CN106402192A - Locking synchronizing module of shift transmission, as well as method for shifting shift transmission with lock synchronizing module - Google Patents
Locking synchronizing module of shift transmission, as well as method for shifting shift transmission with lock synchronizing module Download PDFInfo
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- CN106402192A CN106402192A CN201610601101.3A CN201610601101A CN106402192A CN 106402192 A CN106402192 A CN 106402192A CN 201610601101 A CN201610601101 A CN 201610601101A CN 106402192 A CN106402192 A CN 106402192A
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- circular cone
- slope
- locking type
- synchronization component
- synchronous
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Classifications
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/025—Synchro rings
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
-
- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/0618—Details of blocking mechanism comprising a helical spring loaded element, e.g. ball
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- 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
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
- F16D23/02—Arrangements for synchronisation, also for power-operated clutches
- F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
- F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
- F16D2023/0625—Details of members being coupled, e.g. gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
Abstract
The invention relates to a locking synchronizing module of a shift transmission. The locking synchronizing module comprises a synchronizing ring which is rotatable about a shift transmission axis and has a locking engagement part and a frictional cone, a coupling disc which has a shifting engagement part and is in fixed connection with a shift gear which is rotatable about the shift transmission axis in a state that the locking synchronizing module is installed; and a mating cone which is adjacent to a friction cone of the synchronizing ring and in friction connection with a friction cone when the synchronizing ring moves towards an axis of the coupling disc, wherein the matching cone is connected to the shift gear of the shift transmission in a torsion resistant and axially-movable manner in a circumferential direction in the state when the locking synchronizing module is installed. Further, the invention also relates to a method for shifting the shift transmission with the lock synchronizing module.
Description
Technical field
The present invention relates to a kind of locking type Synchronization Component of manual transmission, it has：Synchronous ring, described synchronous ring can enclose
Rotate and have locking engaging piece and friction circle tapering around variator axis；Couple disk, described couple disk there is gearshift nibble
Conjunction portion and in the mounted state of locking type Synchronization Component with manual transmission can around variator axis rotate gear
Position gear is fixedly connected；And cooperation circular cone, described cooperation conical abutment in synchronous ring friction circle tapering and in synchronous ring
Towards the frictional connection coupling composition and friction circle tapering during disk axially-movable.
Background technology
Generally become known for the synchronous manual transmission of the inertia-type of motor vehicles from the prior art.In these drive mechanisms
In can occur under specific boundary condition：Can not be linked into for example in vehicle stationary state or be only capable of difficulty being linked into first
Keep off or reverse gear.This phenomenon occurs especially in the double-clutch speed changer with wet clutch, and especially due to by cold and
The high trailing moment that sticky transmission oil causes, described trailing moment causes very high in locking type Synchronization Component
Separating force.
In some manual transmissions, first gear is assigned the locking type synchronization group with multiple simultaneous mechanism with reversing gear
Part, realizes rotating speed by multiple frictional connections that act on, concentric simultaneously equal in described multiple simultaneous mechanism.Single same
Only realize by unique frictional connection that rotating speed is equal in step mechanism, different from single lazy-tongs, multiple simultaneous mechanism has bright
Aobvious higher synchronizing capacity, and due to having the locking slope of acute angle angle of lock, there is the separation moment that may be significantly smaller.
However, multiple simultaneous mechanism be also in structure more expend, difficulty bigger and substantially more expensive.Because completely without multiple
Improve synchronizing capacity, so the multiple simultaneous mechanism of this consuming is generally used only in manual transmission：In vehicle transmission
All gearshift situations in guarantee that locking type Synchronization Component no problem separates, and guarantee that desired gear is reliably linked into.
Content of the invention
The purpose of the present invention is to realize a kind of locking type Synchronization Component, and described locking type Synchronization Component especially has single synchronization
Mechanism, described single lazy-tongs structure simply forms, and can be no in the case of all of gearshift of transmission for vehicles
Problem ground and reliably separated.
According to the present invention, described purpose is realized by mentioning the locking type Synchronization Component of type during beginning, in described locking
In formula Synchronization Component, in the installment state of locking type Synchronization Component, cooperation circular cone is along ring circumferential direction torsionally and can be axial
Movably it is connected with the shift gear of manual transmission.The cooperation supporting being axially movable on shift gear for the circular cone being capable of root
Realize the reduction of the frictional resistance in frictional connection according to the synchronization completing, so that can be by the friction in synchronous ring
Relatively rotating between conus portion and cooperation circular cone separates locking type Synchronization Component.
According to an embodiment of locking type Synchronization Component, cooperation circular cone can be in the countershaft of initial position and separation point position
To movement, wherein compared with separation point position, in cooperation circular cone with couple axial spacing between disk more in initial position
Greatly.In the initial position of cooperation circular cone, friction circle tapering and cooperation circular cone can be spaced apart, institute in separation point position on the contrary
State friction circle tapering and described cooperation circular cone against each other.
In said embodiment it is also preferred that in the separation point position of cooperation circular cone synchronous ring axially abut in coupling
In united dish and/or abut on shift gear.Thus the frictional resistance in frictional connection be reduced to so that synchronous ring with respect to
Cooperation circular cone reverses, and then can separate locking type Synchronization Component without problems.
Preferably, synchronous ring here has at least one jut axially extended with respect to coupling disk, wherein in cooperation
In the separation point position of circular cone, the contact surface of jut abuts in the mating surface coupling disk.It is particularly preferred that contact surface and cooperation
Face is oriented parallel in the case, and orients with being substantially perpendicular to variator axis.
According to another embodiment of locking type Synchronization Component, it is provided with spring element, described spring element is to cooperation circular cone
Carry out loading from separation point position axially towards the direction of initial position.
Spring element can be for example radially resilient ring, the unlimited C-shaped ring being especially made up of spring steel.As replacing
For scheme it is also contemplated that using disk spring or other suitable spring elements.
Preferably, spring element is axially disposed at cooperation circular cone and couples between disk, and wherein cooperation circular cone is via spring
Element is axially supported at and couples on disk and/or be supported on shift gear.In the case, spring element is e.g. flat
, radially resilient and axially substantially rigid ring, described ring extends perpendicular to variator axis.
It is particularly preferred that spring element is clamped radially inward in the separation point position of cooperation circular cone.
On the contrary, spring element can substantially relax in the initial position of cooperation circular cone.As an alternative
It is contemplated that spring element cooperation circular cone initial position in by pretension radially inward.Optionally, in addition it is provided with axial stopping
Block piece, described stop part and limits the axially initial of cooperation circular cone to cooperation circular cone axially away from the motion gauge coupling disk
Position.
According to another embodiment of locking type Synchronization Component, coordinate circular cone that profile portion is had on radially inner side, joining
During conjunction circular cone axial movement, in the case of spring element radial deformation, spring element slides along described profile portion.
Preferably, the described profile portion of cooperation circular cone includes synchronous slope, and described synchronous slope is in axial direction towards coupling
United dish is radially expanded, and wherein spring element pastes in the sync bit between initial position and separation point position of cooperation circular cone
Lean against on described synchronous slope.
Additionally, the profile portion of cooperation circular cone can include separated slope, in axial direction direction couples described separated slope
Disk is radially widened, and wherein spring element abuts in described separated slope in the separation point position of cooperation circular cone.
Preferably, synchronous slope and separated slope are respectively provided with conical slope, the coning angle on wherein synchronous slope
Coning angle more than separated slope.Due to the big coning angle on synchronous slope, in the sync bit of cooperation circular cone, guarantee reliability
Synchronization.Conversely, because the little coning angle of separated slope guarantees：In the separation point position in cooperation circular cone of spring element
The power radially outward acting on produces the force component of axial direction, and described force component will coordinate circular cone to be moved back to towards its axial initial position.Especially
It, the three times that the coning angle on synchronous slope is at least the coning angle of separated slope are big.
Additionally, the present invention also includes the manual transmission for vehicle, described manual transmission has as described above
Locking type Synchronization Component and shift gear, described shift gear can rotate around variator axis and have axial protrusion
Portion, described protuberance has external toothing portion, and the cooperation circular cone of wherein locking type Synchronization Component has internal messing on radially inner side
Portion, described internal messing portion is joined in the external toothing portion of axial jut and will coordinate circular cone substantially torsionally and can
Axially movably it is connected with shift gear.By this way, the cooperation circle in locking type Synchronization Component is set up with low structure consumption
And the connection that be axially movable antitorque along ring circumferential direction between cone and the shift gear of manual transmission.
According to an alternative embodiment, manual transmission includes locking type Synchronization Component as described above and gear
Position gear, described shift gear can around variator axis rotate and in the installment state of locking type Synchronization Component with coupling
United dish is fixedly connected, and wherein couples disk or shift gear has profile portion in radially inner side, coordinate circular cone axial movement when
In the case of spring element radial deformation, spring element slides along profile portion.Because profile portion is so formed in shift gear
Side, the manufacture that can significantly reduce cooperation circular cone expends, so that cooperation circular cone enables in particular to be fabricated to simple plate.
In described drive mechanism embodiment, couple disk or shift gear profile portion and preferably include synchronous slope,
Described synchronous slope is axially facing that synchronous ring ground is radially expanded, wherein cooperation circular cone positioned at initial position and separation point position it
Between sync bit in, spring element abuts on described synchronous slope.
Additionally, coupling disk or shift gear profile portion can include separated slope, described separated slope is axially facing
Synchronous ring ground is radially expanded, and wherein spring element abuts in described separated slope in the separation point position of cooperation circular cone.
Preferably, in this manual transmission, synchronous slope and separated slope are respectively provided with conical slope, its
The coning angle on middle synchronous slope is more than the coning angle of separated slope.
The invention still further relates to a kind of method for switching manual transmission, described manual transmission has described above
Locking type Synchronization Component, wherein method comprises the steps：
A), with (gel ü fteten) neutral position of the ventilation of described locking type Synchronization Component synchronous ring is added as starting point
Carry the gear shifting force of axial direction, and so that synchronous ring is axially moved towards the direction coupling disk accordingly, until friction circle tapering and joining
Close circular cone composition frictional connection and locking type Synchronization Component occupies lock position, wherein cooperation circular cone accounts for for synchronization
It is supported on spring element according to axial sync bit and via synchronous slope, and be wherein applied to whole on synchronous ring
Gear shifting force imports in cooperation circular cone via frictional connection；
If b) gear shifting force applying in step a) is not enough to separate locking type synchronization group after completing synchronization
Part, then gear shifting force is brought up to so that spring element radial deformation and be clamped in the case of, synchronous ring and cooperation circular cone
Be axially facing and couple disk and move, until cooperation circular cone reaches axial separation point position, in described separation point position synchronous annulate shaft to
Abut in and couple on disk and/or abut on shift gear, and gear shifting force be importing directly at least in part couple disk and/
Or in power shift gear, so that the frictional resistance in frictional connection reduces, by between friction circle tapering and cooperation circular cone
Relatively rotate and separate locking type Synchronization Component, and then be linked into desired gear.
According to a method flexible program, coordinate circular cone in axial direction via separated slope in axial separation point position
It is supported on clamped spring element, wherein by spring element, cooperation circular cone is axially distant from and couples the direction of disk and carry out
Loading, and cooperation circular cone is moved in its axial initial position after separation process terminates, so that locking type is same
Step assembly occupies the neutral position of its ventilation.
Brief description
Other features and advantages of the present invention obtain from the following explanation referring to the drawings of preferred implementation.In accompanying drawing
Shown in：
- Fig. 1 illustrates to run through the vertical section of the locking type Synchronization Component according to prior art；
- Fig. 2 is shown in the local of the locking type Synchronization Component according to the present invention in the axial initial position of cooperation circular cone；
- Fig. 3 is shown in the local of the locking type Synchronization Component according to Fig. 2 in the axial sync bit of cooperation circular cone；
- Fig. 4 is shown in the local of the locking type Synchronization Component according to Fig. 2 in the axially-apart position of cooperation circular cone；
- Fig. 5 be shown in cooperation circular cone axial initial position according to an alternative embodiment according to this
The local of bright locking type Synchronization Component；
- Fig. 6 is shown in the local of the locking type Synchronization Component according to Fig. 5 in the axially-apart position of cooperation circular cone；
- Fig. 7 illustrates the stereo decomposing with the manual transmission according to the present invention of the locking type Synchronization Component according to Fig. 5
View；And
- Fig. 8 illustrates the three-dimensional view of spring element, cooperation circular cone and synchronous ring for the manual transmission according to Fig. 7.
Specific embodiment
The conventional shift being used for vehicle shown in the region of Fig. 1 locking type known in the prior art Synchronization Component 12 becomes
Fast device 10.Locking type Synchronization Component 12 includes：Synchronous hub 14, described synchronous hub is torsionally placed on transmission shaft and along ring
Circumferential direction rotates around variator axis A；The gearshift clutch collar 16 being torsionally connected with synchronous hub 14, described gearshift clutch collar phase
Synchronous hub 14 in axial direction 18 is movably disposed；Synchronous ring 20, described synchronous ring is used for synchronous hub 14 and gearshift
The power shift gear 22 of variator 10 couples via frictional connection；And pre-synchronization unit 24, described pre-synchronization unit is bonded on and changes
Keep off on clutch collar 16 and when shifting gears clutch collar 16 axial movement, synchronous ring 20 is loaded towards power shift gear 22 to be coupled
Axial shifting power F.
Synchronous ring 20 has locking engaging piece 26 and friction circle tapering 28, and described friction circle tapering is configured to according to Fig. 1
Female cone.Synchronous ring 20 can be rotated around variator axis A and be coupled with synchronous hub 14 along ring circumferential direction, wherein synchronous ring 20
Restrictively can reverse with respect to synchronous hub 14.Thus, synchronous ring 20 can account in known manner with respect to synchronous hub 14
According to lock position, in described lock position, locking engaging piece 26 prevents the axial movement of clutch collar 16 of shifting gears；And can account for
According to off-position, in described off-position, locking engaging piece 26 allows the axial movement of gearshift clutch collar 16, so that gearshift
Clutch collar 16 can be transformed on the gearshift engaging piece 30 being associated with shift gear 22 and be linked into desired gear.
Generally, it is provided with according to Fig. 1 and couples disk 32, the described disk that couples is had gearshift engaging piece 30 and consolidated with shift gear 22
Surely connect.But as an alternative also can be by gearshift engaging piece 30 direct forming on shift gear 22.
Additionally, locking type Synchronization Component 12 has a cooperation circular cone 34 being configured to outer cone, described cooperation conical abutment in
The friction circle tapering 28 of synchronous ring 20, and synchronous ring 20 towards couple disk 32 axially-movable when constitute with friction circle tapering 28
Frictional connection.In order to obtain the extra high desired frictional connection of frictional resistance, friction circle tapering 28 and cooperation circular cone 34 base
On this, there is identical coning angle, so that described friction circle tapering and cooperation circular cone paste in face each other in synchronization
Lean on.In order to improve transferable moment of friction further, friction circle tapering 28 and/or cooperation circular cone 34 are also with friction facings
36 coating.
In the known from the prior art embodiment of the locking type Synchronization Component 12 according to Fig. 1, couple disk 32 He
Cooperation circular cone 34 single type ground is constituted, and couples disk 32 and cooperation circular cone 34 in axial direction 18 and along ring circumferential direction and gear
Position gear 22 is fixedly connected.As an alternative it is also known that following embodiment, wherein cooperation circular cone 34 or direct forming exist
On shift gear 22, or it is made for single component and is subsequently permanently connected with shift gear 22.
The general principle of work and power of manual transmission 10 with this locking type Synchronization Component 12 is from prior art
In it is known that and being therefore subsequently only illustrated in terms of its basic feature according to shift process.
With the neutral position do not put into gear of the manual transmission 10 according to Fig. 1 as starting point, such as via (unshowned)
Axial gear shifting force F is applied on gearshift clutch collar 16 so that court is associated with expecting the shift gear 22 of gear selector fork
Gearshift engaging piece 30 direction apply described gear shifting force.
Here, via pre-synchronization unit 24 by the friction circle tapering 28 of synchronous ring 20 be pressed onto cooperation circular cone 34 on and with institute
State cooperation circular cone and constitute frictional connection.
Rotating speed between synchronous hub 14 and shift gear 22 is not simultaneously as described frictional connection occurs in synchronous ring 20
Relatively rotating and synchronous hub 14 between.
Synchronous ring 20 occupies its lock position, and in described lock position, locking engaging piece 26 prevents clutch collar 16 axle of shifting gears
Shift gears on engaging piece 30 to moving to.The locking engaging piece 26 of the internal messing portion of gearshift clutch collar 16 and synchronous ring 20 they
Locking rake is respectively provided with axial end portion, due to the speed discrepancy in the lock position of synchronous ring 20, described locking tilts
Portion is regularly against each other so that gearshift clutch collar 16 can not carry out hanging shelves (Durchschalten).
When in the extruding force between locking rake due to the synchronization between synchronous hub 14 and shift gear 22
During reduction, gear shifting force F just be enough to reverse synchronous ring 20 and the internal messing portion of clutch collar 16 of shifting gears just passes through locking engaging piece 26
Move on the gearshift engaging piece 30 coupling disk 32.Then, synchronous hub 14 and shift gear 22 via gearshift clutch collar 16 along ring
Circumferential direction seamlessly connects shape-ordinatedly and as far as possible.
But certified be, in the case of some gear shift, though after synchronization nor separate locking type with
Step assembly, and then desired gear can not be linked into.This is especially due to the high drag that caused by cold and sticky transmission oil
Square, and especially in the double-clutch speed changer have wet-type dual-clutch when vehicle under static state first gear to be linked into or
This situation occurs when reversing gear.
In order to also ensure that in the case of these gearshifts expectation gear be reliably linked into, propose a kind of with respect to Fig. 1 change,
Locking type Synchronization Component 12 according to the present invention and described locking type Synchronization Component is elaborated according to Fig. 2 to 8.Here, it is outstanding
Difference on its research structure and functionally and synchronous with reference to the locking type of the manual transmission 10 according to Fig. 1 in other respects
The general embodiment of assembly 12.
Fig. 2 to 4 is shown respectively the local of the locking type Synchronization Component 12 according to the present invention of manual transmission 10, described lock
Only formula Synchronization Component has：Synchronous ring 20, described synchronous ring can rotate around variator axis A and have locking engaging piece 26
And friction circle tapering 28；Couple disk 32, the described disk that couples has gearshift engaging piece 30, and in locking type Synchronization Component 12
In the state of being arranged in manual transmission 10, described couple can rotating of disk and manual transmission 10 around variator axis A
Shift gear 22 be fixedly connected.Additionally, being provided with cooperation circular cone 34, described cooperation conical abutment is in the friction cone of synchronous ring 20
Portion 28 and synchronous ring 20 towards couple disk 32 axially-movable when constitute and the frictional connection in friction circle tapering 28, wherein in lock
Only formula Synchronization Component 12 has been arranged in the state in manual transmission 10, and cooperation circular cone 34 is along ring circumferential direction torsionally and can
Axially movably it is bearing on the shift gear 22 of manual transmission 10.
As indicated in Fig. 2 to 4, shift gear 22 also has the protuberance 38 of the axial direction with external toothing portion 40, and
And coordinating circular cone 34 that internal messing portion 42 is had on radially inner side, wherein engaging piece 40,42 is engaged with each other and will coordinate circular cone
34 substantially torsionally and axially displaceably with shift gear 22 are connected.
Specifically, the cooperation circular cone 34 on the protuberance 38 of the axial direction of shift gear 22 can in initial position (Fig. 2) and
Axially move between separation point position (Fig. 4), wherein compared with separation point position, in cooperation circular cone 34 He in initial position
The axial spacing coupling between disk 32 is bigger.
At it according in the initial position of Fig. 2, cooperation circular cone 34 is separated with friction circle tapering 28.In other words, synchronous ring 20
Occupy the home position of its ventilation, and manual transmission 10 is located at it according in the neutral position do not put into gear of Fig. 1.
On the contrary, at it according in the separation point position of Fig. 4, cooperation circular cone 34 abuts on friction circle tapering 28.In addition joining
Close in the described separation point position of circular cone 34 synchronous ring 20 axially with couple disk 32 directly contact.Specifically, synchronous ring 20 has
, with respect to coupling the axially extended jut of disk 32 44, wherein the contact surface 46 of jut 44 is in joining according to Fig. 4 at least one
Abut in the mating surface 48 coupling disk 32 in the separation point position closing circular cone 34.Here, contact surface 46 and mating surface 48 are preferably flat
Orient capablely, and be directed essentially vertically with respect to variator axis A.
Spring element 50 is also had according to the locking type Synchronization Component 12 of Fig. 2 to 4, described spring element is to cooperation circular cone 34
Carry out loading from its separation point position axially towards the direction of its initial position.
Spring element 50 is preferably the resilient ring of radial direction and is especially configured to unlimited C-shaped ring in the present embodiment,
Described C-shaped ring is made up of spring steel.
Spring element 50 is axially disposed at cooperation circular cone 34 and couples between disk 32, and wherein cooperation circular cone 34 is via spring
Element 50 is axially supported at and couples on disk 32 and/or be supported on shift gear 22.Here, being configured to radially resilient ring
Spring element 50 especially flat, in axial direction 18 substantially rigid ring, described ring prolongs perpendicular to variator axis A
Stretch.
It is adjacent to internal messing portion 42, cooperation circular cone 34 has profile portion 52 on radially inner side, in cooperation circular cone 34 axially
When mobile, in the case of spring element 50 radial deformation, spring element 50 slides along described profile portion.
The profile portion 52 of cooperation circular cone 34 includes the synchronous slope 54 of cincture, and described synchronous slope is axially facing and couples disk 32
Ground radially expanded, wherein spring element 50 cooperation circular cone 34 between initial position (Fig. 2) and separation point position (Fig. 4)
Abut on described synchronous slope 54 in sync bit (Fig. 3).
Additionally, the profile portion 52 of cooperation circular cone 34 includes the separated slope 56 along ring circumferential direction cincture, described separated slope
It is axially facing and couples that disk 32 ground is radially expanded, wherein spring element 50 abuts in the separation point position (Fig. 4) of cooperation circular cone 34
In described separated slope 56.
The profile portion 52 of the radially inner side of cooperation circular cone 34 enlargedly illustrates in the details local of Fig. 2.According to described thin
Section local is it is clear that synchronous slope 54 and separated slope 56 is axially adjacent to each other and slope that be respectively provided with cone
Face, the cone angle alpha on wherein synchronous slope 54 is more than the cone angle beta of separated slope 56.Especially, the cone angle alpha on synchronous slope 54 is extremely
Big for the three times of the cone angle beta of separated slope 56 less.
In the embodiment illustrating of the locking type Synchronization Component 12 of manual transmission 10, spring element 50 is in cooperation circular cone
Substantially relax in 34 initial position according to Fig. 2.But as an alternative, spring element 50 also can design
For it is in the initial position of cooperation circular cone 34 by radially-inwardly pretension.
Also show in fig. 2 shaft to stop part 58, described axial stop part to cooperation circular cone 34 axially away from coupling
The motion gauge of united dish 32, and limit the axial initial position of cooperation circular cone 34.Described axial stop part 58 is for example by card
Ring is constituted, and in the axially projecting portion 38 that described snap ring is moved to shift gear 22 after installing cooperation circular cone 34, and blocks
It is connected in the groove in protuberance 38.Can prevent from rubbing with low cost in the initial position of cooperation circular cone 34 by stop part 58
Wipe the undesirable trailing moment between conus portion 28 and cooperation circular cone 34, or minimize to trailing moment described in major general.
By cooperation circular cone 34 towards couple disk 32 direction axial movement when, spring element 50 along cooperation circular cone 34 radial direction
The profile portion 52 of inner side is slided and here is deformed radially inwardly.Correspondingly, spring element 50 is in the root of cooperation circular cone 34
Clamped radially inward according in the separation point position of Fig. 4.
Hereinafter, the shift process of manual transmission 10 is described according to Fig. 2 to 4.
With the neutral position of the ventilation of the locking type Synchronization Component 12 according to Fig. 2 as starting point, axle is applied to synchronous ring 20
To gear shifting force F, and synchronous annulate shaft moves to towards associated disk 32 direction that couples, until friction circle tapering 28 and cooperation circle
Cone 34 constitutes frictional connection and locking type Synchronization Component 12 occupies its lock position.Here, cooperation circular cone 34 is same for rotating speed
Walk and move to it according in the axial sync bit of Fig. 3, cooperation circular cone is via synchronous slope described in described sync bit
54 are supported on spring element 50, and the whole gear shifting force F being wherein applied on synchronous ring 20 import cooperation circle via frictional connection
In cone 34.The cone angle alpha here on synchronous slope 54 is chosen as so that spring element 50 can absorb rises in described synchronous phase
Effect axial shifting power F and will cooperation circular cone 34 keep in sync bit axially.
If the described gear shifting force F applying in synchronous phase is also not enough to separate locking type synchronization after synchronization
Assembly 12, then improve gear shifting force F below so that synchronous ring 20 and cooperation circular cone 34 clamp and radial deformation in spring element 50
In the case of mobile axially towards coupling disk 32, until cooperation circular cone 34 reaches the separation point position of its axial direction according to Fig. 4.?
In described separation point position, synchronous ring 20 axially abuts in and couples on disk 32 and be introduced directly into gear shifting force F at least in part
Couple in disk 32.Thus, the frictional resistance in the frictional connection being formed between friction circle tapering 28 and cooperation circular cone 34 reduces
To so that produced via locking rake by axial gear shifting force F, the tangential force that is applied on synchronous ring 20 give full measure with will
Friction circle tapering 28 is reversed with respect to cooperation circular cone 34.Due to " skidding " described in frictional connection, 12 points of locking type Synchronization Component
From and clutch collar 16 of shifting gears be moved axially to shift gears engaging piece 30 on.Thus, although because cold and sticky transmission oil
Cause high trailing moment, be still linked into desired gear.
In its separation point position according to the axial direction of Fig. 4, cooperation circular cone 34 is supported on clamped via separated slope 56
On spring element 50, wherein from spring element 50 to circular cone 34 be axially distant from and couple the direction of disk 32 and carry out loading.?
This, the cone angle beta of separated slope 56 is chosen as so that guaranteeing when extracting gear to coordinate circular cone 34 to move axially to it according to figure
2 axial initial position, this moves axially through spring element 50 and causes.Thus, locking type Synchronization Component 12 occupies its root again
Neutral position according to the ventilation of Fig. 2.
Fig. 5 to 8 illustrates to have a replacement of the manual transmission 10 according to the present invention of locking type Synchronization Component 12
Embodiment.
The variator embodiment of described replacement functionally from do not had according to the manual transmission 10 of Fig. 1 to 4 different, with
As in this regard with reference to the difference on above and hereinafter main research structure.
Similar to the embodiment according to Fig. 1 to 4, the cooperation circular cone 34 of the locking type Synchronization Component 12 according to Fig. 5 to 8 can
Move axially between initial position (Fig. 5) and separation point position (Fig. 6), wherein compared with separation point position, in initial position
In cooperation circular cone 34 and shift gear 22 between axial spacing bigger.
However, according to Fig. 7, coordinating circular cone 34 to have axial projection 60, described projection is in locking type Synchronization Component 12
It is joined on coupling disk 32 in mounted state or is joined in the respective recesses portion 62 on power shift gear 22, so that joining
Close circular cone 34 substantially torsionally and axially displaceably with the shift gear 22 of manual transmission 10 to be connected along ring circumferential direction.
Thus, it is possible to give up the engaging piece 40,42 manufacturing consuming according to Fig. 2 to 4.
At it according in the initial position of Fig. 5, cooperation circular cone 34 is separated with friction circle tapering 28.In other words, synchronous ring 20
Occupy the home position of its ventilation, and manual transmission 10 is located at it according in the neutral position do not put into gear of Fig. 1.
On the contrary, at it according in the separation point position of Fig. 6, cooperation circular cone 34 abuts on friction circle tapering 28.Additionally, it is synchronous
Ring 20 cooperation circular cone 34 described separation point position in axially with couple disk 32 directly contact.Specifically, synchronous ring 20 has
, with respect to coupling the axially extended jut of disk 32 44, wherein the contact surface 46 of jut 44 is in cooperation circular cone 34 at least one
According to abutting in the separation point position of Fig. 6 in the mating surface 48 coupling disk 32.Here, contact surface 46 is preferably parallel with mating surface 48
Ground orientation, and be directed essentially vertically with respect to variator axis A.
In the embodiment according to Fig. 5 to 8, locking type Synchronization Component 12 also has spring element 50, described spring element
Part to cooperation circular cone 34 axially from its separation point position towards its initial position direction loading.
Spring element 50 is preferably the resilient ring of radial direction and is especially configured to unlimited C-shaped ring in the present embodiment,
Described C-shaped ring is made up of spring steel.
Spring element 50 is axially disposed at cooperation circular cone 34 and couples between disk 32, and wherein cooperation circular cone 34 is via spring
Element 50 is axially supported at and couples on disk 32 and/or be supported on shift gear 22.Here, being configured to radially resilient ring
Spring element 50 especially flat, in axial direction 18 substantially rigid ring, described ring prolongs perpendicular to variator axis A
Stretch.
According to Fig. 5 and 6, couple disk 32 and there is annular, cincture, axial direction recess 64, wherein spring element 50 is being joined
Extend in described recess 64 in the separation point position (referring to Fig. 6) closing circular cone 34.Replace in coupling disk 32, described recess 64 is made
Also can be arranged in shift gear 22 for alternative.
Couple disk 32 (or shift gear 22) and profile portion 52 is had on the radially inner side of recess 64, in cooperation circular cone 34 axle
To mobile when in the case of spring element 50 radial deformation spring element 50 slide along described profile portion.
Here, profile portion 52 includes the synchronous slope 54 along ring circumferential direction cincture, described synchronous slope is axially facing synchronization
Ring 20 ground is radially expanded, wherein spring element 50 cooperation circular cone 34 positioned at initial position (Fig. 5) and separation point position (Fig. 6) it
Between sync bit in abut on described synchronous slope 54.
Additionally, the profile portion 52 of cooperation circular cone 34 includes the separated slope 56 along ring circumferential direction cincture, described separated slope
It is axially facing that synchronous ring 20 ground is radially expanded, wherein spring element 50 abuts in the separation point position (Fig. 6) of cooperation circular cone 34
In described separated slope 56.
It is suitable for similar to the details Local map according to Fig. 2, synchronous slope 54 and separated slope 56 are axially adjacent each other
Connect and be respectively provided with the slope of cone, the cone angle alpha on wherein synchronous slope 54 is more than the cone angle beta of separated slope 56.
Especially, the cone angle alpha on synchronous slope 54 is at least three times of the cone angle beta of separated slope 56.
Because profile portion 52 is formed in shift gear side, the manufacture that can significantly decrease cooperation circular cone 34 expends.Therefore, just
As synchronous ring 20, cooperation circular cone 34 for example can be fabricated by by plate as simple drip molding.
Axial direction for spring element 50 supports and loading, and cooperation circular cone 34 has for spring element 50 radially-inwardly
The stop part 66 stretching out, is wherein formed on cooperation circular cone 34 according to the multiple backstop section along the distribution of ring circumferential direction of Fig. 8.So
And, also contemplate for as an alternative, stop part 66 is configured to along ring circumferential direction cincture, punching press convex shoulder.
Claims (20)
1. a kind of locking type Synchronization Component of manual transmission (10), it has：
Synchronous ring (20), described synchronous ring can rotate around variator axis (A) and have locking engaging piece (26) and rub
Wipe conus portion (28)；
Couple disk (32), the described disk that couples has gearshift engaging piece (30) and the peace in described locking type Synchronization Component (12)
Connect with fixing around the shift gear (22) that described variator axis (A) rotates of described manual transmission (10) in dress state
Connect；And
Cooperation circular cone (34), described cooperation conical abutment in described synchronous ring (20) described friction circle tapering (28) and in institute
State synchronous ring (20) towards the described frictional connection coupling and constituting during disk (32) axially-movable with described friction circle tapering (28),
It is characterized in that, described cooperation circular cone (34) is in the installment state of described locking type Synchronization Component (12) along ring Zhou Fang
To be connected can axially movably torsionally and with the described shift gear (22) of described manual transmission (10).
2. locking type Synchronization Component according to claim 1 is it is characterised in that described cooperation circular cone (34) can be in initial bit
Put axial movement and separation point position between, wherein compared with described separation point position, join described in described initial position
Close circular cone (34) and the described axial spacing coupling between disk (32) is bigger.
3. locking type Synchronization Component according to claim 2 is it is characterised in that in described cooperation circular cone (34) described point
Off normal in putting, described synchronous ring (20) axially abut in described in couple disk (32) upper and/or abut in described shift gear
(22) on.
4. locking type Synchronization Component according to claim 3 is it is characterised in that described synchronous ring (20) has at least one
Couple the axially extended jut (44) of disk (32) with respect to described, wherein in the described separation point position of described cooperation circular cone (34)
In, the contact surface (46) of described jut (44) abut in described in couple in the mating surface (48) of disk (32).
5. the locking type Synchronization Component according to any one of claim 2 to 4 is it is characterised in that be provided with spring element
(50), described spring element to described cooperation circular cone (34) from described separation point position axially towards described initial position direction
Carry out loading.
6. locking type Synchronization Component according to claim 5 is it is characterised in that described spring element (50) is that radially have bullet
Property ring, especially open wide C-shaped ring.
7. the locking type Synchronization Component according to claim 5 or 6 it is characterised in that described spring element (50) axially
Be arranged on described cooperation circular cone (34) and described couple between disk (32), wherein said coordinate circular cone (34) via described spring element
Part (50) be axially supported at described in couple disk (32) upper and/or be supported on described shift gear (22).
8. the locking type Synchronization Component according to any one of claim 5 to 7 is it is characterised in that described spring element
(50) radially-inwardly clamped in the described separation point position of described cooperation circular cone (34).
9. the locking type Synchronization Component according to any one of claim 5 to 8 is it is characterised in that described spring element
(50) substantially relax in the described initial position of described cooperation circular cone (34).
10. the locking type Synchronization Component according to any one of claim 5 to 9 is it is characterised in that described cooperation circular cone
(34) profile portion (52) is had on radially inner side, in described cooperation circular cone (34) axial movement in described spring element (50)
In the case of radial deformation, described spring element (50) is slided along described profile portion.
11. locking type Synchronization Component according to claim 10 are it is characterised in that the described wheel of described cooperation circular cone (34)
Wide portion (52) includes synchronous slope (54), and described synchronous slope is radially widened axially towards the described disk (32) that couples, wherein
Described spring element (50) is in the synchronization between described initial position and described separation point position of described cooperation circular cone (34)
Abut in position on described synchronous slope (54).
12. locking type Synchronization Component according to claim 10 or 11 are it is characterised in that the institute of described cooperation circular cone (34)
State profile portion (52) and include separated slope (56), described separated slope radially expands axially towards the described direction coupling disk (32)
Width, wherein said spring element (50) abuts in described separated slope in the described separation point position of described cooperation circular cone (34)
(56) on.
13. locking type Synchronization Component according to claim 11 and 12 are it is characterised in that described synchronous slope (54) and institute
State the slope that separated slope (56) is respectively provided with taper, the coning angle (α) of wherein said synchronous slope (54) is more than described point
Coning angle (β) from slope (56).
A kind of 14. manual transmissions for vehicle, it has：
Locking type Synchronization Component (12) according to any one of the claims, and
Shift gear (22), described shift gear can rotate around variator axis (A) and have axial protuberance (38),
Described protuberance has external toothing portion (40),
The described cooperation circular cone (34) of wherein said locking type Synchronization Component (12) has internal messing portion (42) on radially inner side,
Described internal messing portion is joined in the described external toothing portion (40) of axial described protuberance (38) and by described cooperation circular cone
(34) substantially be connected can axially movably torsionally and with described shift gear (22).
A kind of 15. manual transmissions for vehicle, it has：
Locking type Synchronization Component (12) according to any one of claim 5 to 9, and
Shift gear (22), described shift gear can rotate and in described locking type Synchronization Component around variator axis (A)
(12) it is fixedly connected with the described disk (32) that couples in installment state,
Wherein said couple disk (32) or described shift gear (22) has profile portion (52), in described cooperation on radially inner side
During circular cone (34) axial movement in the case of described spring element (50) radial deformation described spring element (50) along described
Profile portion is slided.
16. manual transmissions according to claim 15 are it is characterised in that described gear tooth that couple disk (32) or described
The profile portion (52) of wheel (22) includes synchronous slope (54), and described synchronous slope is axially facing described synchronous ring (20) ground diameter to expansion
Width, wherein said spring element (50) is in described cooperation circular cone (34) between described initial position and described separation point position
Sync bit in abut on described synchronous slope (54).
17. manual transmissions according to claim 15 or 16 are it is characterised in that described gear that couple disk (32) or described
The described profile portion (52) of position gear (22) includes separated slope (56), and described separated slope is axially facing described synchronous ring (20)
Ground is radially expanded, and wherein said spring element (50) abuts in described point in the described separation point position of described cooperation circular cone (34)
On slope (56).
18. manual transmissions according to claim 16 and 17 are it is characterised in that described synchronous slope (54) and described point
It is respectively provided with the slope of taper from slope (56), the coning angle (α) of wherein said synchronous slope (54) is oblique more than described separation
The coning angle (β) on slope (56).
A kind of 19. methods of the gearshift for manual transmission, described manual transmission has appoints according in claim 1 to 13
Locking type Synchronization Component (12) described in one, methods described comprises the steps：
A) with the neutral position of the ventilation of described locking type Synchronization Component (12) as starting point, to described synchronous ring (20) loading axis
To gear shifting force (F) and so that described synchronous ring is axially moved towards the described accordingly direction coupling disk (32), until described
Friction circle tapering (28) and described cooperation circular cone (34) constitute frictional connection and described locking type Synchronization Component (12) occupies lock
Stop bit is put, and wherein said cooperation circular cone (34) occupies axial sync bit and via synchronous slope for synchronization
(54) it is supported on spring element (50), and be wherein applied to whole gear shifting forces (F) on described synchronous ring (20) via institute
State frictional connection to import in described cooperation circular cone (34)；
If b) gear shifting force (F) applying in step a) is not enough to separate described locking type Synchronization Component after synchronization
(12), then described gear shifting force (F) is brought up to so that described synchronous ring (20) and described cooperation circular cone (34) are in described spring
Mobile axially towards the described disk (32) that couples in the case of element (50) radial deformation and clamping, until described cooperation circular cone
(34) reach axial separation point position, synchronous ring (20) described in described separation point position axially abut in described in couple disk
(32) go up and/or abut on described shift gear (22), and described gear shifting force (F) is introduced directly into described coupling at least in part
In united dish (32) and/or described power shift gear (22), so that the frictional resistance in described frictional connection reduces, by institute
State relatively rotating and making described locking type Synchronization Component (12) point between friction circle tapering (28) and described cooperation circular cone (34)
From thus being linked into gear.
20. methods according to claim 19 are it is characterised in that coordinate circular cone (34) in axial described separation by described
It is supported on the spring element (50) of clamping via separated slope (56) in position, wherein pass through described spring element (50) to institute
State cooperation circular cone (34) be axially distant from described in couple the direction of disk (32) and carry out loading, and described in when extracting described gear
Cooperation circular cone moves in its axial initial position, so that described locking type Synchronization Component (12) occupies the neutrality of its ventilation
Position.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102015112219.7A DE102015112219A1 (en) | 2015-07-27 | 2015-07-27 | Locking synchronization assembly of a gearbox and method for switching a gearbox with such a lockout synchronization module |
| DE102015112219.7 | 2015-07-27 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN106402192A true CN106402192A (en) | 2017-02-15 |
| CN106402192B CN106402192B (en) | 2019-08-16 |
Family
ID=57795576
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201610601101.3A Active CN106402192B (en) | 2015-07-27 | 2016-07-27 | The locking type Synchronization Component and process for gear of gear shift transmission |
Country Status (2)
| Country | Link |
|---|---|
| CN (1) | CN106402192B (en) |
| DE (1) | DE102015112219A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111527320A (en) * | 2017-10-26 | 2020-08-11 | 舍弗勒技术股份两合公司 | Apparatus and method for synchronization |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102019206607A1 (en) * | 2019-05-08 | 2020-11-12 | Zf Friedrichshafen Ag | Transmission device for a motor vehicle |
| DE102019214610A1 (en) * | 2019-09-25 | 2021-03-25 | Zf Friedrichshafen Ag | Synchronization device for a drive train |
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| CN104235221A (en) * | 2013-06-12 | 2014-12-24 | 贺尔碧格传动技术控股有限公司 | Synchronizer ring for a synchronization unit of a manual transmission and synchronization unit with such a synchronizer ring |
| CN104712678A (en) * | 2013-12-17 | 2015-06-17 | 欧瑞康摩擦***（德国）有限责任公司 | Friction ring, synchronization ring, synchronization unit and a variable speed gearbox for a motor vehicle |
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2015
- 2015-07-27 DE DE102015112219.7A patent/DE102015112219A1/en not_active Withdrawn
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|---|---|---|---|---|
| DE2431324B1 (en) * | 1974-06-29 | 1975-08-14 | Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen | Synchronizer |
| CN1135254A (en) * | 1993-11-18 | 1996-11-06 | 沃尔沃·拉斯特韦格纳公司 | Synchronizing device in vehicle gearbox |
| CN1339369A (en) * | 2000-08-21 | 2002-03-13 | 现代自动车株式会社 | Hand operated speed gear box synchronous device for automobile |
| CN102052413A (en) * | 2009-11-03 | 2011-05-11 | 贺尔碧格传动技术控股有限公司 | Multiple synchronization module for gearbox and gearbox |
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| CN104235221A (en) * | 2013-06-12 | 2014-12-24 | 贺尔碧格传动技术控股有限公司 | Synchronizer ring for a synchronization unit of a manual transmission and synchronization unit with such a synchronizer ring |
| CN104712678A (en) * | 2013-12-17 | 2015-06-17 | 欧瑞康摩擦***（德国）有限责任公司 | Friction ring, synchronization ring, synchronization unit and a variable speed gearbox for a motor vehicle |
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| CN111527320A (en) * | 2017-10-26 | 2020-08-11 | 舍弗勒技术股份两合公司 | Apparatus and method for synchronization |
Also Published As
| Publication number | Publication date |
|---|---|
| DE102015112219A1 (en) | 2017-02-02 |
| CN106402192B (en) | 2019-08-16 |
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