WO2019153150A1 - 一种多档ev动力装置 - Google Patents

一种多档ev动力装置 Download PDF

Info

Publication number
WO2019153150A1
WO2019153150A1 PCT/CN2018/075648 CN2018075648W WO2019153150A1 WO 2019153150 A1 WO2019153150 A1 WO 2019153150A1 CN 2018075648 W CN2018075648 W CN 2018075648W WO 2019153150 A1 WO2019153150 A1 WO 2019153150A1
Authority
WO
WIPO (PCT)
Prior art keywords
power
gear
motor
tail end
wheel
Prior art date
Application number
PCT/CN2018/075648
Other languages
English (en)
French (fr)
Inventor
刘身谦
刘李州
Original Assignee
深圳市万维博新能源技术有限公司
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 深圳市万维博新能源技术有限公司 filed Critical 深圳市万维博新能源技术有限公司
Priority to PCT/CN2018/075648 priority Critical patent/WO2019153150A1/zh
Publication of WO2019153150A1 publication Critical patent/WO2019153150A1/zh

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • B60K1/02—Arrangement or mounting of electrical propulsion units comprising more than one electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/72—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion with a secondary drive, e.g. regulating motor, in order to vary speed continuously
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H57/00—General details of gearing
    • F16H57/08—General details of gearing of gearings with members having orbital motion

Definitions

  • the invention relates to the field of power control technology, in particular to a multi-speed EV power device.
  • Electric Vehicle is equipped with a motor and battery instead of an engine, a car charger, a battery, a control device, etc., and uses a rechargeable battery instead of a gasoline-powered car because of its energy saving, light weight, low cost, and the like.
  • the advantages have been widely concerned and popularized.
  • the power control device of an electric vehicle is mainly composed of a power motor, a shifting motor and a transmission.
  • the powertrain is adjusted and transformed by the combination of the transmission and the shifting motor group.
  • the output can realize the shifting function of the vehicle.
  • the power control device of the existing electric vehicle still has the following drawbacks: 1.
  • a single differential gear ie, a differential
  • a single planetary gearbox as a transmission, by controlling the output power of the power motor and The shifting motor controls the transmission ratio of the transmission to realize the shifting shift.
  • the shifting motor can only play the role of gear shifting, and cannot be powered. The function sharing of the motor increases the configuration cost of the device and increases the structural complexity of the device. 3.
  • the gear ratio is relatively close, it is not convenient to divide the output speed of the device into multiples. The high and low gear positions of the gears weaken the power output mode of the device.
  • a multi-speed EV power unit includes a first motor unit, a second motor unit, a gear shifting device, and a power output device;
  • the gear shifting device includes:
  • a planet carrier having a first end cavity and a tail end cavity coaxially distributed along a central axis of the planet carrier, and a tail end of the planet carrier being connected to an output shaft of the second motor group;
  • the power center axle is distributed through the planet carrier along a central axis of the planet carrier, and a head end of the power center axle is coupled to an output shaft of the first motor group;
  • An outer sun wheel the outer sun wheel is sleeved on the power center axle and located in the head end cavity, and the first end face of the outer sun wheel is formed around the power center axle to have a distribution and power running through the first end of the planet carrier a power output bushing connected to the output device;
  • An inner sun wheel disposed on the power center axle and located in the tail end cavity;
  • a plurality of outer planet wheels a plurality of the outer planet wheels are mounted on the planet carrier in an axial direction of the planet carrier and evenly distributed around the outer sun gear, and the leading end portion of the outer planet gear meshes with the outer sun gear ;
  • An inner planetary wheel is disposed in the planetary support in the axial direction of the planetary support and located in the tail end cavity, and an inner planetary wheel is disposed between each of the outer planetary wheel and the inner sun gear Each of the inner planet wheels simultaneously meshes with the inner end of the inner sun gear and the corresponding outer planet gear.
  • the planetary bracket comprises a head end ring portion, a tail end disk portion integrally connected to the head end ring portion through a plurality of axial support arm portions and having a center shaft hole, and a ring end portion and a tail end disposed at the head end portion Separating the space between the disc portion and the end end ring portion and the tail end disc portion into an inner partition ring portion of the head end chamber and the tail end chamber, and a plurality of inner spacer ring portions and the axial support arm portion are integrally connected Radial support arm;
  • the power output bushing is inserted through the front end ring portion, the tail end of the power center axle is distributed through the central shaft hole, and the outer planet wheel is disposed between the head end ring portion and the tail end disk portion, The inner planet gear is disposed between the inner spacer ring portion and the tail end disk portion; and the output shaft of the second motor group is coupled to the tail end disk portion.
  • the central shaft hole is provided with a first bearing disposed on the central power wheel axle, and a second bearing is disposed between the inner spacer ring portion and the central power wheel axle and between the outer sun gear and the central power wheel axle. .
  • the first motor group includes a first motor, a first front shift gear mounted on an output shaft of the first motor, and a parallel distribution with the first front shift gear and a first forward shift a first rear-stage shifting gear that meshes with the gear, the first rear-stage shifting gear set is fixed to a front end of the central power axle;
  • the second motor unit includes a second motor, a second front shift gear mounted on the output shaft of the second motor, and a second front shift gear coupled to the second forward shift gear
  • the second rear stage shifting gear is coaxially distributed with the planet carrier and fixed to the tail end of the planet carrier.
  • the power output device includes a power output gear that is sleeved and fixed to the power output bushing, and a differential that is distributed in parallel with the power output gear and meshes with the power output gear.
  • auxiliary power output device is a gear that meshes with the second rear stage gear.
  • a brake or a one-way bearing is further mounted on the output shaft of the first motor and/or on the output shaft of the second motor.
  • the invention has the following beneficial effects: a, multi-position distribution is uniform, covering multiple power output modes such as low speed, medium speed, high speed and over speed, which can meet different application requirements; b, can pass two pairs The motor groups are logically combined to realize the multi-speed shifting function, and the two motors can perform role conversion between the power motor, the shifting motor and the generator motor, which greatly improves the utilization of the motor resources and helps to reduce the total total.
  • the structure of the optimized gear shifting device and the power input mode of the dual motor not only ensure the transmission and conversion effects of the input power of the motor, but also reduce the impact force and noise during the shifting process. And can also avoid power interruptions.
  • Figure 1 is a schematic view of the assembly of the overall structure of the embodiment of the present invention (1);
  • Figure 2 is a schematic view showing the assembly of the overall structure of the embodiment of the present invention (2);
  • FIG. 3 is a schematic exploded view showing the structure of a main body member according to an embodiment of the present invention.
  • FIG. 4 is a schematic exploded view showing the structure of a gear shifting device according to an embodiment of the present invention.
  • Figure 5 is a schematic axial sectional view showing the gear shifting device of the embodiment of the present invention.
  • Fig. 6 is a schematic structural view of a planetary carrier according to an embodiment of the present invention.
  • the present invention provides a multi-speed EV power unit including a first motor unit, a second motor unit, a gear shifting device, and a power output device.
  • the gear shifting device includes:
  • a planet carrier 10 having a head end cavity a and a tail end cavity b coaxially distributed along the central axis thereof, and the tail end of the planet carrier 10 is connected to the output shaft of the second motor unit (eg, gear transmission connection, belt drive connection) and many more);
  • the second motor unit eg, gear transmission connection, belt drive connection
  • a power center axle 20 that is distributed along the central axis of the planet carrier 10 through the planet carrier 10 (wherein the penetration is understood to be a structural relationship that passes through and has a relative rotation with the planet carrier) and is powered
  • the head end of the center axle 20 is connected to the output shaft of the first motor unit (such as a gear transmission connection, a belt drive connection, etc.);
  • An outer sun gear 30 is sleeved on the power center axle 20 and located in the head end cavity a (wherein the socket is understood to be that the power center axle 20 is distributed through the outer sun gear 30 and has a relative rotation therewith.
  • the first end of the outer sun gear 30 is formed around the power center axle 20 with a distribution extending through the head end of the planet carrier 10 (wherein the penetration is understood to be through and through the planet carrier).
  • a power output bushing 40 having a relatively rotating structural relationship and connected to the power output device;
  • An inner sun gear 50 is disposed on the power center axle 20 and located in the tail end cavity b (the arrangement is understood to be fixed to the power center axle 20 in the form of a kit or integrally formed with the power center axle 20 In order to maintain the relationship between the two with synchronous rotation);
  • a plurality of (eg, three) outer planet gears 60 are mounted on the planet carrier 10 in the axial direction of the planet carrier 10 and evenly distributed around the outer sun gear 30 (ie, equivalent to simultaneously encircling the inner sun) The wheel 40 is evenly distributed), and the leading end of the outer planet gear 60 meshes with the outer sun gear 30;
  • an inner planet gear 70 which is disposed in the planetary support 10 in the axial direction of the planetary carrier 10 and located in the tail end cavity b, and an inner space between each outer planetary gear 60 and the inner sun gear 50 is disposed therein.
  • two motors can be disposed at the same time, thereby forming a power control structure of the dual motor, that is, when the first motor group and the second motor group are simultaneously connected with the gear shifting device,
  • the two motor groups can be used simultaneously or independently for logical control, so that the entire assembly can not only output multiple modes of power, but also control the motor group by positive and negative rotation, stop, etc. It can be used as a shifting motor or generator motor at the same time to maximize the utilization of motor resources.
  • the gear shifting device has multiple gear ratios and can provide a structural basis for fast switching between motors, it is beneficial to ensure the motor. Run more efficiently in the work area.
  • the first motor group inputs power to the gear shifting device through the power center axle 20, thereby driving the inner sun gear 50 to rotate, and since the inner sun gear 50 passes through
  • the planetary gear 70 is in meshing engagement with the outer planetary gear 60, and the outer sun gear 30 is rotated by the meshing relationship between the outer planetary gear 60 and the outer sun gear 30; at the same time, the second motor unit passes the planetary carrier 10 to the gear The shifting device inputs power. Since the outer planetary gear 60 is mounted on the planetary carrier 10, the outer planetary gear 60 also rotates synchronously, so that the outer sun is utilized by the meshing relationship between the outer planetary gear 60 and the outer sun gear 30.
  • the wheel 30 is rotated to form a dual power superposition effect (i.e., acceleration mode); as an example, a shifting mode such as that shown in Table 1 can be formed by logical control of different motor groups:
  • the first motor group and the second motor group can also be used as a shift motor while being used as a power motor.
  • the first motor group passes through the power center axle 20, the inner sun gear 50, the inner planet gear 70, and the outer planet gear 60.
  • the linkage action to drive the outer sun gear 60 to achieve the power output, and the structural relationship between the outer planet gear 60 and the planet carrier 10 can also drive the planet carrier 10 to operate, thereby using the planet carrier 10 as the second motor group.
  • the power input component can further use the second motor group as a generator motor; conversely, the second motor group can be used as a power generator motor as the power input motor of the entire assembly and the first motor group.
  • the control assembly of the embodiment can achieve the following beneficial effects: a, multiple gear positions are evenly distributed, covering multiple power output modes such as low speed, medium speed, high speed and over speed, which can meet different application requirements; b.
  • the multi-speed shifting function is realized by logically combining two motor groups, and the two motors can perform role conversion between the power motor, the shifting motor and the generator motor, which greatly improves the utilization of the motor resources, which is beneficial to Reduce the configuration cost and structural complexity of the entire assembly;
  • the structure of the optimized gear shifting device and the power input mode of the dual motor can not only ensure the transmission and conversion effects of the input power of the motor, but also reduce the impact during the shifting process. Force and noise, but also avoid power interruption.
  • the planetary carrier 10 of the present embodiment includes a head end ring portion 11 and is integrally connected to the head end ring portion 11 through a plurality of axial support arm portions 12 and has a tail end disk portion 13 of a center shaft hole c is disposed between the head end ring portion 11 and the tail end disk portion 13 and partitions a space between the head end ring portion 11 and the tail end disk portion 13 into a head end cavity a and An inner spacer ring portion 14 of the tail end cavity b and a plurality of radial support arm portions 15 integrally connecting the inner spacer ring portion 14 and the axial support arm portion 12; wherein the power output bushing 40 penetrates through the head end ring portion 11 distribution, the tail end of the power center axle 20 is distributed through the central shaft hole c, the outer planet gear 60 is disposed between the head end ring portion 11 and the tail end disk portion 13, and the inner planet gear 70 is mounted on the inner ring
  • the power output bushing 40 penetrates through the head end ring portion 11 distribution, the tail end
  • a first bearing 80 fitted to the central power wheel axle 20 is mounted in the central shaft hole c, and between the inner spacer ring portion 14 and the central power wheel axle 20, and A second bearing 90 is disposed between the sun gear 30 and the center power axle 20 .
  • a first bearing 80 fitted to the central power wheel axle 20 is mounted in the central shaft hole c, and between the inner spacer ring portion 14 and the central power wheel axle 20, and A second bearing 90 is disposed between the sun gear 30 and the center power axle 20 .
  • the first motor unit of the embodiment includes a first motor 101 and a first motor 101. a first front stage shifting gear 102 on the output shaft and a first rear stage shifting gear 103 distributed in parallel with the first front stage shifting gear 102 and meshing with the first front stage shifting gear 102, wherein the first rear stage shifting gear
  • the gear 103 is assembled and fixed to the first end of the central power axle 20;
  • the second motor unit of the present embodiment includes a second motor 201 and a second front mounted on the output shaft of the second motor 201.
  • the shaft is distributed and fixed to the trailing end of the planet carrier 10. Therefore, by using the structural matching of each motor group, the wheel body diameter of the front shift gear can be smaller than the wheel diameter of the rear shift gear, so that the power outputted by the motor can be power-driven by first decelerating in the transmission shift mode.
  • the sun gear, the planetary gear, and the aforementioned shifting gear can be used as helical gears, thereby utilizing the multi-spec gear combination to exert the power output effect of the assembly.
  • the power output apparatus of the present embodiment includes a power output gear 301 that is set and fixed to the power output bushing 40, and is distributed in parallel with the power output gear 301 and is coupled to the power output gear 301.
  • the assembly of the embodiment further includes an auxiliary power output device 400 which is a gear that meshes with the second rear stage shifting gear 203 (preferably, it can adopt a helical tooth that meshes with the shifting gear) gear).
  • a brake d is further disposed on the output shaft of the first motor 101 and/or the output shaft of the second motor 201.
  • a one-way bearing is further disposed on the output shaft of the first motor 101 and/or the output shaft of the second motor 201.

Landscapes

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

Abstract

一种多档EV动力装置，包括主要由尾端内装设有内太阳轮（50）且首端内装设有外太阳轮（30）的行星支架（10）、贯穿于行星支架（10）分布并与内太阳轮（50）相连的动力中心轮轴（20）、装设于行星支架（10）上且首端与外太阳轮（30）相啮合的外行星轮（60）、装设于行星支架（10）内并同时与内太阳轮（50）及外行星轮（60）的尾端相啮合的内行星轮（70）构成的齿轮变速装置以及连接动力中心轮轴（20）的首端的第一电机组、连接行星支架（10）的尾端的第二电机组，与形成于外太阳轮（30）上的动力输出轴套（40）相连的动力输出装置。所述多档EV动力装置利用配置的两个电机组进行动力输入，而电机组则可根据逻辑控制需求起到动力电机、换挡电机乃至发电电机的作用，不但有利于实现电机资源运用的最大化，而且极大地丰富了动力输出模式的多样性。

Description

一种多档EV动力装置 技术领域
本发明涉及动力控制技术领域，尤其是一种多档EV动力装置。
背景技术
电动汽车(Electric Vehicle)是装备有代替了发动机的电动机和电池、车载充电器、蓄电池、控制装置等并用充电电池的电力代替汽油驱动的汽车，因其具有节能环保、轻便、费用较低等诸多优点而受到了广泛的关注和推广；周知，电动汽车的动力控制装置主要由动力电机、换挡电机和变速器组合而成，其利用变速器与换挡电机组的配合将动力电机的动力进行调整变换输出即可实现车辆的换挡变速功能。然而，现有的电动汽车的动力控制装置依然存在如下缺陷：1、采用单一的差速齿轮(即：差速器)或单一的行星齿轮箱作为变速器，通过对动力电机的输出功率的控制以及换挡电机对变速器的传动比的切换控制来实现变速换挡，但当采用差速齿轮作为变速器时，其不但噪音大，而且变速换挡的过程中会产生明显的冲击力或动力中断的问题；而采用单一的行星齿轮箱作为变速器时，不但输出的转速过高，而且动力电机的高效率工作区往往较窄；2、换挡电机往往只能起到档位切换的作用，无法与动力电机进行功能共享，从而提高了装置的配置成本、增加了装置的结构复杂性；3、采用行星系齿轮箱作为变速器时，由于变速比相对比较接近，不便于将装置输出的转速均分为多档高低速档位，从而弱化了装置的动力输出模式。
发明内容
针对上述现有技术存在的不足，本发明的目的在于提供一种多档EV动力装置。
为了实现上述目的，本发明采用如下技术方案：
一种多档EV动力装置，它包括第一电机组、第二电机组、齿轮变速装置和动力输出装置；所述齿轮变速装置包括：
一行星支架，所述行星支架的内部具有沿行星支架的中轴线同轴分布的首端腔和尾端腔，且所述行星支架的尾端与第二电机组的输出轴相连；
一动力中心轮轴，所述动力中心轮轴沿行星支架的中轴线贯穿于行星支架分布，且所述动力中心轮轴的首端与第一电机组的输出轴相连；
一外太阳轮，所述外太阳轮套接于动力中心轮轴上并位于首端腔内，且所述外太阳轮的首端面环绕动力中心轮轴形成有一贯穿于行星支架的首端分布并与动力输出装置相连的动力输出轴套；
一内太阳轮，所述内太阳轮设置于动力中心轮轴上并位于尾端腔内；
若干个外行星轮，若干个所述外行星轮沿行星支架的轴向方向装设于行星支架上并环绕外太阳轮均匀分布，且所述外行星轮的首端部与外太阳轮相啮合；
一内行星轮，所述内行星轮沿行星支架的轴向方向装设于行星支架内并位于尾端腔内，每个所述外行星轮与内太阳轮之间均设置有一个内行星轮，每个所述内行星轮均同时与内太阳轮及相对应的外行星轮的尾端部相啮合。
优选地，所述行星支架包括首端环部、通过若干个轴向支撑臂部与首端环部连为一体且具有一中心轴孔的尾端盘部、设置于首端环部与尾端盘部之间并将首端环部与尾端盘部之间的空间分隔为首端腔和尾端腔的内隔环部以及若干个将内隔环部与轴向支撑臂部连为一体的径向支撑臂部；
所述动力输出轴套贯穿于首端环部分布，所述动力中心轮轴的尾端贯穿中心轴孔分布，所述外行星轮装设于首端环部与尾端盘部之间，所述内行星轮装设于内隔环部与尾端盘部之间；且所述第二电机组的输出轴与尾端盘部相连。
优选地，所述中心轴孔内装设有一套装于中心动力轮轴上的第一轴承，所述内隔环部与中心动力轮轴之间以及外太阳轮与中心动力轮轴之间均设置有第二轴承。
优选地，所述第一电机组包括第一电机、一装设于第一电机的输出轴上的第一前级变速齿轮以及一与第一前级变速齿轮并行分布并与第一前级变速齿轮相啮合的第一后级变速齿轮，所述第一后级变速齿轮套装并固定于中心动力轮轴的首端；
所述第二电机组包括第二电机、一装设于第二电机的输出轴上的第二前级变速齿轮以及一与第二前级变速齿轮并行分布并与第二前级变速齿轮相啮合的第二后级变速齿轮，所述第二后级变速齿轮与行星支架同轴分布并固定于行星支架的尾端。
优选地，所述动力输出装置包括一套装并固定于动力输出轴套上的动力输出齿轮以及一与动力输出齿轮并行分布并与动力输出齿轮相啮合的差速器。
优选地，它还包括一辅助动力输出装置，所述辅助动力输出装置为一与第二后级变速齿轮相啮合的齿轮。
优选地，所述第一电机的输出轴上和/或第二电机的输出轴上还装设有一制动器或一单向轴承。
由于采用了上述方案，本发明具有以下有益效果：a、多档位分配均匀，覆盖低速、中速、高速和超速等多种动力输出模式，能够满足不同的应用需求；b、可通过对两个电机组进行逻辑组合来实现多档变速功能的，且两个电机可在动力电机、换挡电机及发电电机之间进行角色转换，极大地提高了电机资源的利用率，有利于降低整个总成的配置成本及结构复杂性；c、通过优化的齿轮变速装置的结构以及双电机的动力输入模式不但可保证对电机输入 动力的传递、转换效果，减小换挡过程中的冲击力及噪音，而且也可避免动力中断。
附图说明
图1是本发明实施例的整体结构装配示意图(一)；
图2是本发明实施例的整体结构装配示意图(二)；
图3是本发明实施例的主体部件的结构分解示意图；
图4是本发明实施例的齿轮变速装置的结构分解示意图；
图5是本发明实施例的齿轮变速装置的轴向截面结构示意图；
图6是本发明实施例的行星支架的结构示意图。
具体实施方式
以下结合附图对本发明的实施例进行详细说明，但是本发明可以由权利要求限定和覆盖的多种不同方式实施。
如图1至图6所示，本实施例提供的一种多档EV动力装置，它包括第一电机组、第二电机组、齿轮变速装置和动力输出装置；其中，齿轮变速装置包括：
一行星支架10，其内部具有沿其中轴线同轴分布的首端腔a和尾端腔b，并且行星支架10的尾端与第二电机组的输出轴相连(如齿轮传动连接、皮带传动连接等等)；
一动力中心轮轴20，其沿行星支架10的中轴线贯穿于行星支架10分布(其中，所述及的贯穿可以理解为是穿设而过并与行星支架具有相对转动的结构关系)，并且动力中心轮轴20的首端与第一电机组的输出轴相连(如齿轮传动连接、皮带传动连接等等)；
一外太阳轮30，其套接于动力中心轮轴20上并位于首端腔a内(其中，所述及的套接可以理解为是动力中心轮轴20贯穿外太阳轮30分布并与其具 有相对转动的结构关系)，同时，在外太阳轮30的首端面环绕动力中心轮轴20形成有一贯穿于行星支架10的首端分布(其中，所述及的贯穿可以理解为是穿设而过并与行星支架具有相对转动的结构关系)并与动力输出装置相连的动力输出轴套40；
一内太阳轮50，其设置于动力中心轮轴20上并位于尾端腔b内(所述及的设置可以理解为是以套装的形式固定于动力中心轮轴20上或者与动力中心轮轴20一体成型以保持两者具有同步转动的关系)；
若干个(如三个)外行星轮60，若干个外行星轮60沿行星支架10的轴向方向装设于行星支架10上并环绕外太阳轮30均匀分布(即：相当于同时环绕内太阳轮40均匀分布)，并且外行星轮60的首端部与外太阳轮30相啮合；
和一内行星轮70，其沿行星支架10的轴向方向装设于行星支架10内并位于尾端腔b内，而每个外行星轮60与内太阳轮50之间均设置有一个内行星轮70，并且每个内行星轮70均同时与内太阳轮50及相对应的外行星轮30的尾端部相啮合。
由此，通过对齿轮变速装置的结构改进可同时与其配置两个电机，从而形成双电机的动力控制结构，即第一电机组与第二电机组同时与齿轮变速装置产生连接关系的情况下，可根据需要对两个电机组同时进行使用或独立分开使用进行逻辑控制，使得整个总成不但能够输出多种模式的动力，而且通过对电机组的正反转、停止等控制转换亦可电机组能够同时作为换挡电机或发电电机来使用，以此实现电机资源运用的最大化；同时，由于齿轮变速装置具有多种变速比并且能够为电机之间的快速切换提供结构基础，有利于保证电机更多地运行在工作高效区。具体如：1、当两个电机组进行同向转动时，第一电机组通过动力中心轮轴20向齿轮变速装置输入动力，从而带动内太阳轮50进行转动，而由于内太阳轮50是通过内行星轮70与外行星轮60过渡啮合的，进而利用外行星轮60与外太阳轮30之间的啮合关系使外太阳轮30 进行转动；与此同时，第二电机组通过行星支架10向齿轮变速装置输入动力，由于外行星轮60是装设于行星支架10上的，故外行星轮60亦会进行同步转动，从而利用外行星轮60与外太阳轮30之间的啮合关系使外太阳轮30进行转动，从而形成双动力的叠加效果(即：加速模式)；以此为例，通过对不同电机组的逻辑控制可形成诸如表一所示的变速模式：
Figure PCTCN2018075648-appb-000001
而通过表一所示的变速模式可知，第一电机组和第二电机组在可被用作动力电机使用的同时亦可作为换挡电机来使用。
2、以第一电机组处于动力输入状态、第二电机组并未进行动力输入时为例，第一电机组在通过动力中心轮轴20、内太阳轮50、内行星轮70和外行星轮60的联动动作来驱动外太阳轮60实现动力输出的同时，由于外行星轮60与行星支架10之间的结构关系亦可带动行星支架10进行动作，从而以行星支架10作为向第二电机组进行动力输入部件，进而可将第二电机组作为发电电机来使用；反之，第二电机组作为整个总成的动力输入电机、第一电机组则可作为发电电机来使用。
基于此，本实施例的控制总成可实现以下有益效果：a、多档位分配均匀，覆盖低速、中速、高速和超速等多种动力输出模式，能够满足不同的应用需求；b、可通过对两个电机组进行逻辑组合来实现多档变速功能的，且两个电机可在动力电机、换挡电机及发电电机之间进行角色转换，极大地提高了电 机资源的利用率，有利于降低整个总成的配置成本及结构复杂性；c、通过优化的齿轮变速装置的结构以及双电机的动力输入模式不但可保证对电机输入动力的传递、转换效果，减小换挡过程中的冲击力及噪音，而且也可避免动力中断。
为优化行星支架的结构以增强齿轮变速装置的结构紧凑性，本实施例的行星支架10包括首端环部11、通过若干个轴向支撑臂部12与首端环部11连为一体且具有一中心轴孔c的尾端盘部13、设置于首端环部11与尾端盘部13之间并将首端环部11与尾端盘部13之间的空间分隔为首端腔a和尾端腔b的内隔环部14以及若干个将内隔环部14与轴向支撑臂部12连为一体的径向支撑臂部15；其中，动力输出轴套40贯穿于首端环部11分布，动力中心轮轴20的尾端贯穿中心轴孔c分布，外行星轮60装设于首端环部11与尾端盘部13之间，而内行星轮70则装设于内隔环部14与尾端盘部13之间；同时，第二电机组的输出轴与尾端盘部13相连。
为保证相关组成部件之间相对运动的顺畅性，在中心轴孔c内装设有一套装于中心动力轮轴20上的第一轴承80，同时在内隔环部14与中心动力轮轴20之间以及外太阳轮30与中心动力轮轴20之间均设置有第二轴承90。当然，为便于将整个控制总成装配于车辆的安装载体上，可相应地在诸如中心动力轮轴20的两端、第一电机组的输出轴上或第二电机组的输出轴上装设相应的轴承。
为最大限度地发挥变速齿轮装置的优势，拉开高低速的变速比，以增强整个总成的性能，本实施例的第一电机组包括第一电机101、一装设于第一电机101的输出轴上的第一前级变速齿轮102以及一与第一前级变速齿轮102并行分布并与第一前级变速齿轮102相啮合的第一后级变速齿轮103，其中，第一后级变速齿轮103套装并固定于中心动力轮轴20的首端；基于同样的结构原理，本实施例的第二电机组包括第二电机201、一装设于第二电机201的输出轴上的第二前级变速齿轮202以及一与第二前级变速齿轮202并行分布 并与第二前级变速齿轮202相啮合的第二后级变速齿轮203，其中，第二后级变速齿轮203与行星支架10同轴分布并固定于行星支架10的尾端。由此，利用各电机组的结构搭配，可采用前级变速齿轮的轮体直径小于后级变速齿轮的轮体直径的方式，使得电机输出的动力能够以先减速在传动变速的方式进行动力输入，而在与具体的齿轮变速装置时，可将太阳轮、行星轮以及前述的变速齿轮均采用斜齿齿轮，从而通过对多规格齿轮组合混用来发挥总成的动力输出效果。
为实现对动力输出效果的最大化，本实施例的动力输出装置包括一套装并固定于动力输出轴套40上的动力输出齿轮301以及一与动力输出齿轮301并行分布并与动力输出齿轮301相啮合的差速器302。
作为一个优选方案，本实施例的总成还包括一辅助动力输出装置400，其为一与第二后级变速齿轮203相啮合的齿轮(作为优选，其可采用与变速齿轮相啮合的斜齿齿轮)。
另外，为增强对第一电机组和第二电机组的启闭及制动控制效果，在第一电机101的输出轴上和/或第二电机201的输出轴上还装设有一制动器d或一单向轴承。
以上所述仅为本发明的优选实施例，并非因此限制本发明的专利范围，凡是利用本发明说明书及附图内容所作的等效结构或等效流程变换，或直接或间接运用在其他相关的技术领域，均同理包括在本发明的专利保护范围内。

Claims (7)

  1. 一种多档EV动力装置，其特征在于：它包括第一电机组、第二电机组、齿轮变速装置和动力输出装置；所述齿轮变速装置包括：
    一行星支架，所述行星支架的内部具有沿行星支架的中轴线同轴分布的首端腔和尾端腔，且所述行星支架的尾端与第二电机组的输出轴相连；
    一动力中心轮轴，所述动力中心轮轴沿行星支架的中轴线贯穿于行星支架分布，且所述动力中心轮轴的首端与第一电机组的输出轴相连；
    一外太阳轮，所述外太阳轮套接于动力中心轮轴上并位于首端腔内，且所述外太阳轮的首端面环绕动力中心轮轴形成有一贯穿于行星支架的首端分布并与动力输出装置相连的动力输出轴套；
    一内太阳轮，所述内太阳轮设置于动力中心轮轴上并位于尾端腔内；
    若干个外行星轮，若干个所述外行星轮沿行星支架的轴向方向装设于行星支架上并环绕外太阳轮均匀分布，且所述外行星轮的首端部与外太阳轮相啮合；
    一内行星轮，所述内行星轮沿行星支架的轴向方向装设于行星支架内并位于尾端腔内，每个所述外行星轮与内太阳轮之间均设置有一个内行星轮，每个所述内行星轮均同时与内太阳轮及相对应的外行星轮的尾端部相啮合。
  2. 如权利要求1所述的一种多档EV动力装置，其特征在于：所述行星支架包括首端环部、通过若干个轴向支撑臂部与首端环部连为一体且具有一中心轴孔的尾端盘部、设置于首端环部与尾端盘部之间并将首端环部与尾端盘部之间的空间分隔为首端腔和尾端腔的内隔环部以及若干个将内隔环部与轴向支撑臂部连为一体的径向支撑臂部；
    所述动力输出轴套贯穿于首端环部分布，所述动力中心轮轴的尾端贯穿中心轴孔分布，所述外行星轮装设于首端环部与尾端盘部之间，所述内行星轮装设于内隔环部与尾端盘部之间；且所述第二电机组的输出轴与尾端盘部相连。
  3. 如权利要求2所述的一种多档EV动力装置，其特征在于：所述中心轴孔内装设有一套装于中心动力轮轴上的第一轴承，所述内隔环部与中心动力轮轴之间以及外太阳轮与中心动力轮轴之间均设置有第二轴承。
  4. 如权利要求1-3中任一项所述的一种多档EV动力装置，其特征在于：
    所述第一电机组包括第一电机、一装设于第一电机的输出轴上的第一前级变速齿轮以及一与第一前级变速齿轮并行分布并与第一前级变速齿轮相啮合的第一后级变速齿轮，所述第一后级变速齿轮套装并固定于中心动力轮轴的首端；
    所述第二电机组包括第二电机、一装设于第二电机的输出轴上的第二前级变速齿轮以及一与第二前级变速齿轮并行分布并与第二前级变速齿轮相啮合的第二后级变速齿轮，所述第二后级变速齿轮与行星支架同轴分布并固定于行星支架的尾端。
  5. 如权利要求4所述的一种多档EV动力装置，其特征在于：所述动力输出装置包括一套装并固定于动力输出轴套上的动力输出齿轮以及一与动力输出齿轮并行分布并与动力输出齿轮相啮合的差速器。
  6. 如权利要求5所述的一种多档EV动力装置，其特征在于：它还包括一辅助动力输出装置，所述辅助动力输出装置为一与第二后级变速齿轮相啮合的齿轮。
  7. 如权利要求4所述的一种多档EV动力装置，其特征在于：所述第一电机的输出轴上和/或第二电机的输出轴上还装设有一制动器或一单向轴承。
PCT/CN2018/075648 2018-02-07 2018-02-07 一种多档ev动力装置 WO2019153150A1 (zh)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CN2018/075648 WO2019153150A1 (zh) 2018-02-07 2018-02-07 一种多档ev动力装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2018/075648 WO2019153150A1 (zh) 2018-02-07 2018-02-07 一种多档ev动力装置

Publications (1)

Publication Number Publication Date
WO2019153150A1 true WO2019153150A1 (zh) 2019-08-15

Family

ID=67548708

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2018/075648 WO2019153150A1 (zh) 2018-02-07 2018-02-07 一种多档ev动力装置

Country Status (1)

Country Link
WO (1) WO2019153150A1 (zh)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060154771A1 (en) * 2005-01-11 2006-07-13 Donald Klemen Electrically variable transmission having six fixed speed ratios
US20160288779A1 (en) * 2015-02-17 2016-10-06 Oshkosh Corporation Multi-mode electromechanical variable transmission
CN106090149A (zh) * 2016-05-25 2016-11-09 广州市新域动力技术有限公司 双电机盘式无级变速动力***
CN206054710U (zh) * 2016-08-17 2017-03-29 广西科技大学 纯电动汽车双电机自动变速器控制***
CN206647505U (zh) * 2017-04-10 2017-11-17 深圳市万维博新能源技术有限公司 双太阳轮输入行星结构
US9840140B1 (en) * 2016-08-05 2017-12-12 GM Global Technology Operations LLC Compound-power-split electrically variable transmissions with motor clutching devices
CN108150637A (zh) * 2018-02-07 2018-06-12 深圳市万维博新能源技术有限公司 一种多档ev动力装置

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20060154771A1 (en) * 2005-01-11 2006-07-13 Donald Klemen Electrically variable transmission having six fixed speed ratios
US20160288779A1 (en) * 2015-02-17 2016-10-06 Oshkosh Corporation Multi-mode electromechanical variable transmission
CN106090149A (zh) * 2016-05-25 2016-11-09 广州市新域动力技术有限公司 双电机盘式无级变速动力***
US9840140B1 (en) * 2016-08-05 2017-12-12 GM Global Technology Operations LLC Compound-power-split electrically variable transmissions with motor clutching devices
CN206054710U (zh) * 2016-08-17 2017-03-29 广西科技大学 纯电动汽车双电机自动变速器控制***
CN206647505U (zh) * 2017-04-10 2017-11-17 深圳市万维博新能源技术有限公司 双太阳轮输入行星结构
CN108150637A (zh) * 2018-02-07 2018-06-12 深圳市万维博新能源技术有限公司 一种多档ev动力装置

Similar Documents

Publication Publication Date Title
WO2018177380A1 (zh) 动力***用混合动力、纯电动传动装置及操作方法
JP5784606B2 (ja) ハイブリッド電気車両用の動力伝達機構
WO2018137421A1 (zh) 一种横置双动力源车辆驱动总成
WO2013014777A1 (ja) ハイブリッド車両用駆動装置
CN103770625A (zh) 一种混合动力汽车双行星排式动力耦合机构
CN106627117B (zh) 一种用于纵置后驱混合动力车辆的传动装置
CN108150637B (zh) 一种多档ev动力装置
CN103978882B (zh) 混合动力车辆的动力传递装置
CN111731089A (zh) 两种适用于商用车的混联式油电混合动力驱动装置
CN113335079B (zh) 双电机驱动***及应用
CN110962572B (zh) 混合动力驱动***及车辆
CN109263460B (zh) 混合动力传动***、控制方法及汽车
CN107310366B (zh) 双电机高低速区复合双速驱动总成
CN106671767B (zh) 一种插电式混合动力汽车动力总成
WO2019153150A1 (zh) 一种多档ev动力装置
CN110843502A (zh) 机电耦合传动装置
CN108274987B (zh) 双行星排动力耦合驱动***
CN104165214B (zh) 一种双动力合成器
CN107719097B (zh) 一种混合动力***及应用
CN208057913U (zh) 一种多档ev动力装置
CN112440723B (zh) 混合动力装置和车辆
CN107640010B (zh) 一种单排双行星轮式电驱动总成
CN111114288A (zh) 行星轮同轴式双行星排混合动力***
CN106740045B (zh) 一种混合动力汽车驱动***
CN112728022A (zh) 一种电动汽车用双速变速器

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: 18905743

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: 18905743

Country of ref document: EP

Kind code of ref document: A1