CN103225655B - A shift gear driver of a flywheel synchronous transmission - Google Patents
A shift gear driver of a flywheel synchronous transmission Download PDFInfo
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- CN103225655B CN103225655B CN201310025326.5A CN201310025326A CN103225655B CN 103225655 B CN103225655 B CN 103225655B CN 201310025326 A CN201310025326 A CN 201310025326A CN 103225655 B CN103225655 B CN 103225655B
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- Prior art keywords
- shift
- breach
- synchronous
- shift gear
- gear
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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
- F16D23/0606—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 the blocking mechanism comprising an axially-extending shouldered pin passing through a hole in a radial wall
Abstract
A shift gear driver (12) of a flywheel synchronous transmission (10) is provided and comprises an integrated annular body (34) capable of rotating round a transmission axis (A). The annular body comprises a first outline (36) on the inner side of the radial direction of the annular body. The first outline (36) is used for rotating not relative to a transmission shaft (38) and is connected with transmission shaft (38) in an axial movement manner. The annular body comprises a second outline (40) on the outer side of the radial direction of the annular body. The second outline (40) is used for being axially connected with a shift gear element (42) capable of moving axially. In addition, the annular body comprises synchronous gaps (24) between the inner side and the outer side of the radial direction. The axial protrusions (18,20,22) of a friction ring (16) can be embedded into the synchronous gaps. The annular body (34) also comprises an independent shift gear gap (32) between the inner side and the outer side of the radial direction. The independent shift gear gap (32) is used for being rotatably connected with a clutch body in a non relative manner.
Description
Technical field
The present invention relates to a kind of for shift gear driver of a flywheel synchronous transmission/conveyer and a kind of with this
The flywheel sychronising formula variator of shift gear driver.
Background technology
Be typically provided with conventional flywheel sychronising formula variator sync-body and it is synergistic with the sync-body individually
Gearshift clutch collar, sync-body can not be relatively rotatably disposed on power transmission shaft, and gearshift clutch collar can not phase relative to sync-body
To arranging rotatably but axially displaceably.In order to simplify this variator in structure and manufacturing process, in the prior art
Known so-called " shift gear driver ", it has annular solid, and each annular physical ability is around transmission axis rotation.Annular solid is inside in its footpath
Side has the first profile, for can not with the relative rotation and axially displaceably couple with power transmission shaft；Have in its radial outside
Second profile, for axially coupled with the shifting element being axially movable；And have between radially inner side and radial outside
Synchronous breach, each axial projections of a drag ring can be embedded in each synchronous breach.This changing for flywheel sychronising formula variator
Gear driver is for example by known to the A of DE 1 101 057.In the publication, referred to as the shift gear driver of jaw clutch gear ring by
Two rotational symmetric disk compositions, the two disks are adjacent to each other vertically.Interior teeth portion, institute are constituted on the radially inner side of the disk
In stating the outer toothed portion of the embedded power transmission shaft of interior teeth portion.Shifting fork is acted on the radial outside of the disk, so that shift gear driver
Move axially on power transmission shaft.Opening is provided with two disks between the radially inner side and radial outside of shift gear driver, its
The tooth of middle synchronous ring and the tooth of free pulley all can be embedded in each opening so that synchronous ring or free pulley along the circumferential direction with change
Gear driver connection.
The driver solution of the A of DE 1 101 057 is right with two of manufacture advantage by using existing structure advantage
The flat stamping parts for claiming provides the loaded down with trivial details structure with sync-body and switching clutch collar in manufacturing process being initially mentioned.
But the drive mechanism for describing in the prior art still manufactures loaded down with trivial details, because two symmetrical annular disks must phase
For being fixed to one another, and the opening in the two disks must coordinate accurately with the tooth in teeth portion and free pulley in synchronous ring
Mutually coordinate in portion.Correspondingly, related driving member will observe narrower dimensional tolerance, to guarantee the good of flywheel sychronising formula variator
Good function.
The content of the invention
Therefore, it is an object of the invention to provide a kind of be used for shift gear driver of a flywheel synchronous transmission, it is being changed
With simplified structure while gear function reliability, high shifting comfort and high life, it is possible to less manufacturing expenses
With production.
According to the present invention, the purpose realizes that it has around biography by a kind of shift gear driver of a flywheel synchronous transmission
The annular solid of the rotatable one of shaft line, the annular solid has the first profile in its radially inner side, for can not with power transmission shaft
Can couple with the relative rotation and axially movably；Its radial outside have the second profile, for movable shifting element
It is axially coupled；And there is synchronous breach between radially inner side and radial outside, each axial projections of drag ring can be embedded in
In each synchronous breach, wherein annular solid also has individually gearshift breach between radially inner side and radial outside, for from
Zoarium can not couple with the relative rotation.Therefore the shift gear driver only also has the annular solid of unique one, in the annular solid
The middle breach constituted for coupling with drag ring and the single breach for coupling with clutch body.It is flat due to being preferably configured as
Annular disk annular solid one structure, extremely simple and axially compact drive mechanism is formed here.Additionally due to institute
State single breach and less tolerance issues occur, because these breach must only be directed at drag ring or must only be directed at clutch body.
Preferably, the first profile is interior teeth portion, and/or the second profile is in the circular gearshift groove of radial outside.For with
Power transmission shaft can not connect with the relative rotation and for axial shifting operation profile have been found to be extremely reliable, it is possible to
It is integrated in the annular solid of one with little expense.Except the gearshift groove for wrapping around, simple edge also can be only set certainly
The edge of circumferencial direction closing, the forked operating element of the surrounded by edges.
In a kind of embodiment of shift gear driver, pressure piece opening is provided with annular solid, is added for accommodating spring
The pressure piece of load.Pressure piece preferably can radial motion, wherein annular solid can be readily constructed for and be used as be accommodated
The radially-directed portion of pressure piece.
Integrated one synchronous breach and/or two gearshift breach can be distinguished in each pressure piece opening.If integrated
One synchronous breach, then pressure piece act directly in the axial projections of drag ring and be achieved in the simple and reliable of variator
Presynchronization.If integrated two gearshifts breach, not only can realize large number of in annular solid in pressure piece opening
Gearshift breach, and breach along the circumferential direction equidistant distribution of shifting gears can be realized, this causes in material stress and manufacturing expenses
With the advantage of aspect.
Preferably, at least one of annular solid synchronous breach is defined by synchronization inclined-plane, these synchronous inclined-planes can with it is corresponding
In the axial projections of the arranging of drag ring constitute synchronous inclined-plane recline.It is pre- by clutch body in flywheel sychronising formula variator
After synchronization, synchronous inclined-plane is used for actual drive coordination, that is, limit rotating against between shift gear driver and drag ring, and
Axial shifting power is converted to the restoring force for along the circumferential direction pointing to.It is particularly preferred that being integrated in all in pressure piece opening
Synchronous breach is defined by synchronous inclined-plane, should with the material for reducing surface pressure and thus reduce in shift gear driver and drag ring
Power.
In a form of implementation of shift gear driver, gearshift breach is than the radially more inner setting of synchronous breach.Here, being
Stablize preferred breach is arranged not radially superposedly.
Particularly, annular solid can have the gearshift breach more than synchronous breach.This considers following facts：What is inserted
Gear must be via the whole engine torque of the edge transfer of gearshift breach or gearshift breach, and via synchronous breach or synchronization
The edge of breach must only transmit the simultaneous force for occurring in the transmission.Due to constituting individually gearshift breach and synchronous breach,
Its quantity can be to load that is independently of each other and being matched with corresponding appearance.Therefore, the quantity of synchronous breach can be reduced, and this not only leads
Cause simple manufacture and cause the higher stability of shift gear driver.
In another form of implementation of shift gear driver, gear shift pin is provided with, each gear shift pin extends axially through annular solid
Gearshift breach, protrude from annular solid at least one end face axial stretch out and be embedded on clutch body constitute gear shift pin open
In mouthful.Gear shift pin here is preferably fixedly connected with annular solid, for example, be pressed in the gearshift breach of annular solid.It is particularly preferred that
Gear shift pin protrudes from two end faces of annular solid.Therefore, when clutch body is arranged on the axial both sides of shift gear driver, each is changed
Backing pin can be used for shape and be joined in locking manner in the gear shift pin opening of two clutch bodies and for power transmission.
In this embodiment, each gear shift pin can have backstop, for making gear shift pin relative to annular solid axially position.
The backstop is for example configured to circular flange and is used as to install assisted parts when gear shift pin is fixed on annular solid.Can by backstop
So that all gear shift pins to be brought in a straightforward manner the axial location relative to annular solid identical preferred center, changing so as to work as
All gear shift pins are embedded in the gear shift pin opening arranged with it in clutch body simultaneously when shift gear driver is moved axially during gear process
In.Therefore the overload and undesirable actuating device scratch of indivedual gear shift pins can reliably be avoided.
In order to be easy to that gear shift pin is imported the gear shift pin opening of the arranging in drag ring in shift process, gear shift pin is preferred
It is configured to so that each gear shift pin is shifted gears pin end, particularly tapered in two axial shifting pin end tapers at least one.
Specifically, pin end of shifting gears for example is configured to point, convex spherical or inclined.
Additionally, each gear shift pin can have gearshift gap segments, the gearshift gap segments adjoin in mounted condition annular
Body, wherein gear shift pin have lateral incision between gearshift gap segments and axial shifting pin end.In shift process, shift gear driver
Move to a drive range by means of axial shifting power after synchronization is realized, in the drive range, gear shift pin be embedded in from
Desired gear is placed in fit gear shift pin opening.By the lateral incision, even if shift gear driver is after shift process
Without being still maintained at its (shifting gears) position in the case of gear shifting force, from and the gear inserted will not be automatically " de- again
From ".
Additionally, present invention additionally comprises a kind of flywheel sychronising formula variator for motor vehicles, including：It is above-mentioned to move axially
Shift gear driver；At least one drag ring for along the circumferential direction coupling with shift gear driver, the drag ring has axial projections,
Each projection can be put in the synchronous breach of shift gear driver；And at least one clutch body, it can along the circumferential direction can not be relative
Rotatably couple with shift gear driver, wherein axially projecting projection is molded on clutch body, the embedded gearshift of each projection is passed
Can not couple with the relative rotation with shift gear driver in the gearshift breach of dynamic device.In this case, one regularly with speed change
The single component of the driven pulley connection of device is referred to as clutch body.Shift gear driver only includes in the form of implementation of variator
The annular solid of one, the annular solid is especially structured to flat annular disk and with multiple profiles being molded and/or breach.
These profiles and/or breach realize different functions, and are arranged so that there is shift gear driver enough stability to transmit
The power for being occurred, and can be manufactured with less manufacturing expense.Clutch body with axially projecting projection equally can be such as
Manufactured with less expense as form panel, projection can be simply pressed in the plate.
For ease of projection is penetrated shift gear driver when gear is inserted gearshift breach in, clutch body preferably so structure
Make：Each projection is tapered towards free axial projection end.In addition, free projection end can in an advantageous manner similar to changing
The above-mentioned gear shift pin end structure of backing pin.Particularly, each projection can first towards free axial projection end expanding, Ran Houjian
Contracting, so as to form the lateral incision for having referred in gear shift pin, shift gear driver has been maintained at it by the lateral incision in the gear inserted
The position of gearshift.
Finally, present invention additionally comprises a kind of flywheel sychronising formula variator for motor vehicles, including：Above-mentioned can axially move
Dynamic shift gear driver, at least one drag ring for along the circumferential direction coupling with shift gear driver, the drag ring has axially prominent
Rise, each projection can be put in the synchronous breach of shift gear driver, and at least one clutch body, it can along the circumferential direction can not phase
To rotatably with shift gear driver coupling and being arranged on the end face relative with annular solid of gear shift pin, wherein clutch body has and changes
Backing pin opening, gear shift pin can be embedded in the gear shift pin opening when shift gear driver is moved axially.In the enforcement shape of variator
In formula, shift gear driver and clutch body all only have gearshift breach or gear shift pin opening, the gearshift breach or gear shift pin opening
For example can be manufactured by Sheet Metal Forming Technology with minimum expense.However, in order to shape couples in locking manner two components, single gear shift pin
It is required, it equally can be manufactured with less expense, but must be pre-installed on annular solid, to form shift gear driver.
In a form of implementation of flywheel sychronising formula variator, the radial outside of clutch body constructs tapered friction
Face, and adjacent rubbing surface that can be with drag ring reclines.Because the structure is the engagement of the embedding tooth with axially projecting projection,
The radial outside of clutch body no longer needs conventional outer toothed portion, so as to the radial outside of clutch body can be configured in an advantageous manner
Rubbing surface.And, this is conducive to simplifying clutch body and the therefore whole flywheel sychronising formula variator of simplification in structure.
Description of the drawings
Other features and advantages of the present invention are given by means of accompanying drawing by preferred implementing form described below.In accompanying drawing
In：
Fig. 1 illustrates that the flywheel sychronising formula of the invention of the shift gear driver with the first form of implementation of the invention becomes
The decomposition diagram of fast device；
Fig. 2 illustrates the vertical section according to the variator of Fig. 1 in pressure piece region；
Fig. 3 is illustrated according to the variator of Fig. 1 in the vertical section of gearshift gap regions；
Fig. 4 illustrates the cross section IV-IV of the variator according to Fig. 2 and 3；
Fig. 5 illustrates the section V-V of the shift gear driver of the variator according to Fig. 4；
Fig. 6 illustrates the perspective cut-away schematic view of a thin portion of the shift gear driver according to Fig. 5；
Fig. 7 illustrates that the flywheel sychronising formula of the invention of the shift gear driver with the second form of implementation of the invention becomes
The decomposition diagram of fast device；
Fig. 8 illustrates the vertical section according to the variator for having assembled of Fig. 7 in pressure piece region；
Fig. 9 illustrates the vertical section according to the variator for having assembled of Fig. 7 in gear shift pin region；
Figure 10 illustrates the cross section X-X of the variator for having assembled according to Fig. 8 and 9；
Figure 11 is illustrated for a thin portion perspective view according to the gear shift pin of the variator of Fig. 7 to 10；
Figure 12 illustrates the vertical section of the gear shift pin according to Figure 11；
Figure 13 illustrates the possibility and structure of free axial projection end or gearshift pin end；And
Figure 14 illustrates other forms of implementation do not mentioned for shift gear driver of a flywheel synchronous transmission.
Specific embodiment
Fig. 1 to 6 illustrates the first form of implementation of the flywheel sychronising formula variator 10 for motor vehicles, and the variator has
The shift gear driver 12 being axially movable according to the first form of implementation, be arranged on shift gear driver 12 two of axial both sides
Clutch body 26 and it is similarly disposed at the axial both sides of shift gear driver 12 and along the circumferential direction 14 couples with shift gear driver 12
Two drag rings 16, the clutch body along the circumferential direction 14 can not can couple with the relative rotation with shift gear driver 12, described
Drag ring has axial projections 18,20,22, and the axial projections can be put in the synchronous breach 24 of shift gear driver 12.
Clutch body 26 is component that is single but being respectively fixedly connected with the driven pulley 28 (referring to Fig. 2 and 3) for arranging.
Particularly, clutch body 26 be form panel and for example with arranging the soldering of driven pulley 28, melting welding, bonding or pressing.
Additionally, the radial outside of clutch body 26 is configured to the rubbing surface 64 of taper, and can be with the rubbing surface 62 of drag ring 16
Recline and formed frictional connection.
Here is particularly, and one of two rubbing surfaces 62 are correspondingly equipped with friction facing and (spread sintering liner, organic lining
Piece, carbon liner etc.).
In the first form of implementation of variator 10, axially projecting projection 30 is molded the end face in clutch body 26
On, these projections are embedded in the gearshift breach 32 of shift gear driver to couple with the relative rotation with shift gear driver 12.
The shift gear driver 12 of flywheel sychronising formula variator 10 includes the annular solid around the rotatable one of transmission axis A
34, according to Fig. 1 to 6, it is configured to flat annular disk.Annular solid 34 has the first profile 36 in its radially inner side, for transmission
Axle 38 can not with the relative rotation and axially displaceably couple (see Fig. 4)；Its radial outside have the second profile 40, for
The shifting element 42 axially coupled (see Fig. 2) being axially movable；And there is synchronous lacking between radially inner side and radial outside
Mouth 24, the axial projections 18,20,22 of drag ring 16 can be embedded in each synchronous breach.
Additionally, annular solid 34 also has individually gearshift breach 32 between radially inner side and radial outside, for from
Fit 26 can not couple with the relative rotation.
Synchronous breach 24 and the gearshift here of breach 32 extend axially through respectively annular solid 34, such as visible in Figure 5.
In the first form of implementation of flywheel sychronising formula variator 10, the first profile 36 is interior teeth portion (see Fig. 1 and 6), the
Two profiles 40 be in the circular gearshift groove 46 of radial outside, the shifting element 42 being axially movable can be embedded in the gearshift groove (see
Fig. 2).Alternately, the second profile 40 also can be only the edge of along the circumferential direction 14 closings of annular solid 34, be configured to forked
The shifting element 42 being axially movable surrounds the edge (see Fig. 8).
In addition to synchronous breach 24 and gearshift breach 32, in annular solid 34 its radially inner side and its radial outside it
Between be additionally provided with pressure piece opening 48 for accommodating spring-loaded pressure piece 50.Pressure piece 50 can radial motion and by spring element
Part 52 is radially outward loaded (see Fig. 2 and 4) towards axial projections 18.
As shown in fig. 6, being respectively equipped with gathering sill 54 in pressure piece opening 48, pressure piece 50 is radially movablely and along axle
To being immovably maintained to the full extent in the gathering sill with tangential direction.
In addition preferably understand in figs. 4 and 6, distinguish in each pressure piece opening 48 integrated one synchronous breach 24 and
Two gearshift breach 32, it is, each opening and the mutual transition of breach.
Synchronous in order to realize in variator 10, at least one synchronous breach 24 is defined by synchronous inclined-plane 56 (see Fig. 6), institute
Stating synchronous inclined-plane can be with synchronous inclined-plane 58 (see Fig. 1) patch of the corresponding construction in the axial projections 18 of the arranging of drag ring 16
Lean on.Therefore, synchronous inclined-plane 56,58 limits rotating against between shift gear driver 12 and drag ring 16.Additionally, synchronous inclined-plane
56th, 58 axial shifting power F is changed into the restoring force of along the circumferential direction 14 effects, by the restoring force, the He of shift gear driver 12
Driven pulley 28 to be shifted gears along the circumferential direction 14 is relative to each other aligned after synchronization so that projection 30 is in gearshift transmission
Device 12 is embedded in the gearshift breach 32 of clutch body 26 along when moving axially towards the direction of driven pulley 28.
In the first form of implementation of the shift gear driver according to Fig. 1 to 6, synchronous inclined-plane 56 is arranged on and is integrated in pressure piece
On all synchronous breach 24 in opening 48.
Also known that according to Fig. 4 and 6, gearshift breach 32 is radially arranged more inner than synchronous breach 24.Due to drag ring 16
The embedded synchronization breach 24 of axial projections 18,20,22 in, therefore can maximize by this way drag ring 16 radius and
Its rubbing surface 62.Therefore produce big friction torque in drive coordination, the friction torque cause shift gear driver 12 with from
Quick speed considerations between fit 26 or driven pulley 28.
In addition, the annular solid 34 of shift gear driver 12 has the gearshift breach 32 than synchronous breach more than 24, because via changing
Gear breach 32 must transmit all engine torques, and must only transmit a small amount of friction torque via synchronous breach 24.Due to it
Individually construct, the quantity of synchronous breach 24 and gearshift breach 32 can individually be matched with the load of corresponding appearance.Therefore, it is special
It is not that the quantity of synchronous breach 24 can be reduced, this causes annular solid 34 and shift gear driver 12 because less component dies down
Higher rigidity.
Can determine by further looking at the axial projections 18,20,22 of drag ring 16：Projection 18,20,22 is realized different
Function and be correspondingly differently composed.
Thus, for example axial projections 18 are embodied as synchronous projection, on the one hand it have presynchronization inclined-plane 60, and pressure piece 50 is made
(see Fig. 2 and 3) on the presynchronization inclined-plane；On the other hand there is previously described synchronous inclined-plane 58, the synchronous inclined-plane can be made
On the complementary synchronous inclined-plane 56 of synchronous breach 24.
When gear shifting force F is applied on the annular solid 34 of shift gear driver 12, pressure piece 50 is axially pressed against corresponding friction
The presynchronization inclined-plane 60 of ring 16, and the conical friction face 62 of drag ring 16 correspondingly axially loaded clutch body 26 is same
The rubbing surface 64 (presynchronization) of taper.
Formed between drag ring 16 and clutch body 26 after frictional connection, drag ring and clutch body are relative due to speed discrepancy
Rotate in shift gear driver 12, rotate against until synchronous inclined-plane 56,58 is touched each other and thus limited.
Gear shifting force F is sufficient so that synergistic synchronous inclined-plane 56,58 along sliding over each other and make to change after synchronous rotational speed
Gear driver 12 is inverted until a centre position relative to drag ring 16, and in the centre position, shift gear driver 12 is by gearshift
Power F is moved further axially towards the direction of driven pulley 28 to be shifted gears, and the axial direction being molded on clutch body 26 is convex
The shape of block 30 is embedded in locking manner in gearshift breach 32.
The axial projections 20 of drag ring 16 are embodied as attachment tabs, and it rubs two in the state of the assembling of variator 10
Wipe ring 16 to be in axial direction fixed relative to each other.For this purpose, the projection of the projection 20 of a drag ring 16 and another drag ring 16
20 are disposed in respectively each other and according to the type structure of complementary building block.It is disposed in group of the mutual projection 20 in variator 10
Shape is embedded in locking manner each other, so as to drag ring 16 only together can be moved in axial direction in the state of dress.For mounting protrusion
20, each drag ring 16 only has two projections 20, and it is diametrically opposed respectively, so as to each ring must be transported radially towards each other
It is dynamic, so that projection 20 is inserted each other.
Axial projections 22 do not have in the embodiment in accordance with fig. 1 specific function, and are only used for making to dash forward to the full extent
Play 18,20,22 along the circumferential direction 14 to be evenly distributed, to avoid the imbalance of drag ring 16.Certainly, projection 22 is also configured to
Synchronous projection 18 or attachment tabs 20.
In order to reduce material stress and surface pressure during synchronization, it is also contemplated that arrive：Projection 20 and/or projection 22 are similar
Also there is synchronous inclined-plane 58 in projection 18.In this case, set on the synchronous breach 24 of corresponding arranging also in annular solid 34
Put the synchronous inclined-plane 56 of complementation.
Fig. 7 to 12 illustrates with the flywheel sychronising formula variator 10 according to the shift gear driver 12 of the second form of implementation the
Two forms of implementation.Functional mode here in the total of the variator 10 and its principle is described above with variator 10
The 26S Proteasome Structure and Function mode of the first form of implementation is identical, therefore hereinafter only discusses with reference to the description to Fig. 1 to 6 with regard to this point
Special character in the structure of the second form of implementation.
It is different from the first form of implementation, also wrapped in addition to annular solid 34 according to the shift gear driver 12 of the second form of implementation
Gear shift pin 66 is included, it extends axially through the gearshift breach 32 of annular solid 34.Gear shift pin 66 is according to the installed of Fig. 8 and 9
Two axial ends of annular solid 34 are axially protruded under state, and the gear shift pin opening constructed on clutch body 26 can be embedded in
68.Gear shift pin 66 is pre-installed on annular solid 34 and is permanently connected with annular solid 34 after its installation, particularly regularly
In the gearshift breach 32 of press-in annular solid 34.
In addition to the shift gear driver 12 being axially movable, also there are two according to the variator 10 of the second form of implementation
It is arranged on the axial both sides of shift gear driver 12 and along the circumferential direction 14 drag ring 16 and two coupled with shift gear driver 12
The clutch body 26 of the individual axial both sides for being similarly disposed at shift gear driver 12, drag ring has respectively axial projections 18,20,22,
Each projection can be put in the synchronous breach 24 of shift gear driver 12, clutch body can along the circumferential direction 14 can not with the relative rotation with change
Gear driver 12 couples.In the second form of implementation of variator 10, clutch body 26 has gear shift pin opening 68, and gear shift pin 66 exists
Shift gear driver 12 can be embedded in gear shift pin opening when moving axially.
Figure 11 and 12 illustrates the perspective view of gear shift pin 66 and vertical section.Preferable visible, the gear shift pin 66 in these detail views
With backstop 70 so that gear shift pin 66 is relative to the axially position of annular solid 34, the backstop is configured in this embodiment circular convex
Edge simultaneously is used as to install assisted parts.
Additionally, gear shift pin 66 is conically tapered in two axial gearshift pin end 72, to be easy to " penetrating " or engagement
To in the gear shift pin opening 68 of clutch body 26.Gearshift pin end 72 the other structures that can realize simply penetrating in Figure 13 a extremely
Illustrate in 13d, and have slightly pointed, convex spherical or inclined gearshift pin end 72.
According to Figure 12, each gear shift pin 66 has gearshift gap segments 74, and it adjoins in mounted condition annular solid 34
(see Fig. 9), wherein gear shift pin 66 have respectively lateral incision 76 between gearshift gap segments 74 and axial shifting pin end 72.Lateral incision 76
Even if for making gear shift pin 66 protect in the case of the gear shifting force F without axial action with gear shift pin opening 68 when gear is connected
Engagement is held, and the gear inserted itself will not depart from again.In order to depart from the gear having been turned on, it is in reverse to gear shifting force F's
Opposite force is required, and power is axially retained by what lateral incision 76 was acted in the drive position having been turned on to overcome.
Certainly, variator 10 according to Fig. 1 to 6 can be similarly transferred to regard to the described above of pin end 72 of shifting gears
The projection 30 being molded on clutch body 26 of the first form of implementation.Therefore, in this case each projection 30 also can be towards certainly
By axial projection end 78 it is tapered, to be easy to engage projection 30 the gearshift breach 32 of annular solid 34 in.
Similar to gearshift pin end 72, it is embodied as also dependent on Figure 13 a to 13d in this projection end 78 point, convex spherical
Or it is inclined.
Pin end 72 of shifting gears is also similarly to, each projection 30 also can expand first towards its free axial projection end 78
It is greatly and then tapered again, so as to form favourable lateral incision 76.
Figure 14 illustrates another form of implementation of shift gear driver 12, wherein the ground construction of the same one of annular solid 34 but not
It is same as above-mentioned form of implementation and is not constructed to flat annular disk.Annular solid 34 has in this case axial centre face E, its central diameter
To ground in the first profile 36 (that is, in the interior teeth portion of radially inner side) and (that is, the circumferentially side on radial outside of the second profile 40
To 14 circular edges) between outer toothed portion 80 is constituted in the annulus section 82 of annular solid 34, the wherein such molding of annular solid 34 makes
Annulus section 82 in axial direction each other/be alternately extended median plane E.
Outer toothed portion 80 is embedded in the complementary interior teeth portion of clutch body 26 when gear is shifted gears, so as to along the circumferential direction 14 are being driven
The sealed connection of shape is formed between axle 38 and the driven pulley 28 shifted gears.
Axial blade tooth teeth portion is by means of the projection 30 according to the first form of implementation and gearshift breach 32 or by means of according to the
The gear shift pin 66 of two forms of implementation, gearshift breach 32 and gear shift pin opening 68 it is last in the form of implementation according to Figure 14 by being segmented
Outer toothed portion 80 and (unshowned) complementary interior teeth portion replace.
Claims (15)
1. a kind of shift gear driver of flywheel sychronising formula variator (10), including can be around the ring of the one of transmission axis (A) rotation
Body (34), the annular solid
There is the first profile (36) in its radially inner side, for can not with the relative rotation and can be axially movably with power transmission shaft (38)
Connection；
There is the second profile (40) in its radial outside, for axially coupled with the shifting element (42) of energy axially-movable；And
There are synchronous breach (24), each axial projections (18,20,22) of drag ring (16) between radially inner side and radial outside
Can be embedded in each synchronous breach,
Wherein annular solid (34) also has individually gearshift breach (32) between radially inner side and radial outside, for clutch
Body (26) can not couple with the relative rotation.
2. shift gear driver according to claim 1, it is characterised in that the first profile (36) is interior teeth portion, and/or second
Profile (40) is in the circular gearshift groove (46) of radial outside.
3. shift gear driver according to claim 1 and 2, it is characterised in that be provided with pressure piece in annular solid (34) and open
Mouth (48), for accommodating spring-loaded pressure piece (50).
4. shift gear driver according to claim 3, it is characterised in that integrated respectively in each pressure piece opening (48)
One synchronous breach (24) and/or two gearshifts breach (32).
5. shift gear driver according to claim 1, it is characterised in that the synchronous breach of at least one of annular solid (34)
(24) defined by synchronous inclined-plane (56), the synchronous inclined-plane can with it is corresponding, construction drag ring (16) arranging axial projections
(18) the synchronous inclined-plane (58) on reclines.
6. shift gear driver according to claim 1, it is characterised in that gearshift breach (32) is than synchronous breach (24) radial direction
More inner setting.
7. shift gear driver according to claim 1, it is characterised in that annular solid (34) is with more than synchronous breach (24)
Gearshift breach (32).
8. shift gear driver according to claim 1, it is characterised in that be provided with gear shift pin (66), each gear shift pin being capable of axle
Stretch out to the gearshift breach (32) for extending through annular solid (34), at least one end face axial for protruding from annular solid (34) and
In being embedded in the gear shift pin opening (68) constructed on clutch body (26).
9. shift gear driver according to claim 8, it is characterised in that each gear shift pin has backstop (70), for making
Gear shift pin (66) is relative to annular solid (34) axially position.
10. shift gear driver according to claim 8 or claim 9, it is characterised in that each gear shift pin (66) is changed at least one
Backing pin end (72) taper is tapered.
11. shift gear drivers according to claim 8, it is characterised in that each gear shift pin (66) is with gearshift gap segments
(74), the gearshift gap segments adjoin in mounted condition annular solid (34), and wherein gear shift pin (66) is in gearshift gap segments
(74) there is lateral incision (76) and the gearshift pin end (72) of axial direction between.
A kind of 12. flywheel sychronising formula variators for motor vehicles, including：
The shift gear driver (12) that can be moved axially according to any one of claim 1 to 7,
At least one drag ring (16) that along the circumferential direction (14) couple with shift gear driver (12), the drag ring has axially prominent
Rise (18,20,22), each projection can be put in the synchronous breach (24) of shift gear driver (12), and
At least one clutch body (26), the clutch physical ability along the circumferential direction (14) can not with the relative rotation with shift gear driver
(12) couple,
Axially projecting projection (30) is wherein molded on clutch body (26), the gearshift of the embedded shift gear driver of each projection lacks
Can not couple with the relative rotation with shift gear driver (12) in mouthful (32).
13. flywheel sychronising formula variators according to claim 12, it is characterised in that each projection (30) is towards free axle
It is tapered to projection end (78).
A kind of 14. flywheel sychronising formula variators for motor vehicles, including：
The shift gear driver (12) that can be moved axially according to any one of claim 8 to 11,
At least one drag ring (16) that along the circumferential direction (14) couple with shift gear driver (12), the drag ring has axially prominent
Rise (18,20,22), each projection can be put in the synchronous breach (24) of shift gear driver (12), and
At least one clutch body (26), the clutch physical ability along the circumferential direction (14) can not with the relative rotation with shift gear driver
(12) couple and be arranged on the end face for protruding from annular solid (34) of gear shift pin (66),
, with gear shift pin opening (68), gear shift pin (66) can be embedding when shift gear driver (12) is moved axially for wherein clutch body (26)
In entering the gear shift pin opening.
The 15. flywheel sychronising formula variators according to any one of claim 12 to 14, it is characterised in that clutch body (26)
It is configured to more by radial outside than conical friction face (64), and can reclines with the rubbing surface (62) of drag ring (16).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102012001836.3 | 2012-01-31 | ||
| DE102012001836.3A DE102012001836B4 (en) | 2012-01-31 | 2012-01-31 | Shift transmitter of a limited slip synchronized manual transmission |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103225655A CN103225655A (en) | 2013-07-31 |
| CN103225655B true CN103225655B (en) | 2017-05-17 |
Family
ID=48783536
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201310025326.5A Active CN103225655B (en) | 2012-01-31 | 2013-01-23 | A shift gear driver of a flywheel synchronous transmission |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN103225655B (en) |
| DE (1) | DE102012001836B4 (en) |
| FR (1) | FR2986290B1 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102013106861A1 (en) * | 2013-07-01 | 2015-01-08 | Hoerbiger Antriebstechnik Holding Gmbh | Synchronization unit for frictional torque transmission in a manual transmission |
| DE102014118913A1 (en) * | 2014-12-17 | 2016-06-23 | Hoerbiger Antriebstechnik Holding Gmbh | Transmitter for a synchronization assembly of a manual transmission |
| DE102014118914B4 (en) * | 2014-12-17 | 2024-03-07 | Hoerbiger Antriebstechnik Holding Gmbh | Pressure piece for a transmitter of a synchronization assembly of a manual transmission and transmitter |
| DE102016102701A1 (en) * | 2016-02-16 | 2017-08-17 | Hoerbiger Antriebstechnik Holding Gmbh | Synchronizing device and synchronization method |
| EP3682131B1 (en) * | 2017-09-12 | 2021-11-17 | Gkn Automotive Ltd. | Overrunning clutch |
Family Cites Families (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE1101057B (en) | 1955-02-02 | 1961-03-02 | Daimler Benz Ag | Lock-synchronized dog clutch |
| FR2466668A1 (en) * | 1979-10-05 | 1981-04-10 | Peugeot | Synchronising mechanism for gear-box - has single piece pawl rings stamped from sheet and formed with axial feet with oblique end faces |
| FR2851022B1 (en) * | 2003-02-07 | 2005-04-29 | Peugeot Citroen Automobiles Sa | SYNCHRONIZATION DEVICE FOR MECHANICAL GEARBOX |
| JP2005114156A (en) * | 2003-09-19 | 2005-04-28 | Nissan Motor Co Ltd | Synchronizer for transmission |
| CN102575724B (en) * | 2009-09-14 | 2014-10-08 | 贺尔碧格传动技术控股有限公司 | Assembly comprising two synchroniser rings |
-
2012
- 2012-01-31 DE DE102012001836.3A patent/DE102012001836B4/en active Active
-
2013
- 2013-01-23 CN CN201310025326.5A patent/CN103225655B/en active Active
- 2013-01-30 FR FR1350782A patent/FR2986290B1/en active Active
Also Published As
| Publication number | Publication date |
|---|---|
| FR2986290A1 (en) | 2013-08-02 |
| FR2986290B1 (en) | 2017-04-28 |
| DE102012001836A1 (en) | 2013-08-01 |
| CN103225655A (en) | 2013-07-31 |
| DE102012001836B4 (en) | 2022-10-13 |
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