WO2015018341A1 - 一种车用自动变速桥总成 - Google Patents

一种车用自动变速桥总成 Download PDF

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Publication number
WO2015018341A1
WO2015018341A1 PCT/CN2014/083799 CN2014083799W WO2015018341A1 WO 2015018341 A1 WO2015018341 A1 WO 2015018341A1 CN 2014083799 W CN2014083799 W CN 2014083799W WO 2015018341 A1 WO2015018341 A1 WO 2015018341A1
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WO
WIPO (PCT)
Prior art keywords
assembly
gear
shifting
power input
ring
Prior art date
Application number
PCT/CN2014/083799
Other languages
English (en)
French (fr)
Inventor
刘培生
Original Assignee
Liu Peisheng
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 Liu Peisheng filed Critical Liu Peisheng
Priority to US14/910,949 priority Critical patent/US10232706B2/en
Publication of WO2015018341A1 publication Critical patent/WO2015018341A1/zh

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • 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
    • 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
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K17/00—Arrangement or mounting of transmissions in vehicles
    • B60K17/04—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing
    • B60K17/16—Arrangement or mounting of transmissions in vehicles characterised by arrangement, location, or kind of gearing of differential gearing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • 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
    • F16H3/46—Gearings having only two central gears, connected by 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
    • F16H3/44—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion using gears having orbital motion
    • F16H3/62—Gearings having three or more central gears
    • F16H3/66—Gearings having three or more central gears composed of a number of gear trains without drive passing from one train to another
    • 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
    • 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
    • F16H59/00—Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/02—Selector apparatus
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • 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
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H63/32—Gear shift yokes, e.g. shift forks
    • F16H2063/321—Gear shift yokes, e.g. shift forks characterised by the interface between fork body and shift rod, e.g. fixing means, bushes, cams or pins
    • 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
    • F16H2200/0039—Transmissions for multiple ratios characterised by the number of forward speeds the gear ratios comprising three 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
    • F16H2200/201—Transmissions using gears with orbital motion characterised by the number of sets of orbital gears with three 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
    • F16H2200/2038—Transmissions using gears with orbital motion characterised by the engaging friction means not of the freewheel type, e.g. friction clutches or brakes with three engaging means
    • 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
    • F16H3/083—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 with radially acting and axially controlled clutching members, e.g. sliding keys

Definitions

  • the present invention relates to the field of power transmission, and more particularly to an automatic transmission bridge assembly for a vehicle.
  • the automobile in order to achieve automatic shifting, the automobile usually has a set of gears and a corresponding control and operating mechanism, which has a complicated structure, high cost, and is prone to failure. If the power and input and output components are added, it is actually the cardiovascular of the car. It is a major component of the car and a weak link in China's automotive technology. It is the key to the innovation of the car, especially the current electric car. Summary of the invention
  • the invention provides an automatic transmission bridge assembly for a vehicle, wherein a power input shaft extends into a shifting chamber, and a shifting mechanism is arranged on a power input shaft in the shifting chamber, the shifting mechanism including a shifting sleeve assembly, a modification
  • the one-way device, the gear sun gear, the planetary gear, the planet carrier and the ring gear, the gear sun gear, the planetary gear and the ring gear constitute a fixed transmission ratio mechanism, and the shift sleeve assembly can be modified with the one-way Matches.
  • the modified one-way device is located outside of the shifting sleeve assembly, and the shifting sleeve assembly is slidable along the power input shaft between the power input shaft and the modified one-way device.
  • the shifting mechanism directly outputs power through an output gear or an output shaft, or drives differential rotation of the first and second power output shafts through a differential
  • the power input shaft is a hollow shaft
  • the first power output A shaft passes through the interior of the power input shaft.
  • the number of fixed transmission ratios is at least two.
  • the modified one-way device has no inner ring, and the variable speed sliding sleeve assembly serves as an inner ring of the modified one-way device, which is respectively in contact with each of the one-way devices, and can be laterally along the power input shaft Spline sliding.
  • the transmission can be integrated with the motor, the motor rotates internally, and the motor output shaft is the transmission power input shaft; when the motor rotates, the outer rotor is connected with the ring gear or the carrier.
  • the assembly may be additionally provided with a bridge or axle housing, and the axle housing or the bridge body may include inner and outer ball cages and suspension support base connectors.
  • the sun gear is a power input component, one of the planet carrier and the ring gear is used as a power output component, and the other is a fixed component; or the ring gear is a power input component, and one of the sun gear and the carrier is used as a power output. a component, the other as a fixed component; or the planet carrier is a power input component, one of the sun gear and the ring gear as a power output One, the other as a fixed part.
  • the sun gear is a power input component
  • the planet carrier is a power output component
  • the outer ring layer of the ring gear is an integral circle, which is a part of a fixed outer casing, and the inner casing is divided into a motor compartment and a transmission bin.
  • the shifting sleeve assembly comprises a sliding sleeve and a cable or a fork, and the pulling ring and the cable can be manually pulled or electrically pulled;
  • the shifting sleeve assembly comprises a spring.
  • the spring sleeve is placed on the input shaft, and the action of the pull ring can be both thrust and tension; the sliding sleeve can also be moved by the fork.
  • the shift sleeve assembly includes a sliding sleeve, a pull ring and a lead screw; the lead screw is electrically driven.
  • plan is as follows:
  • An automatic shifting bridge assembly wherein the power input component, that is, the power input, may be a gear or a (motor) spline shaft, and the power output is a differential output, and the automatic shifting portion includes a sliding sleeve assembly, a one-way component, and a planetary gear row.
  • the assembly or parallel shaft shifting gear assembly is an integrated powertrain.
  • the shifting bridge can be integrated with the motor and directly connected to the shifting part coaxially.
  • the concentric air shaft is better.
  • the motor output shaft is the power input shaft, and the empty shaft can output the spline through the differential.
  • the outer casing is connected with the oil hole of the shifting portion to facilitate heat dissipation; or the outer casing is water-cooled or air-cooled; the assembly can be provided with a final reducer and a bridge body (bridge housing), and the bridge body can include inner and outer ball cages and suspension support base connecting members. .
  • the automatic shifting portion of the shifting bridge is composed of more than one row of planetary row assembly components, the sun gear of the planetary gear row assembly is a power input component, the planet carrier is a power output component, and the ring gear is a fixed outer casing; The wheel is the power input, the ring gear is the power output component, the planet carrier is the fixed part, and so on.
  • the outer ring layer of the ring gear of the planetary row of the present example is an integral circle, and each ring gear is laterally arranged in the whole circle by a plurality of ring gear rings of concentric but different radius and tooth top circle spaced apart by the inner wall, correspondingly meshing Planetary gears in several sets of ring gears, these sets of planetary gears are fixed by the same planet carrier.
  • the tooth profile of each ring gear and planetary gear is different and has a size; the number of teeth is also different, which is determined by the transmission ratio.
  • the inner side of the planetary gear meshes with the sun gear of the corresponding gear, and each of the sun gears has a one-way outer ring connected to the inner wall of the gear.
  • the carrier is fixed to the motor housing of the power output shaft, that is, the partition wall of the assembly (two rolling bearings or a rolling bearing and a sliding sleeve), and the other end is connected to the differential housing, that is, another partition wall of the assembly.
  • the ring gear and the motor housing are a one-piece structure with partition walls (two different chambers for the internal motor and the transmission).
  • variable-speed input spline shaft is axially arranged side by side with two or more one-way devices, and the sliding sleeve is inserted into the one-way device in each sun wheel, which is equivalent to the inner ring of each one-way device.
  • a long sleeve of a sliding ring which has a radial cylindrical protrusion in the middle and which can slide laterally along the spline, that is, a shifting sleeve, which is simply referred to as a sliding sleeve
  • the sliding sleeve comprises a middle radial cylindrical protrusion and a flat bottom on both sides (or a concave portion), a flat sleeve (sliding bearing) which is slidable along the outer diameter of the sliding sleeve along the outer diameter of the sliding sleeve, and the outer diameter of the thin sleeve is the same as the outer diameter of the cylindrical projection; the thin sleeve and the protrusion
  • the outer diameter can be in contact with the rollers (clamshells) in the one-way non-inner ring of each gear, and rotate in the same direction and slide in the lateral direction.
  • the outer ring walls of the separated one-way outer sleeves of the sliding sleeve respectively have two or more high and low speed sun wheels with different modulus and number of teeth.
  • the sliding sleeve and the protrusion When the spline shaft rotates in the forward direction, the sliding sleeve and the protrusion also rotate in the forward direction and the corresponding one-way device of the corresponding contact rotates synchronously, the high or low speed sun gear of a fixed position on the outer ring of the one-way device is also synchronized. Rotating, the output gear meshed with the gear also drives the car to operate at high or low gear; at this time, the one-way device corresponding to the flat bottom portion of the sliding sleeve is positively rotated, but the outer diameter of the flat bottom is much smaller than the inner circle of the side of the parallel block in the one-way device.
  • the inner diameter, the inner diameter of the block is not in direct contact with the flat bottom on the corresponding sliding sleeve, but can only pass through a thin (axial) sleeve which can be slid along the flat bottom (or the concave portion), when the sliding sleeve slides integrally
  • the flat bottom (or the concave portion) on the sliding sleeve and the thin sleeve sliding along it are in contact with the inner block of the one-way device, and the inner block of the one-way device can only be separated by the thin sleeve.
  • the thin sleeve slides between it and the flat bottom, and the one-way device and the block and the integral sliding sleeve cannot rotate synchronously, and the sun (teeth) wheel connected thereto cannot rotate synchronously with the power input spline shaft. If the spline shaft drives the sliding sleeve to rotate in the opposite direction, it will slide away from the inner block of all the positively rotating one-way devices without rotating it. When the protrusion on the sliding sleeve slides to the neutral position between the one-way devices, all the one-way devices do not rotate, which is the machine neutral. The sliding sleeve slides under the action of the fork or the pull cable, and the one-way device and the gear corresponding to the protrusion change, and the machine realizes the shifting.
  • the power is first turned off, the sliding sleeve is pulsed laterally, and the one-way device that contacts the sliding sleeve protrusion is changed, and the gear gear of the gear sun gear or the parallel shaft type connected thereto is also changed accordingly, that is, The high and low gears are realized; one or several one-way devices can be set on the sliding sleeve of the spline shaft, and the forward rotation direction is changed, that is, the original reverse phase is changed to the positive direction (the reverse direction is installed in the opposite direction, that is, the one hundred turns Installed in the 80-degree direction), the reverse rotation of the spline shaft and the sliding sleeve will drive one or several one-way devices to rotate in the forward direction and rotate the reverse gear corresponding to the one-way device to realize the reverse gear.
  • FIG. 1 is a schematic view showing the structure of a main body of a novel automatic transmission of the present invention
  • Figure 2 is a detailed view of the structure of the shifting sleeve.
  • An important embodiment of the present invention is a highly integrated motor and transmission, and the assembly is a new automatic shifting bridge including an automatic transmission and a power input (including an electric motor) and an output connecting member, which can be used as a front part of a pure electric vehicle and a hybrid electric vehicle. Bridge or rear axle.
  • This assembly can be supplied with a differential assembly (including PTO shaft), a bridge (bridge housing, which can contain internal and external cages and suspension supports).
  • the power input shaft is connected to the internal combustion engine power output shaft (wheel), that is, the internal combustion engine automatic shift bridge, it can be used in automobiles and hybrid electric vehicles; if the motor is connected to the power input shaft, it is an electric automatic shift bridge, available Yuchun electric (steam) car and hybrid (steam) car.
  • the invention provides an automatic transaxle assembly for a vehicle, wherein the power input component, that is, the power input can be a gear or a (motor) spline shaft, the power output is a differential output, and the automatic transmission part comprises a series modified one-way device.
  • the assembly has a sliding sleeve assembly and a shifting operation portion, such as a pull ring, and the shifting mechanism, which are respectively in contact with each one-way device in the form of a one-way inner ring, and can be laterally spline-slided, that is, two or more rows of outputs
  • a modified powertrain assembly with different speeds including ring gear, planet gear, planet carrier, sun gear) or parallel shaft gear assembly.
  • the transmission can be integrated with the motor, i.e., the shifting bin 2 shares a housing 1 with the motor compartment 3.
  • the motor output shaft is the transmission power input shaft 32, which is the same air shaft.
  • the spline shafts 51, 52 can be output through the power (differential speed) in the empty shaft; or the outer rotor and the ring gear can be rotated outside the motor.
  • the planet carrier is connected; the motor is connected to the oil hole of the shifting part through the outer casing to facilitate heat dissipation; or the outer casing can be cooled by water or blown in the machine.
  • the assembly may be additionally provided with a speed reducer, a bridge body (bridge housing), and the bridge body may include an inner and outer ball cage and a suspension support base connector.
  • the sun gear, planet carrier and ring gear of the modified planetary row structure component can be power input components, power output components and fixed components.
  • the sun gears 231, 232, 233 of the modified planetary row structure assembly are power input components
  • the carrier 12 is a power output component
  • the ring gears 111, 112, 113 are fixed on the same outer casing, that is, the outer ring wall of the planetary row
  • the layer is an integral circle casing 1.
  • each ring gear of the planetary row is axially arranged in the whole circle by a plurality of ring-shaped ring gears 111, 112, 113 which are axially spaced on the inner wall and are concentric but have a radius of the tooth tip circle, correspondingly meshing several groups of teeth Planetary gears 251, 252, 253 in the ring; these sets of planet gears are fixed by the same planet carrier 12, the gear shapes of the gear sets 251, 252, 253 are different, the size, the number of teeth is also different,
  • the transmission ratio determines that one end of the carrier is fixed to the partition of the motor casing or the assembly through the bearing 1211, or is fixedly supported by the thrust bearing 215 and the carrier support frame 216, and one end is connected to the differential 28 of the power output.
  • the other end of the differential 28 is fixed to the other end of the casing through a bearing 1212; the inner side of the planetary gears 251, 252, 253 is meshed with the sun gears 231, 232, 233 of the corresponding gears, and the sun gears 231, 232, 233 of each gear are also tooth-shaped.
  • the number of teeth is different; the inner wall of the sun gear is further connected with the outer ring of the one-way device 201, 202, 203; the outer ring layer of the ring gear of the planetary row and the motor casing are a partitioned whole structure ( Divided in two different motor chamber 32 and the transmission chamber cartridge).
  • the assembly consists of three or more layers (including three layers) of concentric (spline) shafts, sleeves, rings, and rings.
  • the series modified one-way device assembly of the automatic transmission portion has a shift sleeve assembly 7 which is in contact with each of the modified one-way devices in the form of a one-way inner ring and is laterally movable along the spline.
  • the sliding sleeve assembly passes through the rollers of the one-way device in each sun gear, corresponding to the position of the inner ring of each one-way device, and is a unitary, radially-inflated cylindrical sliding sleeve protrusion in the middle. 21.
  • the concave portion 23, 22 which is tapered on both sides of the protrusion has a transitional (support) thin sleeve (or sleeve sleeve, sliding bearing) which can be traversed along the outer diameter of the sleeve and slides along the outer diameter of the sleeve.
  • 31, 32 the outer diameter of which is the same as the outer diameter of the cylindrical protrusion 21; the outer diameters of the thin sleeves 31, 32 and the protrusions 21 can be in contact with the rollers (clamps) in the one-way device without the inner ring of each gear. Rotate synchronously, reverse each other, and slide laterally along the inside.
  • the corresponding one-way devices 201, 203 of the sliding sleeve flat bottom portion can also rotate in the forward direction, but the inner side of the wedge (roller) inside is not in direct contact with the flat bottoms 23, 22 on the corresponding sliding sleeve but passes through
  • the shafts (thin) on the flat bottom are in indirect contact
  • the one-way devices 201, 203 and the flat bottoms 23, 22 are not synchronously rotated, and the outer ring upper gears 231, 233 corresponding to the one-way devices 201, 203 are of course unable to rotate synchronously.
  • the kinetic energy is output, but only the planetary gears that mesh with it are idling.
  • the sliding sleeve 7 stops at a certain position according to the control requirement when sliding along the axial direction of the spline shaft 32.
  • the protrusion 21 on the sliding sleeve can correspond to a specific one-way device such as 202, the sliding sleeve 7 and
  • the forward rotation of the protrusion 21 can drive the specific one-way device 202 corresponding to the contact to rotate in the forward direction, and the reverse rotation rotates the sliding sleeve 7 and the specific one-way device 202; when the spline shaft 32 rotates in the forward direction and the sliding sleeve 7 Synchronous rotation, the protrusion 21 on the sliding sleeve and its corresponding contact specific one-way device 202 rotate synchronously, and the high-speed tooth (sun) wheel or low-speed tooth (sun) of a certain position fixed on the outer ring of the specific one-way device 202 The wheel also rotates synchronously, and the output gear (circle) engaged with the high speed
  • the power is first turned off, and the sliding sleeve 7 is laterally twitched, and the one-way device that contacts the sliding sleeve protrusion changes, and the gear gear connected thereto changes accordingly.
  • the switch is operated according to the speed change or the operator's will according to the operation, and the computer outputs the instantaneous power off, the driving electromagnet action signal, the spline axis
  • the upper sliding sleeve 7 and the protrusion 21 thereon are slid under the action of the pressing spring 270 and the pulling fork or the pulling ring 211 cable 261, so that the sliding sleeve drives the gear shifting gear to achieve the purpose of raising and lowering speed.
  • the protrusions 21 on the control sleeve and the sliding sleeve are slid down to the space outside the corresponding one-way device by the action of the fork or the pull ring 211, and the rotation of the one-way device is not driven to realize the machine neutral. .
  • the positive rotation direction of a certain one-way device on the sliding sleeve 7 of the spline shaft 32 is opposite, and the reverse rotation of the spline shaft and the sliding sleeve drives one or several one-way devices to rotate forward and make one-way direction
  • the reverse gear corresponding to the rotation of the device realizes the reverse gear.
  • the function of the cable 261 on the sliding sleeve 211 can be either manual pulling or electric pulling; the action of the spring 270 on the tab 211 can be both thrust and tension; the sliding sleeve can be pulled by the pull cable, Use the shift fork to toggle.
  • the sliding sleeve 7 slides left and right under the action of the cable 261 and the spring 270, and the machine realizes the shifting.
  • the sliding sleeve 7 functions as the cable 261 and the pull ring 211, and can be manually pulled or an electric suction switch.
  • the sliding sleeve 7 functions as the cable 261 and the pull ring 211, and can be manually pulled or an electric suction switch.

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Abstract

一种车用自动变速桥总成，动力输入轴（32）延伸至变速仓（2）中，在变速仓（2）中的动力输入轴（32）上设置有变速机构，所述变速机构包括变速滑套总成（7）、改型的单向器（201，202，203）、档位太阳齿轮（231，232，233）、行星齿轮（251，252，253）、行星架（12）以及齿圈（111，112，113），档位太阳齿轮（231，232，233）、行星齿轮（251，252，253）以及齿圈（111，112，113）构成固定传输比的机构，所述变速滑套总成（7）能够与改型的单向器（201，202，203）匹配。该自动变速桥总成实现了一体化的电动汽车自动变速桥。

Description

一种车用自动变速桥总成 技术领域
本发明涉及动力传送领域， 尤其涉及一种车用自动变速桥总成。
背景技术
目前汽车要实现自动变速， 通常要具备形成变速的成套设置和相应的控制与操纵机构， 结构复杂， 成本高， 易出故障。 如果加上动力与输入、 输出部件， 实际是汽车的心血管， 是 汽车的重大部件和我国汽车技术的薄弱环节， 是汽车特别是当前电动汽车研发创新的关键。 发明内容
本发明在此背景下， 为满足整车性能提高、 成本降低的要求， 采用新型离合、 滑动等部 件， 对变速原理与控制方式进行了设计突破， 实现了自动变速的轻型、 可靠与低成本。 本发 明一个重要实施例是电机与变速器的高度集成， 加上差速器总成（含动力输出轴）、 桥体（桥 壳， 可含内外球笼和悬挂支撑件）， 实现了一体化的电动汽车自动变速桥， 结构科学、 简约。
本发明提供了一种车用自动变速桥总成， 动力输入轴延伸至变速仓中， 在变速仓中的动 力输入轴上设置有变速机构， 所述变速机构包括变速滑套总成、 改型的单向器、 档位太阳齿 轮、 行星齿轮、 行星架以及齿圈， 档位太阳齿轮、 行星齿轮以及齿圈构成固定传输比的机构， 所述变速滑套总成能够与改型的单向器匹配。
优选地， 所述改型的单向器位于变速滑套总成外侧， 所述变速滑套总成能够在所述动力 输入轴和所述改型的单向器之间沿动力输入轴滑动。
优选地， 所述变速机构通过输出齿轮或输出轴直接输出动力， 或者通过差速器驱动第一、 第二动力输出轴差速转动， 所述动力输入轴为空心轴， 所述第一动力输出轴穿过所述动力输 入轴内部。
优选地， 所述固定传输比的数量至少为二个。
优选地， 所述改型的单向器无内环， 所述变速滑套总成充当所述改型的单向器的内环， 分别与各单向器内部接触、 可横向沿动力输入轴花键滑动。
优选地， 变速器可与电机做成一体， 电机内转， 电机输出轴即变速器动力输入轴； 电机 外转， 则外转子与齿圈或行星架连接。
优选地， 此总成可另附带桥体或桥壳， 桥壳或桥体可含内外球笼和悬挂支撑基础连接件。 优选地， 太阳轮为动力输入部件， 行星架和齿圈中的一个做为动力输出部件， 另外一个 做为固定部件； 或者齿圈为动力输入部件， 太阳轮和行星架中的一个作为动力输出部件， 另 外一个作为固定部件； 或者行星架为动力输入部件， 太阳轮和齿圈中的一个作为动力输出部 件， 另外一个作为固定部件。
优选地， 太阳轮为动力输入部件， 行星架为动力输出部件， 齿圈外壁层是一整体圆圈， 为固定的外壳的一部分， 外壳内部又分电机仓与变速器仓。
优选地， 所述的变速滑套总成包括滑套拉环以及拉索或拨叉， 所述拉环、 拉索既可手动 拉动， 也可用电动拉动； 所述的变速滑套总成包括弹簧， 弹簧套在输入轴上， 对拉环的作用， 既可推力， 也可拉力； 滑套也可用拨叉拨动。
优选地， 所述的变速滑套总成包括滑套、 拉环以及丝杠； 所述丝杠用电驱动。
更详细地， 方案如下：
一种自动变速桥总成， 其动力接入部件即动力输入可为齿轮或 （电机）花键轴，动力输出 为差速输出，自动变速部分包括滑套组件、 单向器组件、 行星齿轮排组件或平行轴式变速齿轮 组件为一体的动力总成。
变速桥可与电机做成一体直接与变速部分同轴相接， 以同心的空轴为好， 电机输出轴即 动力输入轴， 空轴可通过差速器输出花键； 电机内转， 可通过外壳与变速部分的油孔连接， 以利散热； 或以外壳水冷或内吹风冷； 总成可附带主减速器、 桥体 （桥壳)， 桥体可含内外球 笼和悬挂支撑基础连接件。
优选地， 变速桥的自动变速部分为一排以上的行星排组件结构组成， 其行星齿轮排组件 的太阳轮为动力输入部件， 行星架为动力输出部件， 齿圈为固定的外壳； 也可以太阳轮为动 力输入件， 齿圈为动力输出部件， 行星架为固定件， 等等。
优选地， 本例行星排的齿圈外壁层是一整体圆圈， 各齿圈由其内壁间隔的同心但半径、 齿顶圆不等的几圈齿圈横向排列在此整体圆圈内， 对应啮合几组齿圈内的行星齿轮， 这几组 行星齿轮由同一个行星架固定。 各齿圈、 行星齿轮的齿形是不同的， 有大小； 齿数也是不同 的， 由传输比决定。 行星齿轮内侧与其对应档的太阳轮啮合， 各档的太阳轮内又各有单向器 外环与齿轮内壁相连。 行星架一端固定在动力输出轴外伸的电机外壳即总成的间隔壁上 （两 个滚动轴承或一滚动轴承一滑套）， 另一端接差速器外壳即总成的另一间隔壁上。齿圈与电机 外壳为有间隔壁的一整体结构 （内分电机与变速器两个不同仓室）。
变速输入花键轴上轴向并排分离式套置有两个及其以上的单向器， 滑套穿在各太阳轮内 的单向器内， 相当于各单向器内环为一整体的、 中间带有径向圆柱形突起的、 可横向沿花键 滑动的滑环长套， 即变速滑套， 简称滑套， 滑套包括中间径向圆柱形突起和两侧的平底 (或说 下凹部分)， 平底上又有可沿滑套外径横切轴向、 沿滑套外径滑动的薄套 （滑动轴承）， 薄套 的外径与圆柱突起的外径相同； 薄套和突起外径均可与各档的无内环的单向器内的滚子 （锲 块） 接触、 同向转动并沿其横向滑动。 滑套外各分离的单向器外环壁上分别带有不同模数、齿数的两个及其以上高低速太阳轮。 滑套在沿花键轴轴向滑动时可根据控制要求在某一位置停下， 此时滑套上的突起可对应接触 某一单向器， 滑套上的平底 (或说下凹部分)上的薄套则对应另外的单向器。 当花键轴正向转 动、 滑套及突起也正向转动并带动对应接触的此单向器同步正向转动， 单向器外环上固定的 某一档位的高或低速太阳齿轮也同步转动， 与此齿轮啮合的输出齿轮也带动汽车高或低档运 转； 此时， 滑套平底部分对应的单向器虽是正向转动， 但平底外径远小于单向器内并排锲块 内侧圆的内径， 锲块内径与其对应的滑套上的平底不直接接触而只能通过平底 (或说下凹部分) 上另设的可沿其滑转的薄 （轴） 套， 当滑套整体横向滑动、 滑套上的平底 (或说下凹部分)及 其上沿其滑转的薄套与某一单向器内锲块接触， 则单向器内锲块由于此薄套间隔， 只能由薄 套在其与平底之间滑转， 单向器及锲块与整体滑套不能同步转动， 与其相连的太阳 （齿） 轮 也就不能与动力输入花键轴同步转动。 若花键轴带动滑套反向转动则与所有正向转动的单向 器内锲块相滑离， 不带动其转动。 当滑套上突起滑动至单向器间的空档时， 则所有单向器不 转， 即为机器空档。 滑套在拨叉或拉环拉索的作用下如此滑动， 突起对应的单向器及齿轮变 化， 机器也就实现变速。
当需变档时， 首先瞬时关断动力， 横向抽动滑套， 使滑套突起接触的单向器变化， 与之 相连的某档位太阳轮或平行轴式的档位齿轮也相应变化， 即实现了高低档变换； 花键轴的滑 套上的可另设一个或几个单向器， 变换其正向转动方向即原反相变正向（倒个过反方向安装， 即调转一百八十度方向安装） ， 花键轴及滑套反向转动将带动一个或几个单向器正向转动并 使其单向器对应的倒档齿轮转动， 即实现倒档。
附图说明
图 1是本发明新式自动变速器的主体结构示意图；
图 2为变速滑套的结构详图。
附图标记说明：
图 1中： 1、 外壳； 2、 变速仓； 51、 差速第一动力输出轴； 52、 差速第二动力输出轴； 4221、 4222， 总成盖； 1211、 电机转子轴支撑轴承或兼作行星架支撑轴承； 1212行星架轴承； 216、 行星架支撑架； 3、 电机仓； 33、 电机转子轴支撑轴承； 31、 电机定子； 32、 电机转子 轴， 同时为变速仓的动力输入兼变速轴； 260、 拉索电机； 261、 变档拉索； 270、支撑（压力） 弹簧； 221、 222， 支撑圆环； 201、 202、 203， 改型的单向器； 251、 252、 253， 行星齿轮； 111、 112、 113， 齿圈； 211、 212、 213、 214、 215， 推力轴承； 231、 232、 233， 档位太阳轮 齿轮； 28、 差速器； 12、 行星架； 101、 102、 103， 支撑动力 （差速） 输出轴轴承,； 6、 支撑 弹簧垫圈； 7、 变速滑套总成； 71、 72、 73、 74， 锁紧螺丝； 图 2中： 21、 滑套突起； 220、 滑套挡片； 23、 22, 滑套平底； 24、 滑套定位花键； 25、 滑套滑动花键； 261、 262、 263、 354, 滑套连接内、 外螺纹； 271、 272, 锁定螺丝孔； 281、 282， 拉索固定螺丝 （带孔）； 291、 292, 拉索垫片； 201、 202, 拉索穿孔； 210、 滑套上拔叉 槽或拉环槽； 211、滑套上（拉环槽内）的拉环； 301、 302， 拉索压紧螺母； 31、 32， 过渡（支 撑） 薄套； 33、 34， 过渡薄套上锁定螺丝通孔； 35、 36， 推力轴承。
具体实施方式
下面结合附图， 对本发明做进一步的详细描述。
该总成为满足整车性能提高、 成本降低的要求， 采用新型离合、 滑动等部件， 对变速原 理与控制方式进行了设计突破， 实现了自动变速的轻型、 可靠与低成本。 本发明一个重要实 施例是电机与变速器的高度集成， 总成含自动变速器及动力输入（含电动机）、输出连接件为 一体的新型自动变速桥， 可用作纯电动汽车和混合动力汽车的前桥或后桥。 此总成可附带差 速器总成 （含动力输出轴）、 桥体 （桥壳， 可含内外球笼和悬挂支撑件）。 如在动力输入轴处 接入内燃机动力输出轴 （轮）， 即为内燃机自动变速桥， 可用于汽车和混合动力电动车； 如在 动力输入轴处接入电动机， 即为电动自动变速桥， 可用于纯电动 （汽） 车和混合动力 （汽） 车。
本发明提供了一种车用自动变速驱动桥总成， 动力接入部件即动力输入可为齿轮或 （电 机） 花键轴， 动力输出为差速输出， 自动变速器部分包括系列改型单向器组件， 其中有以单 向器内环形式分别与各单向器接触、 可横向沿花键滑动的滑套组件和变速操纵部分， 如拉环 等， 以及变速机构， 即两排以上的可输出不同速度的改型行星排结构组件（含齿圈、 行星轮、 行星架、 太阳轮） 或平行轴式变速齿轮组件为一体的动力总成。
优选地， 变速器可与电机做成一体， 即变速仓 2与电机仓 3共用一个外壳 1。 若电机内 转， 电机输出轴即变速器动力输入轴 32， 为同一空轴， 空轴内可通过动力 (差速)输出花键轴 51， 52； 也可电机外转， 则外转子与齿圈或行星架连接； 电机通过外壳与变速部分的油孔连 接， 以利散热； 也可以外壳水冷或机内吹风冷却。
优选地， 此总成可另附带减速器， 桥体 （桥壳)， 桥体可含内外球笼和悬挂支撑基础连接 件。
改型行星排结构组件的太阳轮、 行星架和齿圈均可为动力输入部件、 动力输出部件和固 定部件。
优选地， 改型行星排结构组件的太阳轮 231、 232、 233为动力输入部件， 行星架 12为动 力输出部件， 齿圈 111、 112、 113 固定在同一外壳上， 即行星排的齿圈外壁层是一整体圆圈 外壳 1。 优选地，行星排的各齿圈由其内壁上轴向间隔的同心但半径、齿顶圆不等的几圈齿圈 111、 112、 113轴向排列在此整体圆圈内， 对应啮合几组齿圈内的行星齿轮 251、 252、 253； 这几 组行星齿轮由同一个行星架 12固定， 各档组行星齿轮 251、 252、 253的齿形是不同的， 有大 小， 齿数也是不同的， 由传输比决定， 行星架一端通过轴承 1211固定在电机外壳即总成的间 隔壁上， 或通过推力轴承 215和行星架支撑架 216与此间隔壁支撑固定， 一端与动力输出的 差速器 28相连， 差速器 28另一端通过轴承 1212固定在外壳的另一端； 行星齿轮 251、 252、 253 内侧与其对应档的太阳轮 231、 232、 233啮合， 各档太阳轮 231、 232、 233也是齿形大 小、 齿数多少不同； 太阳轮内壁又各有单向器 201、 202、 203外环与之相连固定； 行星排的 齿圈外壁层与电机外壳为一有间隔壁的整体结构（内分电机仓 3与变速器仓 2两个不同仓室）。
其总成由 3层以上 （含三层） 的同心的 （花键） 轴、 套、 环、 圈组成 。
优选地， 自动变速器部分的系列改型单向器组件， 其中有以单向器内环形式分别与各改 型的单向器内部接触、 可横向沿花键滑动的变速滑套总成 7， 此滑套组件穿行在各太阳轮内 的单向器的滚子 （锲块） 内， 相当于各单向器内环位置， 为一整体的、 中间带有径向膨大为 圆柱形滑套突起 21、 突起两侧变细的下凹部分 23、 22上又有可沿滑套外径横切轴向、 沿滑 套外径滑转的过渡 （支撑）薄套 （或轴套， 滑动轴承） 31、 32， 其外径与圆柱突起 21的外径 相同； 薄套 31、 32和突起 21外径均可与各档的无内环的单向器内的滚子 （锲块） 接触、 同 向同步转动、 反向相互滑离、 并沿其内侧横向滑动。
优选地， 滑套平底部分对应的单向器 201、 203虽也可正向转动 但其内的楔块 （滚子） 内侧面与其对应的滑套上的平底 23、 22不直接接触而是通过平底上的轴 （薄） 套 31、 32间 接接触， 则单向器 201、 203与平底 23、 22不同步转动， 单向器 201、 203对应的外环上齿轮 231、 233当然无法同步转动与输出动能， 只是随同与其啮合的行星齿轮空转。
优选地， 滑套 7在沿花键轴 32轴向滑动时根据控制要求在某一位置停下， 此时滑套上的 突起 21可对应接触某一特定单向器比如 202， 滑套 7及突起 21正向转动可带动对应接触的 特定单向器 202同步正向转动， 反向转动二者则滑套 7和特定单向器 202滑离； 当花键轴 32 正向转动且滑套 7同步转动， 滑套上的突起 21及其对应接触的特定单向器 202同步转动， 该 特定单向器 202外环上固定的某一档位的高速齿（太阳）轮或低速齿（太阳）轮也同步转动， 与该高速齿轮或低速齿轮啮合的输出齿轮 （圈） 带动后桥进行高档或低档运转。
优选地， 当需变档时， 首先瞬时关断动力， 横向抽动滑套 7， 使滑套突起接触的单向器 变化， 与之相连的某档位齿轮也相应变化。
优选地， 根据操作者的意愿手动操作， 或根据事先设定的软件程序， 在运行中根据速度 变化或操作者的意愿操作开关， 由计算机输出瞬时关断动力、 驱动电磁铁动作信号， 花键轴 32上滑套 7及其上的突起 21在压力弹簧 270的推动和拨叉或拉环 211拉索 261的作用下滑 动， 实现滑套带动档位齿轮的变换， 达到其升降速的目的。
优选地，控制滑套及滑套上的突起 21在拨叉或拉环 211拉索 261的作用下滑至对应单向 器之外的空当， 从而不带动任何单向器转动， 以实现机器空档。
优选地， 花键轴 32的滑套 7上的某一单向器的正向转动方向相反， 花键轴及滑套反向转 动带动一个或几个单向器正向转动并使其单向器对应的倒档齿轮转动,即实现倒档。
拉索 261对滑套拉环 211的作用， 既可手动拉动， 也可用电动拉动； 弹簧 270对拉环 211 的作用， 既可推力， 也可拉力； 滑套既可用拉环拉索拉动， 也可用拨叉拨动。
滑套 7在拉索 261与弹簧 270的作用下左右滑动， 机器也就实现变速。
优选地， 此滑套 7在拉索 261、 拉环 211的作用， 既可手动拉动， 也可用电动吸力开关。 本领域的技术人员在不脱离权利要求书确定的本发明的精神和范围的条件下， 还可以对 以上内容进行各种各样的修改。 因此本发明的范围并不仅限于以上的说明， 而是由权利要求 书的范围来确定的。

Claims

权利要求书：
1. 一种车用自动变速桥总成， 其特征在于： 动力输入轴延伸至变速仓中， 在变速仓中的动力 输入轴上设置有变速机构， 所述变速机构包括变速滑套总成、 以变速滑套总成充当其内环的 改型的单向器、 档位太阳齿轮、 行星齿轮、 行星架以及齿圈， 档位太阳齿轮、 行星齿轮以及 齿圈或平行轴式变速齿轮组件构成固定传输比的机构， 所述变速滑套总成能够与改型的单向 器匹配。
2. 根据权利要求 1所述的总成， 其特征在于： 所述变速滑套总成分别与各单向器内部接触、 可横向沿动力输入轴花键滑动。
3. 根据权利要求 1-2任意一项所述的总成， 其特征在于： 所述变速机构通过输出齿轮或输出 轴直接输出动力， 或者通过差速器驱动第一、 第二动力输出轴差速转动， 所述动力输入轴为 空心轴， 所述第一动力输出轴穿过所述动力输入轴内部。
4. 根据权利要求 1-2任意一项所述的总成，其特征在于：所述固定传输比的数量至少为二个。
5. 根据权利要求 1 所述的总成， 其特征在于： 所述改型的单向器位于变速滑套总成外侧， 所述变速滑套总成能够在所述动力输入轴和所述改型的单向器之间沿动力输入轴滑动。
6. 根据权利要求 1所述的自动变速桥总成,其特征在于:变速器可与电机做成一体，电机内转， 电机输出轴即变速器动力输入轴； 电机外转， 则外转子与齿圈或行星架连接。
7. 根据权利要求 1所述的自动变速总成桥， 其特征在于： 此总成可另附带桥体或桥壳， 桥壳 或桥体可含内外球笼和悬挂支撑基础连接件。
8. 根据权利要求 1 所述的自动变速桥总成， 其特征在于： 太阳轮为动力输入部件， 行星架 为动力输出部件， 齿圈外壁层是一整体圆圈， 为固定的外壳的一部分， 外壳内部分电机仓与 变速器仓。
9. 根据权利要求 1所述的自动变速桥总成， 其特征在于： 太阳轮为动力输入部件， 行星架和 齿圈中的一个作为动力输出部件， 另外一个作为固定部件； 或者齿圈为动力输入部件， 太阳 轮和行星架中的一个作为动力输出部件， 另外一个作为固定部件； 或者行星架为动力输入部 件， 太阳轮和齿圈中的一个作为动力输出部件， 另外一个作为固定部件。
10. 根据权力要求 1 所述的自动变速桥总成， 其特征在于： 所述的变速滑套总成包括滑套和 拉环以及拉索、 或滑套以及拨叉； 所述拉环、 拉索既可手动拉动， 也可用电动拉动； 所述的 变速滑套总成包括弹簧， 弹簧套在输入轴上， 对拉环的作用， 既可推力， 也可拉力， 滑套也 可用拨叉拨动。
11. 根据权力要求 1所述的自动变速桥总成， 其特征在于： 所述的变速滑套总成包括滑套、 拉环以及丝杠； 所述丝杠用电驱动。
PCT/CN2014/083799 2013-08-08 2014-08-06 一种车用自动变速桥总成 WO2015018341A1 (zh)

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