WO2017185901A1 - 变速驱动桥及其双速驱动模块 - Google Patents

变速驱动桥及其双速驱动模块 Download PDF

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Publication number
WO2017185901A1
WO2017185901A1 PCT/CN2017/076938 CN2017076938W WO2017185901A1 WO 2017185901 A1 WO2017185901 A1 WO 2017185901A1 CN 2017076938 W CN2017076938 W CN 2017076938W WO 2017185901 A1 WO2017185901 A1 WO 2017185901A1
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WO
WIPO (PCT)
Prior art keywords
gear
gear set
drive module
shaft
speed
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Application number
PCT/CN2017/076938
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English (en)
French (fr)
Inventor
钟虎
陈鹏
Original Assignee
舍弗勒技术股份两合公司
钟虎
陈鹏
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.)
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Publication date
Application filed by 舍弗勒技术股份两合公司, 钟虎, 陈鹏 filed Critical 舍弗勒技术股份两合公司
Priority to DE112017002206.1T priority Critical patent/DE112017002206T5/de
Priority to US16/094,538 priority patent/US10808814B2/en
Publication of WO2017185901A1 publication Critical patent/WO2017185901A1/zh

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/06—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing
    • B60K17/08—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of change-speed gearing of mechanical type
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K1/00—Arrangement or mounting of electrical propulsion units
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • B60K17/165—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing provided between independent half axles
    • 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
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/042—Combinations of toothed gearings only change gear transmissions in group arrangement
    • F16H37/046—Combinations of toothed gearings only change gear transmissions in group arrangement with an additional planetary gear train, e.g. creep gear, overdrive
    • 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
    • B60K2001/001—Arrangement or mounting of electrical propulsion units one motor mounted on a propulsion axle for rotating right and left wheels of this axle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H2037/028—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings having two distinct forward drive ratios and one reverse drive ratio arranged in series with a continuously variable transmission unit
    • 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
    • F16H2200/0008—Transmissions for multiple ratios specially adapted for front-wheel-driven vehicles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H2200/00—Transmissions for multiple ratios
    • F16H2200/003—Transmissions for multiple ratios characterised by the number of forward speeds
    • F16H2200/0034—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising two 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
    • 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
    • F16H2200/2005—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with one 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
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts
    • F16H3/087—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears
    • F16H3/089—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially with continuously meshing gears, that can be disengaged from their shafts characterised by the disposition of the gears all of the meshing gears being supported by a pair of parallel shafts, one being the input shaft and the other the output shaft, there being no countershaft involved
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/06—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts
    • F16H37/08—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing
    • F16H37/0806—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts
    • F16H37/0813—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings with a plurality of driving or driven shafts; with arrangements for dividing torque between two or more intermediate shafts with differential gearing with a plurality of driving or driven shafts with only one input shaft

Definitions

  • the present invention relates to the field of vehicles, and in particular to a transaxle and a two-speed drive module thereof.
  • the transaxle is the mechanism at the end of the drive train for varying the speed and torque from the transmission and transmitting them to the drive wheels.
  • the drive axle typically includes a transaxle case, a final drive, a differential, and the like.
  • the two powertrains of the transmission and the drive axle are integrated into one, and are also arranged in the transaxle case. This type of drive axle is called a transaxle.
  • a transaxle with a two-speed drive module is introduced, which is provided with two sets of switchable gear shifting pairs at the output end of the motor.
  • the power output from the motor is transmitted to a set of spur gears via the shifting gear pair.
  • the differential module adjusts the output ratio of the motor by switching gear shifting gears of different gears to improve the driving torque and optimize the driving dynamics performance.
  • each gear pair is sequentially arranged in the radial direction, and the output gear of the spur gear set serves as the final gear of the entire drive module.
  • the size of the final gear affects the maximum output torque of the entire transaxle.
  • the diameter of the final gear is usually large, which in turn makes the diameter of the transaxle case at the final gear portion larger, resulting in the transmission distance from the transmission. Not high enough to be suitable for SUVs.
  • the ultimate gear due to the limitation of the distance from the ground, the ultimate gear The selectable range of diameters is also limited, which in turn limits the output torque of the entire transaxle.
  • the problem solved by the present invention is that the existing transmission module of the two-speed drive module has a large radial dimension at the final gear portion, and the output torque of the entire transaxle is limited.
  • the present invention provides a two-speed drive module of a transaxle including an input shaft, an output shaft, and a gear assembly for transmitting power between the input shaft and the output shaft;
  • the gear assembly The utility model comprises: a two-speed gear set, the two-speed gear set has two sets of shift gear pairs having different speed ratios, and the shift gear pair can be connected or disconnected from the input shaft to input the input The rotational speed of the shaft is output at different speed ratios; the planetary gear set, the output end of the planetary gear set is drivingly coupled to the output shaft; the gear set is coupled, the two-speed gear set and the planetary gear set are coupled through a gear set Drive connection.
  • the two-speed gear set further includes an intermediate shaft;
  • the shift gear pair includes an idler gear and a fixed gear that mesh with each other, and the idler gear is sleeved on the input shaft and the intermediate shaft
  • the fixed gear is fixed on the other of the input shaft and the intermediate shaft;
  • the synchronizer and the idler gear are fixed in the input shaft and the intermediate shaft On the same one, it is used to engage or disengage the idler gear of the shift gear pair.
  • the idler gear and the synchronizer are all disposed on the input shaft, the fixed gear is disposed on the intermediate shaft; and the connecting gear set is disposed along an axial direction of the intermediate shaft Between the two sets of shift gear pairs.
  • the connecting gear set includes a first gear fixed on the intermediate shaft, and a second gear connected to an input end of the planetary gear set; between the first gear and the second gear It is connected by a transmission.
  • the transmission member is a gear, a belt or a chain.
  • the idler gear and the synchronizer are all disposed on the intermediate shaft, the fixed gear is disposed on the input shaft; and the connecting gear set is disposed along an axial direction of the intermediate shaft On one side of the shift gear pair of the two sets.
  • the connecting gear set includes a first gear fixed on the intermediate shaft, and a second gear connected to an input end of the planetary gear set; the first gear and the second gear mesh with each other .
  • the planetary gear set has a sun gear as an input end, and a planet carrier as an output end is connected to the output shaft.
  • the present invention also provides a transaxle comprising the two-speed drive module of any of the above, and a motor, a differential; an output of the motor is coupled to the input shaft of the two-speed drive module The input end of the differential is coupled to the output shaft of the two-speed drive module.
  • the invention adds a planetary gear set in the two-speed drive module, and uses the planetary gear set as the final gear.
  • the amplification function of the input torque can be improved by the two-speed drive module, on the other hand,
  • the radial dimension of the two-speed drive module can be reduced to reduce the diameter of the transaxle case at the final gear portion, thereby reducing the ground clearance of the transaxle.
  • Figure 1 is a schematic block diagram showing the structure of a transmission axle of a first embodiment of the present invention
  • FIG. 2 is a schematic block diagram showing the structure of a two-speed driving module according to a first embodiment of the present invention
  • Figure 3 is a schematic block diagram showing the structure of a transmission axle of a second embodiment of the present invention.
  • FIG. 4 is a schematic structural diagram of a two-speed driving module according to a second embodiment of the present invention.
  • Figure 5 is a schematic view showing the structure of a transmission transaxle in a modification of the second embodiment of the present invention.
  • Figure 6 is a schematic view showing the structure of a two-speed drive module in a modification of the second embodiment of the present invention.
  • An embodiment of the present invention provides a two-speed drive module T for a transaxle.
  • the two-speed drive module T includes an input shaft 1, an output shaft (not shown), and is used for input.
  • a gear assembly that transmits power between the shaft 1 and the output shaft. The input torque from the power source is input from the input shaft 1, and the torque is amplified by the gear assembly to become the output torque, and the output torque is output by the output shaft.
  • the gear assembly includes three major components, a two-speed gear set 31, a planetary gear set 32, and a connecting gear set 33.
  • the two-speed gear set 31 has two sets of shift gear pairs Z1 and Z2 having different speed ratios, and the shift gear pairs Z1 and Z2 can be respectively connected or disconnected from the input shaft 1 to rotate the input shaft 1. Output at different speed ratios.
  • the planetary gear set 32 acts as the final gear of the gear assembly with its output coupled to the output shaft.
  • the two-speed gear set 31 and the planetary gear set 32 are drivingly coupled by a connecting gear set 33: in the torque transmitting direction, the connecting gear set 33 is disposed between the two-speed gear set 31 and the planetary gear set 32, and at its input end and two speeds
  • the output of the gear set 31 is in driving connection and is coupled at its output to the input of the planetary gear set 32.
  • the input torque is input from the input shaft 1, it is transmitted to the two-speed gear set 31 for one-time torque amplification, and then transmitted from the two-speed gear set 31 to the connected gear set 33 for secondary torque amplification, and finally transmitted from the connecting gear set 33 to the planetary gears.
  • the group 32 performs three torque amplifications, and the planetary gear set 32 outputs the amplified final torque as an output torque to the output shaft.
  • a planetary gear set 32 is added to the two-speed drive module T, and the planetary gear set 32 is placed at the end of the drive module T as a final gear based on the planetary gear set.
  • the small size and large speed ratio of 32 can not only improve the amplification function of the input torque of the two-speed drive module T, but also reduce the radial dimension of the two-speed drive module T.
  • the diameter of the final gear portion can be reduced for the transaxle housing accommodating the two-speed drive module T, thereby reducing the variable speed drive. The distance from the bridge to the ground.
  • the planetary gear set 32 takes the sun gear P1 as an input end and the carrier P2 as an output shaft of the two-speed drive module T. It should be noted that since the planetary gear set 32 has a good torque amplifying function, the speed ratio of the connecting gear set 33 can be set to be large, so the diameter of the output gear of the connecting gear set 33 can also be designed to be relatively small. Ensure the distance of the transaxle from the ground.
  • the two-speed gear set 31 further includes an intermediate shaft 4 and a synchronizer S, and the shift gear pairs Z1, Z2 are supported by the input shaft 1 and the intermediate shaft 4.
  • the two sets of shifting gear pairs Z1 and Z2 respectively have an idler gear and a fixed gear (not shown), and each set of shifting gear pairs is sleeved on the input shaft 1 and the intermediate shaft through the idler gear.
  • One of the 4 is fixed to the other of the input shaft 1 and the intermediate shaft 4 by a fixed gear.
  • the synchronizer S is fixed to the same one of the input shaft 1 and the intermediate shaft 4 with the idler gear for engaging or disengaging with the idler gear of the shift gear pair Z1, Z2.
  • the idler gears of the two sets of shift gear pairs Z1, Z2 can share a synchronizer S, and the synchronizer S is axially disposed between the two idler gears.
  • the idle gears of the two sets of shifting gear pairs Z1 and Z2 are all disposed on the input shaft 1 as the driving gear of the shifting gear pair, and the fixed gear is disposed on the intermediate shaft 4 as the shifting gear.
  • the synchronizer S is sleeved on the input shaft 1 and located between the two idler gears.
  • the connecting gear set 33 is disposed between the two sets of shifting gear pairs Z1, Z2 along the axial direction of the intermediate shaft 4. As can be seen from Figures 1 and 2, the position of the connecting gear set 33 in the axial direction is between the two sets of gears, which can effectively reduce the axial dimension of the drive module T.
  • the connecting gear set 33 includes a first gear G1 fixed to the intermediate shaft 4, and a second gear G2 coupled to the input end of the planetary gear set 32.
  • First gear G1 The second gear G2 is drivingly connected by a transmission member G3.
  • the transmission member G3 can be a gear, a belt, a chain or other conveyor belt.
  • the transmission member G3 is a gear, and the gears are an odd number, for example, one or three intermeshing gears.
  • the first gear G1 and the second gear G2 may also be directly engaged.
  • the two-speed driving module T of the embodiment of the present invention can realize a larger torque amplifying function, and has a smaller radial size, which is advantageous for improving the ground clearance of the transaxle, and has The compact axial size allows for more space for the arrangement of the exhaust pipe.
  • the embodiment of the invention further provides a transaxle, as shown in FIG. 1, which comprises the above two-speed driving module T, and the motor M, the differential D, and two and a half connected to the output of the differential D. Shafts 51, 52.
  • the motor M is used as a power source, and the output end thereof is connected to the input shaft 1 of the two-speed drive module T, the input end of the differential D is connected to the output shaft of the two-speed drive module T, and the second gear G2 of the gear set 33 is connected.
  • the air sleeve is sleeved on one of the half shafts 51 of the differential D, and the sun gear P1 of the planetary gear set 32 is also sleeved on the half shaft 51 and fixed to the transaxle case (not shown) via the ring gear P3. .
  • the output torque output from the motor M is amplified by the torque of the two-speed drive module T, and then distributed through the differential D to the two half shafts 51, 52 of the transaxle to drive the wheels forward.
  • the difference between this embodiment and the first embodiment lies in the arrangement of the two-speed gear set 31 and the connecting gear set 33.
  • the idle gears of the two sets of shift gear pairs Z1 and Z2 are all disposed on the intermediate shaft 4, and are used as the driven gears of the shift gear pair, and the fixed gears are all provided.
  • the synchronizer S is also disposed on the intermediate shaft 4 and is disposed between the two idler gears in the axial direction.
  • the connecting gear set 33 is provided on one side of the two sets of shifting gear pairs Z1, Z2 along the axial direction of the intermediate shaft 4.
  • the connecting gear set 33 includes a first gear G1 fixed to the intermediate shaft 4, and a second gear G2 connected to the input end of the planetary gear set 32.
  • First gear G1 The second gear G2 meshes with each other.
  • first gear G1 and the second gear G2 can be connected by the transmission member G3, as shown in FIG. 5 and FIG.
  • the transmission member G3 may be a gear, a belt or a chain or the like.

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

Abstract

一种变速驱动桥及其双速驱动模块（T），其中双速驱动模块（T）包括输入轴（1）、输出轴以及用于在所述输入轴（1）和所述输出轴之间传递动力的齿轮组件（31，32，33）；所述齿轮组件（31，32，33）包括：双速齿轮组（31），所述双速齿轮组（31）具有两组具有不同速比的换挡齿轮副（Z1，Z2），所述换挡齿轮副（Z1，Z2）能够与所述输入轴（1）传动连接或断开连接，以将所述输入轴（1）的转速以不同的速比输出；行星齿轮组（32），所述行星齿轮组（32）的输出端与所述输出轴传动连接；连接齿轮组（33），所述双速齿轮组（31）和所述行星齿轮组（32）通过连接齿轮组（33）传动连接。所述双速驱动模块（T）能够减小径向尺寸，减小变速驱动桥的离地距离。

Description

变速驱动桥及其双速驱动模块
本申请要求于2016年04月28日提交中国专利局、申请号为201610278591.8、发明名称为“变速驱动桥及其双速驱动模块”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。
技术领域
本发明涉及车辆领域，具体涉及一种变速驱动桥及其双速驱动模块。
背景技术
传统汽车中，驱动桥是位于传动系统末端、用于改变来自变速器的转速和转矩，并将它们传递给驱动轮的机构，驱动桥一般包括驱动桥壳、主减速器、差速器等。而对于采用发动机前置前桥驱动形式的车辆，变速器和驱动桥两个动力总成合为一体，一并布置在驱动桥壳内，这种形式的驱动桥则称为变速驱动桥。
当变速驱动桥用于混合动力车辆或纯电车辆时，电机将作为变速驱动桥的动力源，为了在不增加电机体积和成本的前提下提高驱动扭矩，吉凯恩(GKN)在在2014年推出了一款具有双速驱动模块的变速驱动桥，其在电机的输出端设置了两组可切换的换挡齿轮副，电机输出的动力经由换挡齿轮副后通过一组直齿轮组传递至差速器，该驱动模块通过切换不同挡位的换挡齿轮副来调整电机的输出传动比，以提高驱动扭矩、优化行驶动力学表现。在该驱动模块中，各个齿轮副按径向依次排列，直齿轮组的输出齿轮作为整个驱动模块的终极齿轮。
其中终极齿轮的大小影响着整个变速驱动桥的最大输出扭矩，为了提升最大输出扭矩，终极齿轮的直径通常较大，进而使得驱动桥壳体在终极齿轮部位的直径较大、导致变速器离地距离不够高，从而不能适用于SUV。相对应地，由于受到离地距离的限制，终极齿轮的 直径的可选范围也很有限，进而限制了整个变速驱动桥的输出扭矩。
发明内容
本发明解决的问题是现有具有双速驱动模块中传动模块在终极齿轮部位的径向尺寸大，整个变速驱动桥的输出扭矩受限。
为解决上述问题，本发明提供一种变速驱动桥的双速驱动模块，包括输入轴、输出轴以及用于在所述输入轴和所述输出轴之间传递动力的齿轮组件；所述齿轮组件包括：双速齿轮组，所述双速齿轮组具有两组具有不同速比的换挡齿轮副，所述换挡齿轮副能够与所述输入轴传动连接或断开连接，以将所述输入轴的转速以不同的速比输出；行星齿轮组，所述行星齿轮组的输出端与所述输出轴传动连接；连接齿轮组，所述双速齿轮组和所述行星齿轮组通过连接齿轮组传动连接。
可选的，所述双速齿轮组还包括中间轴；所述换挡齿轮副包括相互啮合的空套齿轮和固套齿轮，所述空套齿轮空套于所述输入轴、所述中间轴的其中一个上，所述固套齿轮固设于所述输入轴、所述中间轴的另一个上；同步器，与所述空套齿轮固套于所述输入轴、所述中间轴中的同一个上，用于与所述换挡齿轮副的空套齿轮接合或分离。
可选的，所述空套齿轮、所述同步器均设于所述输入轴上，所述固套齿轮设于所述中间轴上；所述连接齿轮组沿所述中间轴的轴向设于两组所述换挡齿轮副之间。
可选的，所述连接齿轮组包括固设于所述中间轴上的第一齿轮，以及与所述行星齿轮组的输入端连接的第二齿轮；所述第一齿轮、第二齿轮之间通过传动件传动连接。
可选的，所述传动件为齿轮、皮带或链条。
可选的，所述空套齿轮、所述同步器均设于所述中间轴上，所述固套齿轮设于所述输入轴上；所述连接齿轮组沿所述中间轴的轴向设 于两组所述换挡齿轮副的一侧。
可选的，所述连接齿轮组包括固设于所述中间轴上的第一齿轮，以及与所述行星齿轮组的输入端连接的第二齿轮；所述第一齿轮、第二齿轮相互啮合。
可选的，所述行星齿轮组以太阳轮作为输入端，以行星架作为输出端与所述输出轴连接。
本发明还提供一种变速驱动桥，其包括上述任一项所述的双速驱动模块，以及电机、差速器；所述电机的输出端与所述双速驱动模块的所述输入轴连接，所述差速器的输入端与所述双速驱动模块的所述输出轴连接。
与现有技术相比，本发明的技术方案具有以下优点：
本发明在双速驱动模块中增设行星齿轮组，并将行星齿轮组作为终极齿轮，相比于现有的直齿轮组，一方面可以提高双速驱动模块对输入扭矩的放大功能，另一方面可以减小双速驱动模块径向尺寸，以减小驱动桥壳在终极齿轮部位的直径，从而减小变速驱动桥的离地距离。
附图说明
图1是本发明第一实施例的变速器驱动桥的结构示意简图；
图2是本发明第一实施例的双速驱动模块的结构示意简图；
图3是本发明第二实施例的变速器驱动桥的结构示意简图；
图4是本发明第二实施例的双速驱动模块的结构示意简图；
图5是本发明第二实施例的变形例中变速器驱动桥的结构示意简图；
图6是本发明第二实施例的变形例中双速驱动模块的结构示意 简图。
具体实施方式
为使本发明的上述目的、特征和优点能够更为明显易懂，下面结合附图对本发明的具体实施例做详细的说明。
第一实施例
本发明实施例提供一种变速驱动桥的双速驱动模块T，参照图1、图2所示，该双速驱动模块T包括输入轴1、输出轴(图中未标注)以及用于在输入轴1和输出轴之间传递动力的齿轮组件。来自动力源的输入扭矩从输入轴1输入，由齿轮组件将扭矩放大后变为输出扭矩，并由输出轴将输出扭矩输出。
如图2所示，齿轮组件包括三大部件，双速齿轮组31、行星齿轮组32以及连接齿轮组33。其中，双速齿轮组31具有两组具有不同速比的换挡齿轮副Z1、Z2，换挡齿轮副Z1、Z2分别能够与输入轴1传动连接或断开连接，以将输入轴1的转速以不同的速比输出。
行星齿轮组32作为齿轮组件的终极齿轮，其输出端与输出轴传动连接。双速齿轮组31和行星齿轮组32通过连接齿轮组33传动连接：沿扭矩传递方向，连接齿轮组33设于双速齿轮组31和行星齿轮组32之间，并在其输入端与双速齿轮组31的输出端传动连接，在其输出端与行星齿轮组32的输入端传动连接。
输入扭矩从输入轴1输入后，传递至双速齿轮组31进行一次扭矩放大，然后由双速齿轮组31传递至连接齿轮组33进行二次扭矩放大，最后由连接齿轮组33传递至行星齿轮组32进行三次扭矩放大，并由行星齿轮组32将放大后的最终扭矩作为输出扭矩输出至输出轴。
本方案中，在双速驱动模块T中增设行星齿轮组32，并将行星齿轮组32放置于驱动模块T的末端作为终极齿轮，基于行星齿轮组 32体积小、速比大的特点，不仅可以提高双速驱动模块T对输入扭矩的放大功能，还可以减小双速驱动模块T径向尺寸。那么相应地，当双速驱动模块T安装在汽车的变速驱动桥上时，对于容纳双速驱动模块T的驱动桥壳来说，可以减小其在终极齿轮部位的直径，从而减小变速驱动桥的离地距离。
其中，行星齿轮组32以太阳轮P1作为输入端，以行星架P2作为双速驱动模块T的输出轴。需要注意的是，由于行星齿轮组32具有良好的扭矩放大功能，连接齿轮组33的速比可以不需要设置地很大，故连接齿轮组33的输出齿轮的直径也可以设计得比较小，从而保证变速驱动桥的离地距离。
继续参照图1、图2所示，双速齿轮组31还包括中间轴4和同步器S，换挡齿轮副Z1、Z2通过输入轴1、中间轴4支承。具体地，两组换挡齿轮副Z1、Z2分别具有一个空套齿轮和一个固套齿轮(图中未标注)，每组换挡齿轮副均通过空套齿轮空套于输入轴1、中间轴4的其中一个上，并通过固套齿轮固设于输入轴1、中间轴4的另一个上。同步器S则与空套齿轮固套于输入轴1、中间轴4中的同一个上，用于与换挡齿轮副Z1、Z2的空套齿轮接合或分离。其中，为了节约轴向空间，两组换挡齿轮副Z1、Z2的空套齿轮可以共用一个同步器S，同步器S沿轴向设于两空套齿轮之间。
本实施例中，两组换挡齿轮副Z1、Z2的空套齿轮均设于输入轴1上、作为换挡齿轮副的主动齿轮，固套齿轮则设于中间轴4上、作为换挡齿轮副的从动齿轮。同步器S则套设于输入轴1上且位于两空套齿轮之间。
连接齿轮组33沿中间轴4的轴向设于两组换挡齿轮副Z1、Z2之间。从图1、图2中可以看出，连接齿轮组33沿轴向的位置处于两固套齿轮之间，这样可以有效减小驱动模块T的轴向尺寸。
具体地，连接齿轮组33包括固设于中间轴4上的第一齿轮G1，以及与行星齿轮组32的输入端连接的第二齿轮G2。第一齿轮G1、 第二齿轮G2之间通过传动件G3传动连接。传动件G3可以是齿轮、皮带、链条或者其他传送带。本实施例中，传动件G3选用齿轮，齿轮为奇数个，例如为1个或者3个相互啮合的齿轮。在其他实施例中，第一齿轮G1、第二齿轮G2也可以直接啮合。
综上，相比于现有技术，本发明实施例的双速驱动模块T能够实现较大的扭矩放大功能，且具有更小的径向尺寸，利于提高变速驱动桥的离地距离，同时具有紧凑的轴向尺寸，可以给排气管的布置预留更多的空间。
本发明实施例还提供一种变速驱动桥，如图1所示，其包括上述双速驱动模块T，以及电机M、差速器D，以及与差速器D的输出端连接的两根半轴51、52。其中，电机M作为动力源，其输出端与双速驱动模块T的输入轴1连接，差速器D的输入端与双速驱动模块T的输出轴连接，连接齿轮组33的第二齿轮G2空套在差速器D的一根半轴51上，行星齿轮组32的太阳轮P1也空套在半轴51上，并通过齿圈P3固定在驱动桥壳(图中未示出)上。电机M输出的输出扭矩经由双速驱动模块T的扭矩放大后，通过差速器D分配至驱动桥的两个半轴51、52，以驱动车轮前进。
第二实施例
本实施例与第一实施例的区别在于双速齿轮组31以及连接齿轮组33的设置方式上。
本实施例中，如图3、图4所示，两组换挡齿轮副Z1、Z2的空套齿轮均设于中间轴4上、作为换挡齿轮副的从动齿轮，固套齿轮均设于输入轴1上、作为换挡齿轮副的主动齿轮，同步器S也设于中间轴4上且沿轴向设于两空套齿轮之间。
连接齿轮组33沿中间轴4的轴向设于两组换挡齿轮副Z1、Z2的一侧。其中，连接齿轮组33包括固设于中间轴4上的第一齿轮G1，以及与行星齿轮组32的输入端连接的第二齿轮G2。第一齿轮G1、 第二齿轮G2相互啮合。
在其他实施例中，第一齿轮G1、第二齿轮G2可以通过传动件G3实现传动连接，如图5、图6所示。其中，传动件G3可以是齿轮、皮带或者链条等。
虽然本发明披露如上，但本发明并非限定于此。任何本领域技术人员，在不脱离本发明的精神和范围内，均可作各种更动与修改，因此本发明的保护范围应当以权利要求所限定的范围为准。

Claims (9)

  1. 一种变速驱动桥的双速驱动模块，包括输入轴、输出轴以及用于在所述输入轴和所述输出轴之间传递动力的齿轮组件；
    其特征在于，所述齿轮组件包括：
    双速齿轮组，所述双速齿轮组具有两组具有不同速比的换挡齿轮副，所述换挡齿轮副能够与所述输入轴传动连接或断开连接，以将所述输入轴的转速以不同的速比输出；
    行星齿轮组，所述行星齿轮组的输出端与所述输出轴传动连接；
    连接齿轮组，所述双速齿轮组和所述行星齿轮组通过连接齿轮组传动连接。
  2. 如权利要求1所述的双速驱动模块，其特征在于，所述双速齿轮组还包括中间轴；
    所述换挡齿轮副包括相互啮合的空套齿轮和固套齿轮，所述空套齿轮空套于所述输入轴、所述中间轴的其中一个上，所述固套齿轮固设于所述输入轴、所述中间轴的另一个上；
    同步器，与所述空套齿轮固套于所述输入轴、所述中间轴中的同一个上，用于与所述换挡齿轮副的空套齿轮接合或分离。
  3. 如权利要求2所述双速驱动模块，其特征在于，所述空套齿轮、所述同步器均设于所述输入轴上，所述固套齿轮设于所述中间轴上；
    所述连接齿轮组沿所述中间轴的轴向设于两组所述换挡齿轮副 之间。
  4. 如权利要求3所述的双速驱动模块，其特征在于，所述连接齿轮组包括固设于所述中间轴上的第一齿轮，以及与所述行星齿轮组的输入端连接的第二齿轮；
    所述第一齿轮、第二齿轮之间通过传动件传动连接。
  5. 如权利要求4所述的双速驱动模块，其特征在于，所述传动件为齿轮、皮带或链条。
  6. 如权利要求2所述双速驱动模块，其特征在于，所述空套齿轮、所述同步器均设于所述中间轴上，所述固套齿轮设于所述输入轴上；
    所述连接齿轮组沿所述中间轴的轴向设于两组所述换挡齿轮副的一侧。
  7. 如权利要求6所述的双速驱动模块，其特征在于，所述连接齿轮组包括固设于所述中间轴上的第一齿轮，以及与所述行星齿轮组的输入端连接的第二齿轮；
    所述第一齿轮、第二齿轮相互啮合。
  8. 如权利要求1-7中任一项所述的双速驱动模块，其特征在于，所述行星齿轮组以太阳轮作为输入端，以行星架作为输出端与所述输出轴连接。
  9. 一种变速驱动桥，其特征在于，包括权利要求1-8中任一项所 述的双速驱动模块，以及电机、差速器；
    所述电机的输出端与所述双速驱动模块的所述输入轴连接，所述差速器的输入端与所述双速驱动模块的所述输出轴连接。
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