矩传递效率高的优点，且可以使车辆的输出扭矩范围大，载荷稳定，可以应对复杂的路况，具有节省能源的优点，在一些示例中，根据本申请的车辆可以为电动车辆或混合动力车辆等。本申请的附加方面和优点将在下面的描述中部分给出，部分将从本申请的描述中变得明显，或通过本申请的实践了解到。The vehicle according to the present application is provided with the above-mentioned power drive system, so that the vehicle has the advantages of smooth shifting, rapid shifting and high torque transmission efficiency, and can make the vehicle's output torque range large, load stable, and can cope with complicated road conditions. It has the advantage of saving energy. In some examples, the vehicle according to the present application may be an electric vehicle, a hybrid vehicle, or the like. Additional aspects and advantages of the present application will be partially given in the following description, and some will become apparent from the description of the present application, or be learned through practice of the present application.

Claims (10)

  1. 一种变速器，其特征在于，包括：A transmission characterized by comprising:
    第一行星齿轮机构，所述第一行星齿轮机构包括第一太阳轮、第一行星轮、第一行星架和第一齿圈；A first planetary gear mechanism, which includes a first sun gear, a first planet gear, a first planet carrier, and a first ring gear;
    第二行星齿轮机构，所述第二行星齿轮机构包括第二太阳轮、第二行星轮、第二行星架和第二齿圈，所述第二齿圈与所述变速器的输出端相连；A second planetary gear mechanism, which includes a second sun gear, a second planet gear, a second planet carrier, and a second ring gear, and the second ring gear is connected to an output end of the transmission;
    输入轴，所述输入轴与所述第一太阳轮相连；An input shaft connected to the first sun gear;
    中间轴，所述第一行星架与所述中间轴相连，所述中间轴与所述第二太阳轮相连；An intermediate shaft, the first planet carrier is connected to the intermediate shaft, and the intermediate shaft is connected to the second sun gear;
    第一同步器，所述第一同步器将所述第一齿圈与变速器的壳体固定或者将所述第一齿圈与所述第一太阳轮连接；A first synchronizer that fixes the first ring gear to a transmission housing or connects the first ring gear to the first sun gear;
    第二同步器，所述第二同步器将所述第二行星架与所述变速器的壳体固定或者将所述第二行星架与所述第二太阳轮连接。A second synchronizer, which fixes the second planet carrier to the housing of the transmission or connects the second planet carrier to the second sun gear.
  2. 根据权利要求1所述的变速器，其特征在于，所述变速器的输出端包括输出轴，所述输入轴的轴线、所述中间轴的轴线、所述输出轴的轴线共线。The transmission according to claim 1, wherein an output end of the transmission includes an output shaft, an axis of the input shaft, an axis of the intermediate shaft, and an axis of the output shaft are collinear.
  3. 根据权利要求1所述的变速器，其特征在于，所述变速器的输出端包括输出轴，所述中间轴布置在所述输入轴与所述输出轴之间，所述第一同步器布置在所述第一行星齿轮机构背离所述第二行星齿轮机构的一侧，所述第二同步器布置在所述第一行星齿轮机构与所述第二行星齿轮机构之间。The transmission according to claim 1, wherein an output end of the transmission includes an output shaft, the intermediate shaft is disposed between the input shaft and the output shaft, and the first synchronizer is disposed at the The side of the first planetary gear mechanism facing away from the second planetary gear mechanism, and the second synchronizer is disposed between the first planetary gear mechanism and the second planetary gear mechanism.
  4. 根据权利要求1所述的变速器，其特征在于，所述第一行星齿轮机构和所述第二行星齿轮机构中的一个为单级行星齿轮机构，所述第一行星齿轮机构和所述第二行星齿轮机构中的另一个为双级行星齿轮机构。The transmission according to claim 1, wherein one of the first planetary gear mechanism and the second planetary gear mechanism is a single-stage planetary gear mechanism, the first planetary gear mechanism and the second planetary gear mechanism The other of the planetary gear mechanisms is a two-stage planetary gear mechanism.
  5. 根据权利要求1-4中任一项所述的变速器，其特征在于，所述变速器挂入第一挡，所述第一同步器将所述第一齿圈与所述变速器的壳体固定，且所述第二同步器将所述第二行星架与所述变速器的壳体固定。The transmission according to any one of claims 1-4, wherein the transmission is engaged in a first gear, and the first synchronizer fixes the first ring gear to a housing of the transmission, And the second synchronizer fixes the second planet carrier to the casing of the transmission.
  6. 根据权利要求1-5中任一项所述的变速器，其特征在于，所述变速器挂入第二挡，所述第一同步器将所述第一齿圈与所述变速器的壳体固定，且所述第二同步器将所述第一行星架与所述第二行星架连接。The transmission according to any one of claims 1-5, wherein the transmission is engaged in a second gear, and the first synchronizer fixes the first ring gear to a housing of the transmission, And the second synchronizer connects the first planet carrier with the second planet carrier.
  7. 根据权利要求1-6中任一项所述的变速器，其特征在于，所述变速器挂入第三挡，所述第一同步器将所述第一太阳轮与所述第一齿圈连接，且第二同步器将所述第二行星架与所述变速器的壳体固定。The transmission according to any one of claims 1-6, wherein the transmission is engaged in a third gear, and the first synchronizer connects the first sun gear with the first ring gear, And a second synchronizer fixes the second planet carrier to the casing of the transmission.
  8. 根据权利要求1-7中任一项所述的变速器，其特征在于，所述变速器挂入第四挡，所述第一同步器将所述第一太阳轮与所述第一齿圈连接，且第二同步器将所述第一行星架与所述第二行星架连接。The transmission according to any one of claims 1-7, wherein the transmission is engaged in a fourth gear, and the first synchronizer connects the first sun gear with the first ring gear, And a second synchronizer connects the first planet carrier with the second planet carrier.
  9. 一种动力传动***，其特征在于，包括：A power transmission system, comprising:
    驱动电机；motor;
    如权利要求1-8中任一项所述的变速器，所述驱动电机与所述输入轴动力耦合连接。The transmission according to any one of claims 1-8, wherein the drive motor is dynamically coupled to the input shaft.
  10. 一种车辆，其特征在于，包括：如权利要求9所述的动力传动***。A vehicle, comprising: the power transmission system according to claim 9.
PCT/CN2019/093561 2018-06-29 2019-06-28 Transmission, power drive system and vehicle WO2020001589A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201810713252.7 2018-06-29
CN201810713252.7A CN110657201B (en) 2018-06-29 2018-06-29 Transmission, power driving system and vehicle

Publications (1)

Publication Number Publication Date
WO2020001589A1 true WO2020001589A1 (en) 2020-01-02

Family

ID=68985808

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2019/093561 WO2020001589A1 (en) 2018-06-29 2019-06-28 Transmission, power drive system and vehicle

Country Status (2)

Country Link
CN (1) CN110657201B (en)
WO (1) WO2020001589A1 (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120593A (en) * 2020-01-23 2020-05-08 广州市新域动力技术有限公司 Pure electric double-gear planetary row driving system
CN112810435A (en) * 2020-07-19 2021-05-18 清研华科新能源研究院(南京)有限公司 Coaxial electric drive axle based on tower planet row
CN113650488A (en) * 2021-08-20 2021-11-16 北方汤臣传动科技有限公司 Transmission system with double-motor power coupling function
CN114017475A (en) * 2021-11-10 2022-02-08 一汽解放汽车有限公司 Speed change device, transmission and vehicle
CN115214337A (en) * 2022-06-09 2022-10-21 一汽解放汽车有限公司 Hybrid power system
CN115366655A (en) * 2022-09-26 2022-11-22 浙江吉利控股集团有限公司 Multi-stage transmission, power drive system and vehicle

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112744038A (en) * 2021-01-28 2021-05-04 江西科技学院 Flying automobile driving system and flying automobile
CN113232501B (en) * 2021-05-12 2022-12-27 东风汽车集团股份有限公司 Hybrid power driving system

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN102777555A (en) * 2012-08-13 2012-11-14 山东常林机械集团股份有限公司 Continuous power infinitely variable speed transmission mechanism
US8777789B2 (en) * 2012-01-04 2014-07-15 Zf Friedrichshafen Ag Split axis transmission hybrid system architecture
CN105402334A (en) * 2015-12-21 2016-03-16 江苏大学 Four-gear mechanical automatic transmission power assembly system based on planetary gear mechanisms
CN106183780A (en) * 2016-08-30 2016-12-07 上海交通大学 The coaxial coupling drive system of dual planetary gear system bi-motor
CN106402291A (en) * 2016-12-07 2017-02-15 天津天海同步集团有限公司 Compact type dual-motor power coupling transmission
CN106476607A (en) * 2015-08-31 2017-03-08 比亚迪股份有限公司 Power drive system and the vehicle with it
WO2017076567A1 (en) * 2015-11-03 2017-05-11 Zf Friedrichshafen Ag Method for synchronising the layshaft speed in the direct gear

Family Cites Families (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1252557A (en) * 1969-03-20 1971-11-10
KR100302749B1 (en) * 1995-11-23 2001-12-28 이계안 Power train of automatic transmission for vehicle
CN201651191U (en) * 2010-02-11 2010-11-24 哈尔滨东安汽车发动机制造有限公司 Automatic transmission planetary mechanism
CN202017736U (en) * 2011-04-27 2011-10-26 北京理工华创电动车技术有限公司 Planet gear type automatic speed change system for electric automobile
DE102011109352A1 (en) * 2011-08-03 2013-02-07 Volkswagen Aktiengesellschaft Hybrid drive system for a motor vehicle
EP2584220B1 (en) * 2011-10-20 2014-08-13 AIRBUS HELICOPTERS DEUTSCHLAND GmbH Planetary gear for variable transmission
DE102011086061A1 (en) * 2011-11-10 2013-05-16 Zf Friedrichshafen Ag Transfer Case
DE202012101546U1 (en) * 2012-04-25 2013-07-26 Caterpillar Global Mining Europe Gmbh Transmission in particular for drive systems of construction equipment and mining machines
CN202901186U (en) * 2012-10-30 2013-04-24 顺德职业技术学院 Planet gear type manual transmission
CN103953698B (en) * 2014-04-30 2016-08-03 北京航空航天大学 A kind of electrically driven (operated) planetary transmission
CN105299155B (en) * 2015-11-20 2019-12-31 昆山德拉特兰传动科技有限公司 Modular transmission
CN106808996B (en) * 2015-11-27 2021-02-23 长城汽车股份有限公司 Hybrid power drive system
CN106915239B (en) * 2015-12-25 2020-06-19 比亚迪股份有限公司 Power driving system and vehicle with same
CN106915244A (en) * 2015-12-25 2017-07-04 比亚迪股份有限公司 Power-driven system and the vehicle with the power-driven system
CN106915236A (en) * 2015-12-25 2017-07-04 比亚迪股份有限公司 Power-driven system and the vehicle with the power-driven system
CN105570419A (en) * 2016-01-22 2016-05-11 吉林大学 Electric driving device based on double-planet-row two-gear transmission
DE102016207482A1 (en) * 2016-05-02 2017-11-02 Zf Friedrichshafen Ag Transmission for a motor vehicle
CN107448561B (en) * 2017-09-04 2019-08-30 杭州前进齿轮箱集团股份有限公司 A kind of two grades of high speed difference speed changers

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8777789B2 (en) * 2012-01-04 2014-07-15 Zf Friedrichshafen Ag Split axis transmission hybrid system architecture
CN102777555A (en) * 2012-08-13 2012-11-14 山东常林机械集团股份有限公司 Continuous power infinitely variable speed transmission mechanism
CN106476607A (en) * 2015-08-31 2017-03-08 比亚迪股份有限公司 Power drive system and the vehicle with it
WO2017076567A1 (en) * 2015-11-03 2017-05-11 Zf Friedrichshafen Ag Method for synchronising the layshaft speed in the direct gear
CN105402334A (en) * 2015-12-21 2016-03-16 江苏大学 Four-gear mechanical automatic transmission power assembly system based on planetary gear mechanisms
CN106183780A (en) * 2016-08-30 2016-12-07 上海交通大学 The coaxial coupling drive system of dual planetary gear system bi-motor
CN106402291A (en) * 2016-12-07 2017-02-15 天津天海同步集团有限公司 Compact type dual-motor power coupling transmission

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111120593A (en) * 2020-01-23 2020-05-08 广州市新域动力技术有限公司 Pure electric double-gear planetary row driving system
CN112810435A (en) * 2020-07-19 2021-05-18 清研华科新能源研究院(南京)有限公司 Coaxial electric drive axle based on tower planet row
CN113650488A (en) * 2021-08-20 2021-11-16 北方汤臣传动科技有限公司 Transmission system with double-motor power coupling function
CN113650488B (en) * 2021-08-20 2023-11-21 北方汤臣传动科技有限公司 Transmission system with double-motor power coupling function
CN114017475A (en) * 2021-11-10 2022-02-08 一汽解放汽车有限公司 Speed change device, transmission and vehicle
CN114017475B (en) * 2021-11-10 2023-11-21 一汽解放汽车有限公司 Speed change device, speed changer and vehicle
CN115214337A (en) * 2022-06-09 2022-10-21 一汽解放汽车有限公司 Hybrid power system
CN115214337B (en) * 2022-06-09 2024-06-04 一汽解放汽车有限公司 Hybrid power system
CN115366655A (en) * 2022-09-26 2022-11-22 浙江吉利控股集团有限公司 Multi-stage transmission, power drive system and vehicle
CN115366655B (en) * 2022-09-26 2023-06-27 浙江吉利控股集团有限公司 Multi-speed transmission, power drive system and vehicle

Also Published As

Publication number Publication date
CN110657201A (en) 2020-01-07
CN110657201B (en) 2022-03-18

Similar Documents

Publication Publication Date Title
WO2020001589A1 (en) Transmission, power drive system and vehicle
WO2020001588A1 (en) Transmission, power drive system, and vehicle
US9114699B2 (en) Hybrid drive apparatus
JP3991970B2 (en) Hybrid vehicle drive system
CN108248362B (en) Four keep off single motor hybrid assembly
CN209164506U (en) Speed changer, power drive system and vehicle
CN110822034A (en) Nine-gear automatic transmission
US9441710B2 (en) Multi-speed gearbox
WO2019233329A1 (en) Electric drive powertrain having vertically-positioned multi-stage gearboxes
CN110962570B (en) Hybrid power driving system and vehicle
CN110657204B (en) Transmission, power driving system and vehicle
WO2023010714A1 (en) Dual-electric-motor and multi-gear hybrid power transmission system and vehicle
CN110657200B (en) Transmission, power driving system and vehicle
CN110657208B (en) Transmission, power driving system and vehicle
CN110657206B (en) Transmission, power driving system and vehicle
CN111376715A (en) Electrically-driven speed reducer, electrically-driven axle power assembly and vehicle
CN110657202B (en) Transmission, power driving system and vehicle
CN108274987B (en) Double-planet-row power coupling driving system
CN114382845B (en) Double-row speed change mechanism and power assembly
CN110657205B (en) Transmission, power driving system and vehicle
US11926311B2 (en) Hybrid driving system and hybrid electric vehicle
CN209795160U (en) hybrid power driving system and hybrid power automobile
US20180222306A1 (en) Power train for driving a motor vehicle with a variable-speed transmission device having a triple planetary gear set and especially a power train for a hybrid-type vehicle
CN110657207B (en) Transmission, power driving system and vehicle
CN216033750U (en) Electrically driven power transmission device

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 19824572

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 19824572

Country of ref document: EP

Kind code of ref document: A1