CN108980337A - Two-speed automatic transmission and its control method - Google Patents

Two-speed automatic transmission and its control method Download PDF

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Publication number
CN108980337A
CN108980337A CN201810752291.8A CN201810752291A CN108980337A CN 108980337 A CN108980337 A CN 108980337A CN 201810752291 A CN201810752291 A CN 201810752291A CN 108980337 A CN108980337 A CN 108980337A
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CN
China
Prior art keywords
gear
synchronizer
speed
power reception
engagement
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Granted
Application number
CN201810752291.8A
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Chinese (zh)
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CN108980337B (en
Inventor
石刚
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Lvchuan (Beijing) Automotive Technology Co.,Ltd.
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Green Transmission (beijing) Technology Co Ltd
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Priority to CN201810752291.8A priority Critical patent/CN108980337B/en
Publication of CN108980337A publication Critical patent/CN108980337A/en
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Publication of CN108980337B publication Critical patent/CN108980337B/en
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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/02Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used
    • F16H61/0202Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric
    • F16H61/0204Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal
    • F16H61/0213Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing characterised by the signals used the signals being electric for gearshift control, e.g. control functions for performing shifting or generation of shift signal characterised by the method for generating shift signals
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H3/00Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/08Toothed 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
    • F16H3/12Toothed 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 means for synchronisation not incorporated in the clutches
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36Inputs being a function of speed
    • F16H59/38Inputs being a function of speed of gearing elements
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H59/00Control inputs to control units of change-speed-, or reversing-gearings for conveying rotary motion
    • F16H59/36Inputs being a function of speed
    • F16H59/46Inputs being a function of speed dependent on a comparison between speeds
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H61/00Control functions within control units of change-speed- or reversing-gearings for conveying rotary motion ; Control of exclusively fluid gearing, friction gearing, gearings with endless flexible members or other particular types of gearing
    • F16H61/26Generation or transmission of movements for final actuating mechanisms
    • F16H61/28Generation or transmission of movements for final actuating mechanisms with at least one movement of the final actuating mechanism being caused by a non-mechanical force, e.g. power-assisted
    • F16H61/30Hydraulic or pneumatic motors or related fluid control means therefor
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16HGEARING
    • F16H2200/00Transmissions for multiple ratios
    • F16H2200/0021Transmissions for multiple ratios specially adapted for electric vehicles

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

Abstract

The invention discloses a kind of two-speed automatic transmissions of single clutch, it can be used for electric car, it includes power reception portion, power output portion and speed ratio converter section, speed ratio converter section includes unilateral bearing and second gear clutch, and under unilateral bearing engagement state, rotary driving force passes to power output portion with the first rotating ratio, at this time, if the revolving speed in power reception portion reaches at or above the first shift rate, second gear clutch engagement, unilateral bearing disengages automatically;Under second gear clutched state, rotary driving force passes to power output portion with the second rotating ratio, at this point, if second gear throw-out-of clutch, unilateral bearing engages automatically when the revolving speed in power reception portion reaches or shift gears less than second rate.The present invention, which only controls a clutch, can be realized two gears, and does not need oil pump when one keeps off and reverses gear and support, reduces pump oil loss, improves course continuation mileage.

Description

Two-speed automatic transmission and its control method
Technical field
The present invention relates to the automatic transmission of automobile and the control methods of automatic transmission.Fluid drive of the invention Device belongs to the automatic transmission of single clutch, is mainly used in electric car.
Background technique
Currently, pure electric automobile mainly selects to carry single gear retarder, although simple, the small in size, quality with structure The advantages that light and at low cost, but there is also following disadvantages.First, it is higher to driving motor performance requirement.Due to driving motor Generally high-speed motor then requires for the contradiction between climbing, accelerating ability demand and the max. speed in balancing when low speed Driving motor possesses higher driving torque, thus then increases the volume and cost of driving motor;Second, electricity under Part load The efficiency of machine working region is lower.Under the premise of meeting dynamic property demand, single transmission ratio is difficult to ensure motor long-term work In high efficiency region, especially under highest, minimum speed and low load condition, driving motor efficiency can be greatly reduced, seriously Vehicle-mounted electric energy is wasted to reduce course continuation mileage.Therefore, the power of pure electric automobile can be promoted by increasing gear number Property and economy, reduce to the performance requirement of driving motor and increase course continuation mileage.
There are mainly two types of forms for the pure electric automobile two-speed automatic transmission of mainstream at present, the first is the two of AMT form Speed automatic transmission, the two-speed automatic transmission of this form have many advantages, such as it is at low cost, high-efficient, do not need hydraulic oil pump, But exist shift there are power interruption, smooth gear shifting it is bad, to the high fatal defects of motor requirement, therefore can not be in pure electric vehicle It is promoted the use of on passenger car.It is for second the two-speed automatic transmission of DCT or AT form, the two-speed automatic transmission tool of this form Have the advantages that shift gears power failure-free, smooth gear shifting is good, matched with motor simply, durability it is good.But the disadvantage is that need according to Powerful electronic oil pump, electronic oil pump longevity of service power consumption is big, reduces the course continuation mileage of pure electric automobile.
Summary of the invention
(1) technical problems to be solved
The present invention is intended to provide a kind of single clutch two-speed automatic transmission for electric car, is slowed down with solving single gear The problem of device dynamic property and economy cannot be taken into account.
(2) technical solution
In order to solve the above technical problems, the present invention mainly proposes a kind of two-speed automatic transmission comprising power reception portion, Power output portion and speed ratio converter section, power reception portion are used to receive rotary driving force from outside, and speed ratio converter section is used for institute It states rotary driving force and power output portion is passed to the first rotating ratio or the second rotating ratio, power output portion is for converting speed ratio The rotary driving force of portion's transmitting is exported to the wheel shaft of automobile, and the speed ratio converter section includes the one-way shaft for being coupled to power reception portion Hold with second gear clutch, also, under unilateral bearing engagement state, the rotary driving force passes to power with the first rotating ratio Output section, at this point, if second gear clutch engages, one-way shaft when the revolving speed in power reception portion reaches at or above the first shift rate Hold automatic disengagement;Under second gear clutched state, the rotary driving force passes to power output portion with the second rotating ratio, At this point, if second gear throw-out-of clutch, unilateral bearing connects automatically when the revolving speed in power reception portion reaches or shift gears less than second rate It closes;The second shift rate is less than the first shift rate.
According to the preferred embodiment of the present invention, the engaging force of the second gear clutch is provided by oil pressure, the oil pressure by Oil pump provides, and the torque in the power output portion is higher, then the oil pressure that the oil pump provides is higher.
According to the preferred embodiment of the present invention, the oil pump is mechanical oil pump.
According to the preferred embodiment of the present invention, the engagement of the second gear clutch and disengagement are by an electrichydraulic control assembly Control.
According to the preferred embodiment of the present invention, the speed ratio converter section further includes synchronizer, the power output portion packet Engagement gear ring is included, power reception portion can be engaged or be separated with the engagement gear ring by the synchronizer.
According to the preferred embodiment of the present invention, when the synchronizer make power reception portion with it is described engage gear ring engagement and When power reception portion reversely rotates, the engagement gear ring drives power output portion and power reception portion synchronous rotary, is formed It reverses gear.
According to the preferred embodiment of the present invention, when the synchronizer make power reception portion with it is described engage gear ring engagement but When power reception portion rotates in the forward direction, the engagement gear ring drives power output portion and power reception portion synchronous rotary, is formed One gear.
According to the preferred embodiment of the present invention, when power reception portion rotates in the forward direction and revolving speed rises to the first synchronizer speed When rate, the synchronizer separates power reception portion with the engagement gear ring;When power reception portion rotate in the forward direction and revolving speed decline When to the second synchronizer rate, the synchronizer makes the rotation in power reception portion engage gear ring engagement with described.
According to the preferred embodiment of the present invention, the synchronizer is with the engagement for engaging gear ring and disengagement by an electricity Son shift assembly control.
According to the preferred embodiment of the present invention, the second synchronizer rate is less than the first synchronizer rate.
According to the preferred embodiment of the present invention, the first synchronizer rate less than first shift rate, described second Synchronizer rate is less than the second shift rate.
According to the preferred embodiment of the present invention, the power output portion includes a gear driving gear and second gear driving tooth Wheel, a gear driving gear are fixedly connected with the outer ring of unilateral bearing, and engagement gear ring is fixed on a gear driving gear;Second gear is actively Gear is fixed in the Partner of second gear clutch.
According to the preferred embodiment of the present invention, the power reception is a shaft, a gear driving gear and second gear The equal free end bearing of driving gear is in the shaft.
According to the preferred embodiment of the present invention, the power output portion further includes a gear driven gear and second gear passive tooth Wheel is engaged in a gear driving gear and two gear driving gear using as transmission gear respectively.
According to the preferred embodiment of the present invention, the power output portion further includes gear of output end, passive with a gear Gear, second gear driven gear rotate synchronously.
According to the preferred embodiment of the present invention, the gear of output end, a gear driven gear, second gear driven gear are solid It is connected on a jackshaft.
Meanwhile the present invention also proposes a kind of control method of corresponding two-speed automatic transmission, the two-gear automatic speed changing Device includes power reception portion, power output portion and speed ratio converter section, and the speed ratio converter section includes being coupled to power reception portion Unilateral bearing and second gear clutch, which comprises
Power reception portion receives rotary driving force from outside;Speed ratio converter section is by the rotary driving force with the first rotating ratio Or second rotating ratio pass to power output portion, in which: under unilateral bearing engagement state, if the revolving speed in power reception portion reaches Or when being higher than the first shift rate, engaging second gear clutch, unilateral bearing disengages automatically;In second gear clutched state Under, if the revolving speed in power reception portion reaches or shift gears less than second rate, make second gear throw-out-of clutch, unilateral bearing connects automatically It closes.Power output portion exports the rotary driving force that speed ratio converter section transmits to the wheel shaft of automobile.
According to the preferred embodiment of the present invention, the engagement of the second gear clutch is controlled by an electrichydraulic control assembly With disengagement.
According to the preferred embodiment of the present invention, the speed ratio converter section further includes synchronizer, the power output portion packet Engagement gear ring is included, power reception portion is engaged or separated with the engagement gear ring by the movement by controlling synchronizer.
According to the preferred embodiment of the present invention, when the synchronizer make power reception portion with it is described engage gear ring engagement and When power reception portion reversely rotates, the engagement gear ring drives power output portion and power reception portion synchronous rotary, is formed It reverses gear.
According to the preferred embodiment of the present invention, when the synchronizer make power reception portion with it is described engage gear ring engagement but When power reception portion rotates in the forward direction, the engagement gear ring drives power output portion and power reception portion synchronous rotary, is formed One gear.
According to the preferred embodiment of the present invention, when power reception portion rotates in the forward direction and revolving speed rises to the first synchronizer speed When rate, the synchronizer separates power reception portion with the engagement gear ring;When power reception portion rotate in the forward direction and revolving speed decline When to the second synchronizer rate, the synchronizer makes the rotation in power reception portion engage gear ring engagement with described.
According to the preferred embodiment of the present invention, the synchronizer and the engagement are controlled by an electric gear change assembly The engagement and disengagement of gear ring.
According to the preferred embodiment of the present invention, the second synchronizer rate is less than the first synchronizer rate.
According to the preferred embodiment of the present invention, the first synchronizer rate less than first shift rate, described second Synchronizer rate is less than the second shift rate.
(3) beneficial effect
Compared with the prior art, the invention has the following beneficial effects:
(1) present invention realizes two speed ratios, so that a gear dynamic property is stronger, motor speed is lower when second gear high speed, So that motor working efficiency is higher, the course continuation mileage of pure electric automobile is improved.
(2) present invention uses the combination of single clutch and synchronizer and unilateral bearing, therefore at low cost.
(3) structure that the present invention is applied in combination using single clutch and synchronizer and unilateral bearing, so that one keeps off and reverses gear When do not need operation of oil pump support.The efficiency losses for reducing oil pump pump oil improve the course continuation mileage of pure electric automobile.
(4) this hair has 1 clutch of control that two gears can be realized, and electronic controlling strategies are simpler, hydraulic behaviour Control system is simpler, and cost is lower.
(5) only one clutch needs oil pump pump oil to support in the present invention, reduces oil pump volume and power loss, subtracts Work oil mass is lacked, has improved pure electric automobile speed automatic transmission working efficiency, to increase the continuation of the journey of pure electric automobile Mileage.
(6) for the present invention when oil pump breaks down, a gear is still can be used and traveling of reversing gear in pure electric automobile, it is ensured that security row Sail go back to maintenance station.
(7) for the present invention in most of electronic system malfunction, a gear is still can be used and traveling of reversing gear in pure electric automobile, it is ensured that Drive safely back maintenance station.
Detailed description of the invention
Fig. 1 is the component design drawing of one embodiment of two-speed automatic transmission of the invention;
Fig. 2 is the flow chart of the control method of the embodiment of Fig. 1.
Specific embodiment
Generally speaking, proposed by the present invention is a kind of two automatic transmission kept off, i.e., there are two forward gears for speed changer tool Position, i.e. " gear " and " second gear ", " gear " are bottom gear, and " second gear " is top gear.Certainly, in the specific implementation, of the invention Automatic transmission can also realize " reversing gear ".
Although present invention is preferably applied in pure electric automobile, this is not meant to that the present invention may not apply to Use is not precluded in the automobile of non-pure electric vehicle, such as oil-electric vehicle or traditional fuel power automobile, the present invention, this It is because which kind of engine is the present invention, which be not intended to limit by, provides the power of rotation.In addition, the present invention be not limited in four-wheel with On automobile, in fact, the present invention is in being applied to three-wheel, two-wheeled or wheelbarrow there is no any technology barrier.Namely It says, automatic transmission of the invention can actually be applied to the vehicles of two forward ranges of any required offer.
Automatic transmission of the invention may include power reception portion, power output according to saying in the division of functional component Portion and speed ratio converter section, power reception portion are used to receive rotary driving force from outside, and speed ratio converter section is used to drive the rotation Power passes to power output portion, and power output portion is for exporting the rotary driving force that speed ratio converter section transmits to the wheel of automobile Axis.Since the present invention is the automatic transmission of two gears, speed ratio converter section can be enough with the first rotating ratio or the second rotating ratio Transmit rotary driving force." the first rotating ratio " and " the second rotating ratio " herein refer to power output portion and power reception portion it Between rotating ratio, or for driving ratio.In the description of the invention, " the first rotating ratio " can be defined and be greater than " the second revolving speed Than ", i.e., it respectively corresponds " gear " and " second gear ".
Power reception portion and power output portion of the invention is single.Power reception portion is without being particularly limited to, Ren Heneng Receiving any part that rotary driving force and revolving speed change with driving part can be used as power reception portion.But usually, Power reception portion is embodied as a shaft, receives rotary driving force from such as motor.But the present invention is not limited to shafts Specific structure.
Crucial innovation of the invention is to propose a kind of speed ratio converter section structure of innovation, specifically comprising Be coupled to the unilateral bearing and second gear clutch in power reception portion, wherein second gear clutch be only used for " one gear " and The clutch converted between " second gear ", therefore the present invention can be described as single clutch structure.
The structure of unilateral bearing is known technology, its working principle is that: torque can only from inner ring to outer ring unidirectional delivery, It cannot be transmitted from outer ring to inner ring, inner ring and power reception portion are affixed, and outer ring and power output portion are affixed.Therefore, when torque side To (or being referred to as to engage) when inner ring being made to drive outer ring, inner ring and outer ring is rotated synchronously, and can realize torque transfer;And works as and turn When square direction makes a kind of outer ring driving inner ring (and non-genuine driving, only tendency), pass is freely rotated in inner ring and outer ring formation System's (or to disengage), that is, cannot achieve torque transfer.According to the present invention, under unilateral bearing engagement state, by power reception The received rotary driving force in portion passes to power output portion with the first rotating ratio, i.e. " gear ".At this point, if power reception portion turns When speed reaches at or above the first shift rate, the engagement of second gear clutch, unilateral bearing disengages automatically, completes from " gear " to " two The automatic conversion of gear ".And under second gear clutched state, it is defeated that the rotary driving force with the second rotating ratio passes to power Portion out, as " second gear ", at this point, if second gear clutch is de- when the revolving speed in power reception portion reaches or shift gears less than second rate It opens, unilateral bearing engages automatically, completes the automatic conversion from " second gear " to " gear ".
In view of the efficiency of gear-change operation in practical driving procedure, the preferably second shift rate is less than first shift Rate.
Realize that the principle of above-mentioned gear conversion is to cooperate between unilateral bearing and second gear clutch.Therefore, this hair As long as bright control second gear clutch engagement, the revolving speed decline in power reception portion, at this point, the inner ring revolving speed of unilateral bearing is under Drop, when torque direction is to drive inner ring by outer ring by inner ring driving outer ring variation, thus inner ring and outer ring is disengaged, complete " one Gear " arrives the automatic conversion of " second gear ".Opposite, as long as the present invention is when control second gear throw-out-of clutch, the revolving speed in power reception portion It increases, at this point, the inner ring revolving speed of unilateral bearing increases, when torque direction is driven by the variation of outer ring driving inner ring by inner ring Thus outer ring, inner ring and outer ring engage, complete the automatic conversion of " second gear " to " gear ".
As it can be seen that the present invention, which need to only control the engagement of second gear clutch and disengagement, to shift gears automatically.And second gear clutch The control of device can then realize by the prior art, this makes structure of the invention compact and highly reliable.In the present invention, it is preferred that two The engagement for keeping off clutch is provided with disengagement by hydraulic pressure, specifically oil pressure can be provided by an oil pump, by the way that oil pump to be coupled to Power output portion (or arbitrarily being can provide in the shaft of revolving speed in speed changer), the torque in power output portion is higher, then the oil pump The oil pressure of offer is higher.Preferably, the oil pump is mechanical oil pump, and structure thus can be made simple and reduce cost.
According to the preferred embodiment of the present invention, two-gear transmission can also additional realization reverse gear.It is of the invention as a result, The speed ratio converter section preferably further includes synchronizer, and power output portion further includes engagement gear ring.Power is connect by synchronizer Receipts portion engages or separates with engagement gear ring, and when engaged, power and power output portion rotate synchronously, and realizes driving when reversing gear. Need to illustrate when, when reversing gear, since the rotation direction of rotary driving force is in inverted status, unilateral bearing is in de- automatically Open state.And second gear clutch is also controlled by disengaged condition at this time.That is, when the synchronizer makes power reception portion Gear ring engagement is engaged and when power reception portion reversely rotates with described, and the engagement gear ring drives power output portion and the power Receiving unit synchronous rotary is now in " reversing gear " working condition.
According to the preferred embodiment of the present invention, when electric car is static, speed changer can not prejudge driver's next step Operation is to hang forward gear or reverse gear.In order to reverse gear switch when it is more quick, the present invention rotates in the forward direction in power reception portion And revolving speed in a certain range (normally below some value) when, control synchronizer in advance for power reception portion and the soldered tooth Circle engagement.In this way, when driver hangs forward gear by static or low speed, when power reception portion rotates in the forward direction, electric car can be One gear, which advances, to travel;When driver is reversed gear by static or low speed extension, when power reception portion reversely rotates, electric car can fallen Gear falls back traveling.The advance or retroversion starting of electric car are more quick, without waiting for engagement gear ring and the power reception portion Engaging process.
A kind of specific embodiment is, when power reception portion rotates in the forward direction and revolving speed rises to the first synchronizer rate When, the synchronizer separates power reception portion with the engagement gear ring;When power reception portion rotates in the forward direction and revolving speed drops to When the second synchronizer rate, the synchronizer makes the rotation in power reception portion engage gear ring engagement with described.Synchronizer with it is described The engagement and disengagement for engaging gear ring can be controlled by an electric gear change assembly.In view of the optimization of actual operating efficiency, institute Stating the second synchronizer rate can be set to less than the first synchronizer rate.
Further, since unilateral bearing is unable to the characteristic of back transfer torque, reverses gear and synchronizer is needed to be in joint shape always State, therefore the output par, c with a gear common power output section of reversing gear, therefore the first synchronizer rate should be set and be less than First shift rate, the second synchronizer rate is less than the second shift rate.
For power output portion, since there are two forward ranges for present invention design, and the output par, c reversed gear is preferred Ground can share the output par, c of a gear, and therefore, there are two driving gear, i.e., one gears for power output portion of the invention preferably tool Driving gear and two gear driving gear, a gear driving gear is fixedly connected with the outer ring of unilateral bearing, and is engaged gear ring and be fixed in On one gear driving gear;Two gear driving gear is fixed in the Partner of second gear clutch.A gear driving gear can drive as a result, By unidirectional bearing outer ring forward driving when dynamic portion rotates forward, it is back-driven into driving portion reversion via engagement gear ring.Second gear master Moving gear is driven at " second gear " by second gear clutch.Preferably, a gear driving gear and the equal free end bearing of two gear driving gear In the shaft as power reception portion.
In addition, preferably, power output portion of the invention correspondingly has a gear driven gear, second gear quilt Moving gear is engaged in a gear driving gear and two gear driving gear using as transmission gear respectively.And as power output end, It may also include the gear of output end rotated synchronously with a gear driven gear, second gear driven gear, gear of output end and differential mechanism tooth Wheel engagement, and the structure of differential mechanism to wheel shaft is the prior art, is no longer described in detail in this specification.Gear of output end, one Gear driven gear, second gear driven gear can be fixed on a jackshaft, be achieved in the synchronous rotation of three.
Certainly, in order to accommodate the above-mentioned all parts of speed changer of the invention, speed changer can also have a shell, described Shaft as power reception portion and the jackshaft as intermediate transfer power can be supported on shell and be formed certainly with shell By rotating.
To make the objectives, technical solutions, and advantages of the present invention clearer, below in conjunction with specific embodiment, and reference Attached drawing, the present invention is described in further detail.
Fig. 1 is the component design drawing of one embodiment of two-speed automatic transmission of the invention.As shown in Figure 1, the implementation Example is embodied as the automatic transmission of a pure electric automobile comprising input shaft 1, one keep off driving gear 2, two gear driving gear 3, Jackshaft 4, second gear driven gear 5, gear of output end 6, differential gear 7, one keep off driven gear 8, differential assembly 9, second gear Clutch drive end 16, second gear clutch Partner 17, unilateral bearing 12, synchronizer assembly 13, splined hub 14, engagement gear ring 15, mechanical oil pump assembly 18, shell 19, electric gear change assembly 20 and electrichydraulic control assembly 21.
Wherein, input shaft 1 is connect with the driving motor of external pure electric automobile by spline, the both ends difference of input shaft 1 Through bearing support on shell 19, and relationship is freely rotated with the formation of shell 19.The shell and speed change of mechanical oil pump assembly 18 Device shell 19 is bolted to connection.18 inner rotator of mechanical oil pump assembly is unidirectionally connect by unilateral bearing with input shaft 1. When external drive motors are positive direction of rotation, input shaft 1 drives mechanical 18 inner rotator synchronous rotary of oil pump assy.It is external Driving motor is when reversely rotating direction, and 18 inner rotator of oil pump assy and the formation of input shaft 1 rotate freely relationship.
Engagement gear ring 15 is integrated processing or welding etc. with a gear driving gear 2 and is fixedly connected with relationship.Splined hub 14 with it is defeated Enter axis 1 to be fixedly connected by spline, and input shaft 1 is followed to rotate synchronously.Synchronizer assembly 13 can be in electric gear change assembly 20 Control under move, thus its can by splined hub 14 and engagement gear ring 15 link together, formed synchronous rotation relationship.
The inner ring of unilateral bearing 12 is that interference fit is fixedly connected, and input shaft 1 is followed to rotate synchronously with input shaft 1.It is single It is fixedly connected to the outer ring of bearing 12 with a gear driving gear 2 for interference fit.Unilateral bearing 12 is known currently on the market produces Product, its working principle is that torque is from inner ring to outer ring unidirectional delivery.I.e. when torque direction is that inner ring drives outer ring, inner ring and outer Circle rotates synchronously, and can realize torque transfer;When torque direction is that outer ring drives inner ring, inner ring and outer ring is disengaged and is formed certainly By rotation relation, torque transfer cannot achieve.
Two gear driving gear 3 is supported on input shaft 1 by bearing, and relationship is freely rotated with the formation of input shaft 1.Second gear Clutch drive end 16 is connected to one with input shaft 1 by welding or be bolted etc., and follows input shaft 1 synchronous Rotation.
The both ends of jackshaft 4 pass through bearing support on case of transmission 19 respectively, and are formed certainly with case of transmission 19 By rotation relation.One gear driven gear 8 by being integrally machined, welding, spline or arbitrarily be fixedly connected mode and jackshaft 4 fixation Connection, and rotated synchronously with jackshaft 4.Second gear driven gear 5 by being integrally machined, welding, spline or any side of being fixedly connected Formula is fixedly connected with jackshaft 4, and is rotated synchronously with jackshaft 4.Gear of output end 6 by be integrally machined, weld, spline or appoint Meaning is fixedly connected with mode and is fixedly connected with jackshaft 4, and rotates synchronously with jackshaft 4.Differential gear 7 and differential assembly 9 It is bolted to connection, and is rotated synchronously with differential assembly 9.Differential assembly 9 is by bearing support in case of transmission On 19, and relationship is freely rotated with the formation of case of transmission 19.Differential assembly 9 is known product currently on the market.
The right axle 10 and left hand side half shaft 11 of pure electric automobile pass through respectively to be connected inside spline and differential assembly 9, And it is driven and is rotated according to itself working principle by differential assembly 9.Electric gear change assembly 20 can be manipulated according to control instruction and be synchronized Device assembly 13 moves left and right.Electrichydraulic control assembly 21 can one second gear clutch drive end 16 and second gear are manipulated according to control instruction Clutch Partner 17 is closed mutually, disengages or is formed the relatively sliding rotation relation that rubs of specific rotation speeds.
The working principle for stating the speed changer of embodiment is described below.
(1) one gear working principle
When pure electric automobile original place is static, 1 revolving speed of input shaft is zero, and mechanical oil pump assembly 18 does not work.Electric gear change is total Synchronizer assembly 13 and the main Partner 16,17 of second gear clutch can not controlled 20 and electrichydraulic control assembly 21, so that synchronizer is total At 13 and the main Partner of second gear clutch 16,17 all in default conditions.Two-speed automatic transmission automatically forms a gear at this time.
When pure electric automobile is started to walk, the revolving speed of input shaft 1 is gradually risen, and mechanical oil pump assembly 18 is started to work, machinery oil Pump assembly 18 rotates the oil liquid flow pumped out and gradually increases, but flow is it is possible to too low without being able to satisfy use demand.Electronics Shift assembly 20 and electrichydraulic control assembly 21 do not control synchronizer assembly 13 and the main Partner 16,17 of second gear clutch, so that together Device assembly 13 and the main Partner of second gear clutch 16,17 are walked all in default conditions.Two-speed automatic transmission automatically forms at this time One gear.
When pure electric automobile normally travel, the revolving speed of input shaft 1 is increased to 500 revolutions per minute kinds and (does not limit 500 revolutions per minute Kind) more than, 18 rotary rpm of mechanical oil pump assembly satisfies the use demand enough the fuel-displaced flow quantity of rotary pump.Electric gear change is total Synchronizer assembly 13 and the main Partner 16,17 of second gear clutch can not controlled 20 and electrichydraulic control assembly 21, so that synchronizer is total At 13 and the main Partner of second gear clutch 16,17 all in default conditions.Two-speed automatic transmission automatically forms a gear at this time.
Mechanical oil pump assembly 18 breaks down or speed changer inner fluid deficiency causes the rotation of mechanical oil pump assembly 18 to pump out When oil liquid underfed is required with meeting the main compression of Partner 16,17 of second gear clutch.And electric gear change assembly 20 does not control together Step device assembly 13 makes synchronizer assembly 13 be in default conditions.Two-speed automatic transmission automatically forms a gear at this time.
When two-speed automatic transmission electric gear change assembly 20 or electrichydraulic control assembly 21 break down, electric gear change assembly 20 Synchronizer assembly 13 and the main Partner 16,17 of second gear clutch are not controlled with electrichydraulic control assembly 21, so that synchronizer assembly 13 With the main Partner of second gear clutch 16,17 all in default conditions.Two-speed automatic transmission automatically forms a gear at this time.
When two-speed automatic transmission forms a gear, the torque transfer route of external drive motors is successively are as follows: input shaft 1, 12 inner ring of unilateral bearing, 12 outer ring of unilateral bearing, to a gear driving gear 2, a gear driven gear 8, jackshaft 4, output end tooth Take turns 6, differential gear 7, differential assembly 9, right side and left side semiaxis 10 and 11.
When two-speed automatic transmission forms a gear, the gear ratio calculation method of two-speed automatic transmission are as follows:
Wherein: i1For the speed ratio of a gear;z2、z8、z6、z7Respectively one gear driving gear 2, one keeps off driven gear 8, output end The number of gear teeth of gear 6, differential gear 7.
(2) second gear working principle
When pure electric automobile normally travel, the revolving speed of input shaft 1 is increased to 500 revolutions per minute kinds and (does not limit 500 revolutions per minute Kind) more than, 18 rotary rpm of mechanical oil pump assembly satisfies the use demand enough the fuel-displaced flow quantity of rotary pump.Electric gear change is total Synchronizer assembly 13 can not controlled 20 so that synchronizer assembly 13 is in default conditions.Electrichydraulic control assembly 21 controls machinery oil The oil liquid oil pressure that pump assembly 18 exports makes the main Partner 16,17 of second gear clutch compress closure mutually.So that input shaft 1 turns Speed gradually decreases in the main Partner 16 of second gear clutch, 17 closing courses, and makes the revolving speed of a gear driving gear 2 lower than one The revolving speed of driven gear 8 is kept off, relationship, a gear power transmission path interruptions are freely rotated in the formation of 12 inner ring and outer ring of unilateral bearing. Two-speed automatic transmission forms second gear under the control action of electrichydraulic control assembly 21 at this time.
When two-speed automatic transmission forms second gear, the torque transfer route of external drive motors is successively are as follows: input shaft 1, Two gear driving gear 3, second gear driven gear 5, jackshaft 4, gear of output end 6, differential gear 7, differential assembly 9, right side With left hand side half shaft 10 and 11.
When two-speed automatic transmission forms second gear, the gear ratio calculation method of two-speed automatic transmission are as follows:Wherein: i2For the speed ratio of second gear;z3、z5、z6、z7Respectively two gear driving gear 3, second gear driven gear 5, defeated The number of gear teeth of outlet gear 6, differential gear 7.
(3) it reverses gear working principle
When pure electric automobile original place is static, 1 revolving speed of input shaft is zero, and mechanical oil pump assembly 18 does not work.Electrichydraulic control is total The main Partner 16,17 of second gear clutch can not controlled 21, so that the main Partner of second gear clutch 16,17 is all in default conditions. Electric gear change assembly 20 controls the movement of synchronizer assembly 13, is connected splined hub 14 and engagement gear ring 15 by synchronizer assembly 13 Together, synchronous rotation relationship is formed.Two-speed automatic transmission formation at this time is reversed gear.
Pure electric automobile reverses gear starting or when normal reverse travel, reverse rotation of the external drive motors with driven input shaft 1, Revolving speed gradually rises, and mechanical oil pump assembly 18 rotates freely under the action of unilateral bearing to work, and it is fuel-displaced to be unable to rotary pump Liquid.Electrichydraulic control assembly 21 does not control the main Partner 16,17 of second gear clutch, so that the main Partner 16,17 of second gear clutch is all In default conditions.It is mobile that electrichydraulic control assembly 21 controls synchronizer assembly 13, by synchronizer assembly 13 by 14 He of splined hub Engagement gear ring 15 links together, and forms synchronous rotation relationship.Since external input motor is to reversely rotate, pure electric vehicle vapour Vehicle travels backward, and two-speed automatic transmission formation at this time is reversed gear.
When the failure of mechanical oil pump assembly 18 or speed changer inner fluid deficiency, electric gear change assembly 20 is still controllable to be synchronized Device assembly 13 is mobile, and splined hub 14 and engagement gear ring 15 are linked together by synchronizer assembly 13, is formed to rotate synchronously and be closed System.Two-speed automatic transmission formation at this time is reversed gear.
When two-speed automatic transmission electrichydraulic control assembly 21 breaks down, the still controllable synchronizer of electric gear change assembly 20 is total It is mobile at 13, splined hub 14 and engagement gear ring 15 are linked together by synchronizer assembly 13, form synchronous rotation relationship.This When two-speed automatic transmission formation reverse gear.
When two-speed automatic transmission formation is reversed gear, the torque transfer route of external drive motors is successively are as follows: input shaft 1, Splined hub 14, synchronizer assembly 13 engage gear ring 15, a gear driving gear 2, a gear driven gear 8, jackshaft 4, output end tooth Take turns 6, differential gear 7, differential assembly 9, right side and left side semiaxis 10 and 11.
When two-speed automatic transmission formed to gear when, the gear ratio calculation method of two-speed automatic transmission are as follows:
Wherein: iRFor the speed ratio of a gear;z2、z8、z6、z7Respectively one gear driving gear 2, one keeps off driven gear 8, output end The number of gear teeth of gear 6, differential gear 7.
Illustrate the control method of the embodiment of the invention below with reference to Fig. 2:
S0: electric car powers on, the electronic controller of two-speed automatic transmission of the invention (including electric gear change assembly 20 With electrichydraulic control assembly 21) it powers on and enters standby mode.
S1: judge whether gear lever is in the position P or N (P gear or N gear).
It is then driving motor to be allowed to start;Synchronizer 13 engages, and clutch 16 disengages (default conditions);It is no, then do not allow Driving motor starting.And return step S0 state.
S2: judge whether gear lever is linked into the position D.
It is that then automatic transmission enters a gear, synchronizer 13 engages, and clutch 16 disengages (default conditions);It is no, then automatically Speed changer enters the S7 stage.
S3: judge whether speed is higher than the first synchronizer vehicle velocity Va
VaSpeed, V are judged for synchronizer stateaThe size of numerical value determines by throttle, i.e. Va=fa(throttle).Special, When throttle is 0%, VaPer hour equal to 50 kilometers.V in actual mechanical processa=fa(throttle) can be appointing for engineer's setting Meaning function.
It is that then synchronizer 13 disengages;It is no, then keep one gear state of previous step.
S4: judge whether speed is higher than the first shift vehicle velocity V1
First shift vehicle velocity V1The shift for rising second gear for a gear judges speed, V1The size of numerical value determines by throttle, i.e. V1= f1(throttle).Special, when throttle is 20%, speed V1Per hour equal to 75 kilometers.V in actual mechanical process1=f1 (throttle) can be the arbitrary function of engineer's setting.
It is that then clutch 16 engages, automatic transmission enters second gear;
It is no, then keep previous step one to keep off, and the state that synchronizer 13 disengages.
S5: judge whether speed is lower than the second shift vehicle velocity V2
V2Shift for one gear of second gear drop judges speed, V2The size of numerical value determines by throttle, i.e. V2=f2(throttle).It is special Different, when throttle is 0%, speed V2Per hour equal to 40 kilometers.V in actual mechanical process2=f2(throttle) can be work The arbitrary function of Cheng Shi setting.
It is that then clutch 16 disengages, automatic transmission enters a gear;
It is no, then keep previous step second gear state.
S6: judge whether speed is lower than the second synchronizer vehicle velocity Vb。VbSpeed, V are judged for synchronizer engagementbNumerical value it is big It is small to be determined by throttle, i.e. Vb=fb(throttle).Special, when throttle is 0%, speed VbPer hour equal to 35 kilometers.It is practical V in operating processb=fb(throttle) can be the arbitrary function of engineer's setting.
It is that then synchronizer 13 engages;
It is no, then keep previous step one to keep off, and the state that synchronizer 13 disengages.
S7: judge whether gear lever is linked into the position R (reversing gear).
It is that then automatic transmission enters R gear, synchronizer 13 engages, and clutch 16 disengages (default conditions);
It is no, then return to N or P the gear state of S1 step;
S8: judge whether gear lever has exited the position R.
It is N or P the gear state for then returning to S1 step;
It is no, then keep the R of S7 step to keep off state.
It should be noted that in above-mentioned control method, the first synchronizer vehicle velocity Va, the second synchronizer vehicle velocity Vb, first shift Vehicle velocity V1, second shift vehicle velocity V2It is fast with first synchronizer of power reception portion above-mentioned (shaft or input shaft 1) rotation respectively Rate, the second synchronizer rate, the first shift rate, the second shift rate are corresponding.That is, synchronizer state of the invention Switching, clutch state switching are all based on speed to judge.And above-mentioned correspondence is when taken turns about current revolving speed is depended on The outer diameter of tire.
By upper description it is found that two-gear transmission proposed by the present invention has following advantage compared with the existing technology:
(1) single clutch, synchronizer and unilateral bearing are applied in combination, so that the present invention is got rid of in a gear and while reversing gear Dependence to oil pump, so that two gears can be realized in the opening and closing state that electrohydraulic control system only controls a clutch Position.Also, under the fault conditions such as oil pump breaks down, oil liquid is insufficient, electrohydraulic system failure, pure electric automobile can still be adopted With a gear and traveling of reversing gear.
(2) unilateral bearing is used, so that the one torque transfer route kept off when second gear clutch drive end and Partner are closed It is automatic to disengage.
(3) mechanical oil pump with unilateral bearing is used, so that mechanical oil pump does not work when input shaft 1 inverts.
(4) synchronizer assembly structure is used, external motor is formed when reversely rotating and is reversed gear.
(5) synchronizer state of the present invention judges vehicle velocity Va, when speed is higher than VaWhen, synchronizer 13 disengages, when speed is lower than Vb When, synchronizer 13 engages.Vehicle velocity VaLess than vehicle velocity Vb, VaAnd VbBuffering matching relationship is formed, 13 state of a control of synchronizer can be maintained Stabilization, reduce synchronizer 13 state frequent switching.
(6) two speed ratios make a gear dynamic property stronger, and motor speed is lower when second gear high speed, and motor works as a result, It is more efficient, improve the course continuation mileage of pure electric automobile.
Particular embodiments described above has carried out further in detail the purpose of the present invention, technical scheme and beneficial effects Describe in detail bright, it should be understood that the above is only a specific embodiment of the present invention, is not intended to restrict the invention, it is all Within the spirit and principles in the present invention, any modification, equivalent substitution, improvement and etc. done should be included in protection of the invention Within the scope of.

Claims (25)

1. a kind of two-speed automatic transmission, including power reception portion, power output portion and speed ratio converter section, power reception portion are used for Rotary driving force is received from outside, speed ratio converter section is used to pass the rotary driving force with the first rotating ratio or the second rotating ratio Power output portion is passed, power output portion is used to export the rotary driving force that speed ratio converter section transmits to the wheel shaft of automobile, It is characterized in that:
The speed ratio converter section includes the unilateral bearing and second gear clutch for being coupled to power reception portion, also,
Under unilateral bearing engagement state, the rotary driving force passes to power output portion with the first rotating ratio, at this point, if dynamic When the revolving speed of power receiving unit reaches at or above the first shift rate, second gear clutch engagement, unilateral bearing disengages automatically;
Under second gear clutched state, the rotary driving force passes to power output portion with the second rotating ratio, at this point, if When the revolving speed in power reception portion reaches or shift gears less than second rate, second gear throw-out-of clutch, unilateral bearing engages automatically;
The second shift rate is less than the first shift rate.
2. two-speed automatic transmission as described in claim 1, which is characterized in that
The engaging force of the second gear clutch is provided by oil pressure, and the oil pressure is provided by oil pump, the torque in the power output portion Higher, then the oil pressure that the oil pump provides is higher.
3. two-speed automatic transmission as claimed in claim 2, which is characterized in that the oil pump is mechanical oil pump.
4. two-speed automatic transmission as claimed in claim 2, which is characterized in that the engagement of the second gear clutch and disengage by One electrichydraulic control assembly control.
5. two-speed automatic transmission as described in claim 1, which is characterized in that the speed ratio converter section further includes synchronizer, The power output portion include engagement gear ring, the synchronizer can by power reception portion with it is described engage gear ring engage or divide From.
6. two-speed automatic transmission as claimed in claim 5, which is characterized in that when the synchronizer makes power reception portion and institute When stating the engagement of engagement gear ring and the reverse rotation of power reception portion, the engagement gear ring drives power output portion and the power reception Portion's synchronous rotary, formation are reversed gear.
7. two-speed automatic transmission as claimed in claim 5, which is characterized in that when the synchronizer makes power reception portion and institute The engagement of engagement gear ring but power reception portion are stated when rotating in the forward direction, the engagement gear ring drives power output portion and the power reception Portion's synchronous rotary forms a gear.
8. two-speed automatic transmission as claimed in claim 7, which is characterized in that when power reception portion rotates in the forward direction and on revolving speed When rising to the first synchronizer rate, the synchronizer separates power reception portion with the engagement gear ring;When power reception portion just To rotation and when revolving speed drops to the second synchronizer rate, the synchronizer makes the rotation in power reception portion and the engagement gear ring Engagement.
9. two-speed automatic transmission as claimed in claim 8, which is characterized in that the synchronizer engages connecing for gear ring with described It closes and disengages by an electric gear change assembly control.
10. two-speed automatic transmission as claimed in claim 8, which is characterized in that the second synchronizer rate is less than first Synchronizer rate.
11. two-speed automatic transmission as claimed in claim 10, which is characterized in that the first synchronizer rate is less than first Shift rate, the second synchronizer rate is less than the second shift rate.
12. two-speed automatic transmission as claimed in claim 5, which is characterized in that the power output portion includes a gear active Gear and two gear driving gear, a gear driving gear are fixedly connected with the outer ring of unilateral bearing, and engagement gear ring is fixed in a gear master On moving gear;Two gear driving gear is fixed in the Partner of second gear clutch.
13. two-speed automatic transmission as claimed in claim 12, which is characterized in that the power reception is a shaft, described One gear driving gear and the equal free end bearing of two gear driving gear are in the shaft.
14. two-speed automatic transmission as claimed in claim 12, which is characterized in that the power output portion further includes a gear quilt Moving gear and second gear driven gear are engaged in a gear driving gear and two gear driving gear using as transmission gear respectively.
15. two-speed automatic transmission as claimed in claim 14, which is characterized in that the power output portion further includes output end Gear is rotated synchronously with a gear driven gear, second gear driven gear.
16. two-speed automatic transmission as claimed in claim 15, which is characterized in that the gear of output end, a gear passive tooth Wheel, second gear driven gear are fixed on a jackshaft.
17. a kind of control method of two-speed automatic transmission, the two-speed automatic transmission includes power reception portion, power output Portion and speed ratio converter section, the speed ratio converter section includes the unilateral bearing and second gear clutch for being coupled to power reception portion, described Method includes:
Power reception portion receives rotary driving force from outside;
The rotary driving force is passed to power output portion with the first rotating ratio or the second rotating ratio by speed ratio converter section, in which: Under unilateral bearing engagement state, if the revolving speed in power reception portion reaches at or above the first shift rate, make second gear clutch Engagement, unilateral bearing disengage automatically;Under second gear clutched state, if the revolving speed in power reception portion reaches or less than second When rate of shifting gears, make second gear throw-out-of clutch, unilateral bearing engages automatically;
Power output portion exports the rotary driving force that speed ratio converter section transmits to the wheel shaft of automobile.
18. the control method of two-speed automatic transmission as claimed in claim 17, which is characterized in that pass through an electrichydraulic control Assembly controls the engagement and disengagement of the second gear clutch.
19. the control method of two-speed automatic transmission as claimed in claim 17, which is characterized in that the speed ratio converter section is also Including synchronizer, the power output portion include engagement gear ring, by control synchronizer movement by power reception portion with it is described Engage gear ring engagement or separation.
20. two-speed automatic transmission as claimed in claim 19, which is characterized in that when the synchronizer make power reception portion with When the engagement gear ring engagement and the reverse rotation of power reception portion, the engagement gear ring drives power output portion to connect with the power Receipts portion synchronous rotary, formation are reversed gear.
21. the control method of two-speed automatic transmission as claimed in claim 20, which is characterized in that when the synchronizer makes Power receiving unit engages gear ring engagement but when power reception portion rotates in the forward direction with described, the engagement gear ring drive power output portion and Power reception portion synchronous rotary forms a gear.
22. the control method of two-speed automatic transmission as claimed in claim 21, which is characterized in that when power reception portion forward direction Rotation and revolving speed is when rising to the first synchronizer rate, the synchronizer separates power reception portion with the engagement gear ring;When When power reception portion rotates in the forward direction and revolving speed drops to the second synchronizer rate, the synchronizer make the rotation in power reception portion with The engagement gear ring engagement.
23. the control method of two-speed automatic transmission as claimed in claim 22, which is characterized in that pass through an electric gear change Assembly controls the synchronizer and the engagement and disengagement for engaging gear ring.
24. the control method of two-speed automatic transmission as claimed in claim 22, which is characterized in that the second synchronizer speed Rate is less than the first synchronizer rate.
25. the control method of two-speed automatic transmission as claimed in claim 24, which is characterized in that the first synchronizer speed Rate is less than the first shift rate, and the second synchronizer rate is less than the second shift rate.
CN201810752291.8A 2018-07-10 2018-07-10 Two-gear automatic transmission and control method thereof Active CN108980337B (en)

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CN113048198A (en) * 2019-12-10 2021-06-29 博格华纳公司 Method for operating a gear shift system for a vehicle transmission
EP3961065A4 (en) * 2019-04-23 2022-12-21 HJ Transmission Co., Ltd. Power transmission device

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