CN1089149C - Synchronizing apparatus for transmission - Google Patents
Synchronizing apparatus for transmission Download PDFInfo
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- CN1089149C CN1089149C CN96111837A CN96111837A CN1089149C CN 1089149 C CN1089149 C CN 1089149C CN 96111837 A CN96111837 A CN 96111837A CN 96111837 A CN96111837 A CN 96111837A CN 1089149 C CN1089149 C CN 1089149C
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- lever
- sleeve
- synchronizing ring
- speed change
- change gear
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Abstract
A magnification mechanism is provided between the hub of a warner-type synchronizing device and the synchronizing ring, the magnification mechanism magnifies a pressing force and transmits this force to one side of synchronizing rings following the movement of a sleeve. In addition to the magnification device in a forward speed changing gear side, a backward synchronizing mechanism for stopping the rotation of a drive shaft by inverting a pressing force and transmitting this force to the synchronizing rings and so as to exert synchronizing force when receiving a pressing force by the reverse shifting of the sleeve is provided.
Description
The present invention relates to be used for the synchronizer of automatic transimission, the invention particularly relates to and to make net synchronization capability obtain improved Warner formula synchronizer.
Warner formula synchronizer is a kind of common synchronizer that is used for automatic transimission.The working principle of Warner formula synchronizer is known as follows: the inclined-plane on the synchronizing ring outer rim is subjected to the compressing on the inclined-plane on the sleeve spline, like this, frictional force on the synchronizing ring inner edge conical surface and the speed change tooth between the outer rim conical surface makes that just synchronous effect is achieved, thereby has eliminated the speed discrepancy between sleeve and the speed change gear.Synchronous effect can make sleeve spline be meshed with the engagement sleeve of speed change gear reposefully.That is to say that in Warner formula synchronizer, the moving sleeve by handling shifting fork, a certain key pin just can be pressed in the groove of synchronizing ring along with moving of sleeve.Then, synchronizing ring is crushed on the outer rim conical surface on the speed change gear, and speed change gear begins because of the frictional force of its outer rim conical surface synchronously.When the projection of key pin is removed from the groove of sleeve interior surface (this moment, sleeve continued to move), the inclined-plane of the inboard splined end of sleeve can lean against the end of synchronizing ring spline, thereby synchronizing ring has thrust function to sleeve.Like this, synchronizing ring can produce bigger frictional force because of its cone-shaped inner surface pressurized under the weight of sleeve.More than action is exactly the synchronizing process of sleeve and speed change gear.Do not have relative speed difference between above-mentioned synchronizing process end and sleeve and speed change gear after, friction torque will disappear, and synchronizing ring is still rotatable, and sleeve can be crossed synchronizing ring and be meshed with the engagement sleeve of speed change gear, thereby finishes speed-change process.
Yet in having the conventional synchronizer of as above working principle, the power that synchronizing ring is pressed on the speed change gear outer rim conical surface equates with the power that the operating mechanism shifting fork acts on the sleeve.Therefore just have such problem: the increase of capacity synchronously is accompanied by the increase of structural complexity, that is needs to increase the conical surface, increases conical surface number, or the like, therefore, be difficult to increase synchronous capacity with simple structure.In addition, for advance five grades/fall one grade speed change gear, at the sleeve of the 5th grade of gear when mobile with the 5th grade of direction that gear is opposite (reverse gear gear direction), if live axle can with the 5th grade of synchronous stall of gear, the reverse gear gear just can not send noise when gear shift so.Yet the problem of conventional synchronizer is: be reversed when mobile at sleeve, synchronous effect is difficult to realize.
The synchronizer that is used for speed change gear as described herein can be realized the remarkable increase of synchronous capacity with simple structural modification.
The synchronizer of speed change gear of the present invention comprises with the bottom: in order to the output shaft of output rotary motive power; Outer rim has spline and is fixed tightly in axle sleeve on the output shaft; The sleeve that can be in axial sliding, the spline on its inner rim can be inserted in the outer rim spline of axle sleeve; With the output shaft is the speed change gear of revolution pivot, be provided with the outer rim conical surface and engagement sleeve at it near axle sleeve one side, engagement sleeve extends from the speed change gear body and forms and mutually continuous with the outer rim conical surface, and it can be meshed with the inner edge spline of sleeve by axial motion; Synchronizing ring between the sleeve and the above-mentioned outer rim conical surface, its inner rim conical surface is relative with the outer rim conical surface of speed change gear.With regard to above-described synchronizing ring structure, the invention is characterized in: the booster body between axle sleeve and synchronizing ring has born by sleeve and has moved the active force that is produced and make the gain of this active force and pass to synchronizing ring to speed change gear.
Booster body contains a pair of prominent shape fulcrum as fulcrum, and fulcrum is to form by at least two place's symmetrical positions on axle sleeve one side end face are outstanding in synchronizing ring.A pair ofly be positioned at the both sides of prominent shape fulcrum and the certain spacing of being separated by with it at the levers that circumferentially are divided at least two joints.Two lever radially expansions under pressure.Lever head stretches out the center portion of outer rim at lever.Each lever head is provided with chamfered edge, and chamfered edge bears the axial pressure that is produced by the sleeve motion and this pressure can be decomposed into entad warp-wise component and axial thrust load.In addition, also be provided with the projection as point of application of force on each lever, the effect of this point of application of force is that the axial thrust load that compressing lever head supporting plane is produced is increased and is delivered to the precalculated position on the synchronizing ring end face.Booster body can increase to (the L that sleeve is exerted pressure to the pressure of synchronizing ring
1/ L
2) doubly, at this moment, the distance L from prominent shape fulcrum to point of application of force
2Should be less than distance L from prominent shape fulcrum to supporting plane
1When the synchronizing ring inner edge conical surface and speed change gear outer rim conical surface generation rubbing contact, prominent shape fulcrum should be able to overcome the reaction force of lever end face exerts pressure and the warp-wise component that forms to the chamfered edge of arm of couple lever head, for this reason, the inclination angle of chamfered edge should reasonably be chosen on the booster body.Like this, the fulcrum of lever had both made and has been in pressured state and warp-wise can not take place yet moves, thereby the pressure of gain can be passed to synchronizing ring reliably.A kind of modified model as booster body, be provided with near several symmetrical position places on axle sleeve one side end face if a prominent shape fulcrum of dried overhanging triangle in synchronizing ring, and vertex of a triangle is towards outer rim, simultaneously, several have tri-angle-holed and along the lever that is circular layout respectively with corresponding prominent shape fulcrum tabling.Synchronizing ring can adopt the bicone structure, and wherein contained a certain cone is between outer synchronizing ring and inter-sync ring.The booster body of this structure contains several prominent shape fulcrums as fulcrum, these fulcrums are to protrude near at least two symmetrical position places on axle sleeve one side end face in inside and outside synchronizing ring to form, each lever unit all contains a projection as point of application of force, and the effect of point of application of force is compressing lever head supporting plane formed axial thrust load is gained and to be delivered to precalculated position on the outer synchronizing ring end face.
For as described herein a kind of be used to into five grades/fall the synchronizing ring of one grade of speed change gear, though sleeve is to move towards the direction that deviates from the 5th grade of gear in the reverse gear operation, but the 5th grade of gear can obtain synchronously, thereby the noise when having avoided the reverse gear operation.
In this occasion, purport of the present invention still is the synchronizer of speed change gear, and this synchronizer comprises; Receive the live axle of rotary motive power; Be fixed tightly on the live axle and outer rim has the axle sleeve of spline; Can make its inner rim spline insert sleeve in the axle sleeve outer rim spline by slip; With the output shaft is the forward gears speed change gear of pivot being installed and being positioned at a certain side of axle sleeve, on it near axle sleeve one side have the outer rim conical surface and from body stretch out and with the continuous engagement sleeve of the outer rim conical surface, this clutch can be meshed with the inner edge spline of sleeve by moving axially of sleeve; Synchronizing ring between the above-mentioned outer rim conical surface of sleeve, its inner rim conical surface is relative with the outer rim conical surface that just changes fast gear.
In having the synchronizer of said structure, booster body is between axle sleeve and synchronizing ring as described in the present invention, and this booster body has born because of march forward pressure that the motion of grade speed change gear causes and this pressure increased and pass to synchronizing ring of sleeve.In addition, as a kind of reverse gear synchronous mechanism, this booster body also makes the live axle stall by synchronous effect, and its action principle is: when reverse gear synchronous mechanism was subjected to deviating from the pressure that forward gears speed change gear motion causes because of sleeve, this reverse gear synchronous mechanism can pass to synchronizing ring with pressure reversal.
Booster body contains a pair of first prominent shape fulcrum as first fulcrum, and fulcrum is to form by at least two place's symmetrical positions on axle sleeve one side end face are outstanding in synchronizing ring.A pair of at the levers that circumferentially are divided at least two joints in the both sides of the first prominent shape fulcrum and with it mutually across a certain distance with annular arrangement.This expands along warp-wise because of the pressure that is subjected to a spring to lever.Lever head stretches out from this center portion to the lever outer rim.Each lever has first chamfered edge as first supporting plane, and it can bear because of march forward a axial pressure that the motion of grade speed change gear causes and this pressure can be decomposed into warp-wise and entad be divided into and axial thrust load of sleeve.In addition, also be provided with first convex portion on each lever as point of application of force, the effect of this first point of application of force is to make the axial thrust load of compressing lever head first supporting plane be increased and be delivered to precalculated position on the synchronizing ring end face.Booster body can increase to (the L that sleeve is exerted pressure to the pressure of synchronizing ring
1/ L
2) doubly, at this moment, the distance L from the first prominent shape fulcrum to first point of application of force
2Should be less than distance L from the first prominent shape fulcrum to first supporting plane
1When the synchronizing ring inner edge conical surface and speed change gear outer rim conical surface generation rubbing contact, the first prominent shape fulcrum should be able to overcome the reaction force of lever end face exerts pressure and the warp-wise component that forms to first chamfered edge of arm of couple lever head, for this reason, the cone angle of chamfered edge should reasonably be chosen on the booster body.Like this, the first prominent shape fulcrum of lever had both made and has been subjected to warp-wise pressure and also can move, thereby made the pressure of gain pass to synchronizing ring reliably.Reverse gear synchronous mechanism contains second chamfered edge, this chamfered edge be on the lever head near forming on the edge of forward gears speed change gear one side, as second supporting plane, it has born because of sleeve and has deviated from the pressure that the motion of forward gears speed change gear causes.In addition, reverse gear synchronous mechanism contains the second prominent shape fulcrum that is positioned at the axle sleeve end face, when second point of application of force of each lever end affacted second supporting plane of second chamfered edge, the above-mentioned second prominent shape fulcrum had served as second fulcrum that above-mentioned pressure reversal is passed to synchronizing ring at pressure.In reverse gear synchronous mechanism, the distance L from second fulcrum to second supporting plane
3Be substantially equal to distance L from second fulcrum to second point of application of force
4
The detailed description of doing below in conjunction with accompanying drawing will be introduced more clearly and above address and do not add the object of the invention, feature and the advantage of addressing.
Brief description
Fig. 1 is a synchronizer sectional view of being furnished with booster body as described herein, and this figure is an example with bottom gear and second grade of speed change gear.
Fig. 2 is a synchronizer sectional view as described in the present invention, and this figure has omitted the part of second grade of speed change gear one side among Fig. 1.
Fig. 3 is the sectional view of being done along III-IV line among Fig. 2, and this figure has omitted the sleeve part.
Fig. 4 is the profile stretch-out view of being done along IV-IV line among Fig. 1, and this figure is outer side view and does not contain the axle sleeve part.
Fig. 5 is the diagram that concerns between synchronizing ring and the lever.
Fig. 6 is a synchronizer sectional view of being furnished with booster body and reverse gear synchronous mechanism as described herein.
Fig. 7 is the sectional view of being done along VII-VII line among Fig. 6 that omits the sleeve part.
Fig. 8 is the profile stretch-out view of being done along VIII-VIII line among Fig. 6 that omits axle sleeve outer side view part.
Fig. 9 is the diagram that concerns between synchronizing ring among Fig. 6 and the lever.
Figure 10 illustrates the speed change pattern of speed change lever in five grades of speed change gears.
Figure 11 has described to be furnished with the major component of the synchronizer of booster body as described in another embodiment of the present invention.
Figure 12 is a synchronizer sectional view of being furnished with booster body as described in another embodiment of the present invention.
Figure 13 is the synchronizer sectional view as employing bicone structure as described in another embodiment of the present invention.
Figure 14 is the sectional view of being done along XIV-XIV line among Figure 13 that does not contain the sleeve part.
The preferred embodiment explanation
Fig. 1 is a synchronizer sectional view of being furnished with booster body as described herein.Bootom gear 140 among the figure and second grade of speed change gear 14 are installed on the gyroscopic output pivot 10 by bearing 120,12, are provided with synchronizer 100 between two speed change gears.Rotary motive power is from motor, by clutch, passes to bottom gear speed change gear 140 and second grade of speed change gear 14 via the idle pulley (not shown).The axle sleeve 22 of synchronizer meshes and is fixed tightly on the splined shaft 10-1 between second grade of speed change gear and the bottom gear speed change gear by its inner rim spline.The outer rim of axle sleeve 22 has outer rim spline 26.The inner edge spline 30 of sleeve 28 keeps and can mesh in axial sliding with the outer rim spline of axle sleeve 22, and the outer rim of sleeve 28 has fork groove 38.Engagement sleeve 16 extends naturally near a side of sleeve 28 from second grade of speed change gear 14 and forms, and its effect is that the inner edge spline 30 of sleeve 28 inner edges is meshed with engagement sleeve 16.Also be provided with the outer rim conical surface 18 with engagement sleeve 16 connecting places.Part height relative with the outer rim conical surface 18 on synchronizing ring 40 has the inner edge conical surface 42.In addition, engagement sleeve 160 extends naturally near a side of sleeve 28 from the bottom gear speed change gear 140 and forms, and it is meshed with the inner edge spline 30 of sleeve 28 inner edges.Also be provided with the outer rim conical surface 180 with engagement sleeve 160 connecting places.Part relative with the outer rim conical surface 180 on synchronizing ring 400 is provided with the inner edge conical surface 420.In addition, in the present invention, booster body is between synchronizing ring 40,400 and axle sleeve 22.
Fig. 2 is the synchronizer that only contains second grade of speed change gear part among Fig. 1.Although hereinafter as the example introduction be second grade of speed change gear 14, bottom gear speed change gear 140 parts are similar to second grade of speed change gear 14 part structurally.The a pair of lever 50-1 of formation booster body and 50-2 are between synchronizing ring 40 and axle sleeve 22.Fig. 3 clearly shows lever 50-1 and the assembling form of 50-2 on axle sleeve 22 that constitutes booster body, and this figure is the sectional view of being done along III-III line among Fig. 2.It may be noted that and do not contain sleeve 28 parts among Fig. 3.
In Fig. 3, because of being horseshoe-shaped lever 50-1 and 50-2 respectively and being mounted in spoke recess between axle sleeve 22 hub flanges and the outer rim spline 26 circumferentially being divided into two joints.The edge center portion has lever head 52-1 and the 52-2 that the nature extension forms outside lever 50-1 and the 50-2.The apart determining deviation in the end of two lever 50-1,50-2 is piece shape prominent shape fulcrum 44-1, the 44-2 that stretches out near second grade of speed change gear one side end face from synchronizing ring 40 in the spacing.The annular spring 60 of certain local excision is installed in lever 50-1,50-2 inboard, so that lever 50-1,50-2 are in radially pressurized and expansion.So the spring of installing 60 can make prominent shape fulcrum 44-1, and 44-2 and two lever 50-1 form certain clearance 45-1,45-2 between the end of 50-2.
The sectional view of Fig. 2 clearly shows: lever 50-1, and lever head 52-1, the 52-2 of 50-2 have L shaped cross section, and one is terminal to be pointed to second grade of speed change gear 14 1 side and its and goes up close sleeve 28 1 side margin and be provided with chamfered edge 54-1,54-2.The scarf 36 and the chamfered edge 54-1 in sleeve 28 inner edge splines 30 left sides, 54-2 contacts.The profile stretch-out view Fig. 4 that is done along IV-IV line among Fig. 2 clearly shows sleeve 28 inner edge splines 30, and the engagement sleeve 16 of coupling gear and synchronizing ring 40 threes are with respect to the relation of lever head 52-1.
In Fig. 4, the lever head 52-1 projection corresponding to lever 50-1 on the sleeve 28 inner edge splines 30 is cut, has also formed the relative scarf of position 54-1 of cutting sth. askew with lever head 52-1 simultaneously.Like this, be subjected to the shifting fork effect and during to engagement sleeve 16 1 side shiftings, the chamfered portion 54-1 of lever head 52-1 will be subjected to the compressing of the scarf 36 of inner edge spline 30 cut-out (see figure 2)s at sleeve 20.Therefore, lever head 52-1 constitute sleeve 28 move due to the carrier of pressure.
Fig. 5 is an axle sleeve 22 shown in Figure 2, the partial sectional view of sleeve 28 and second grade of speed change gear 14 1 side synchronizing ring 40 (wherein synchronizing ring 40 is an external view).Prominent shape fulcrum 44-1 end face near axle sleeve 22 1 sides on the synchronizing ring 40 stretches out.See easily that by Fig. 3 prominent shape fulcrum 44-2 is positioned at and the relative opposite side in shape fulcrum 44-1 orientation of dashing forward.Prominent shape fulcrum 44-1 is the lever 50-1 of both sides up and down, and 50-2 is the spring 60 compressing lower edge radial expansions of side within it.Lever head 52-1, the 52-2 of lever 50-1,50-2 has the chamfered edge 54-1 relative with the scarf 36 of sleeve 28 inner edge splines 30,54-2.In addition, lever 50-1, the end face of 50-2 are provided with the prominent shape fulcrum 58-1 relative with synchronizing ring 40,58-2, and lever 50-1,50-2 can be by prominent shape fulcrum 58-1,58-2 and leaning against on the end face of synchronizing ring 40.Prominent shape fulcrum 58-1,58-2 has constituted lever 50-1, and 50-2 is to the point of application of force of synchronizing ring 40.At lever 50-1, the chamfered portion 54-1 of 50-2,54-2 and prominent shape point of application of force 58-1,58-2 is assumed that respectively under the condition of supporting plane and point of application of force, lever 50-1,50-2 will be in the prominent shape fulcrum 44-1 with synchronizing ring, the contacted position of 44-2.That is to say, synchronizing ring 40 is subjected to lever 50-1 as booster body because of the motion of sleeve 28, the compressing of 50-2, consequent contact friction force will start synchronizing process, under the contact friction force effect that causes because of second grade of speed change gear 14 outer rim conical surface 18 of the synchronizing ring 40 inner edge conical surfaces, 42 compressings, the lower-left end of upside lever 50-1 (one of possible situation) can lean against the prominent shape fulcrum 44-1 among Fig. 3.Simultaneously, the upper right side of downside lever 50-2 also can lean against on the fulcrum 44-2, and therefore, the formation of balance pivot is by lever 50-1, and the respective end of 50-2 leans against prominent shape fulcrum 44-1, last and the realization of 44-2.
Following introduction is still carried out around lever 50-1 in conjunction with Fig. 5.If the position of the fulcrum when lever 50-1 end leans against on the synchronizing ring 40 prominent shape fulcrum 44-1 is O, the working position that acts on the pressure on the lever head 52-1 chamfered edge 54-1 because of sleeve 28 motions is P, and the position of the prominent shape point of application of force 58-1 of lever 50-1 end face is Q, then make fulcrum O to the distance of supporting plane P be L
1, and point of application of force Q to the distance (shorter) of fulcrum O be L
2Suppose that the axial pressure that acts on the supporting plane P is F
In, the axial pressure that is acted on the synchronizing ring 40 by point of application of force Q is F
Out, then can set out and derive following relation by fulcrum O, supporting plane P and the relation of point of application of force Q three on lever 50-1
F
in×L
1＝F
out×L
2 (1)
Therefore, act on power F on the point of application of force Q
OutCan show to be following formula:
F
out＝F
in×(L
1/L
2) (2)
Because of L
1＞L
2So, (L
1/ L
2) greater than 1, therefore, the power F that synchronizing ring 40 is suffered
OutBe the pressure F that sleeve 20 motions are produced
InBe amplified to (L
1/ L2) the result after doubly.
On the other hand, act on axial pressure F on the lever head 52-1 supporting plane P because of sleeve 28 motion
InSynchronously be decomposed into axial force and radial centripetal power.Like this, the prominent shape fulcrum 44-1 of synchronizing ring 40 just can be oppressed in the end of lever 50-1.At this moment, if synchronizing ring 40 moves because of the effect of lever 50-1 pressure, the axial thrust load that acts on chamfered edge 54-1 place so will reduce greatly, thereby makes the booster body disabler.Therefore, the reaction force that produces on the synchronizing ring 40 rubbing contact surfaces must be able to overcome because of sleeve 28 motion and acts on pressure on the prominent shape fulcrum 44-1 of lever 50-1.For this reason, the inclination angle of chamfered edge 52-1 should be chosen by following principle among the present invention: because of contact friction force due to the synchronous effect must can overcome the radial component that moves and oppress lever 50-1 because of sleeve 28 to the reaction force of synchronizing ring 40 prominent shape fulcrum 44-1.
Below introduce Fig. 2-running embodiment illustrated in fig. 5.In Fig. 2, shifting fork of not drawing is inserted in the fork groove 38 on sleeve 28 outer rims, in variable speed operation, sleeve 28 is pressed to the left side by the action of shifting fork, thereby realizes the rate conversion towards second grade of speed change gear.Along with moving to left of sleeve 28, the scarf 36 of sleeve 28 inner edge splines 30 at first leans against lever 50-1, and the chamfered edge 54-1 of 50-2 on the 54-2, and oppresses lever 50-1 to the left, and 50-2 can then make synchronizing ring 40 pressurizeds again.Therefore, the synchronizing ring 40 inner edge conical surfaces 42 can come in contact with the outer rim conical surface of second grade of speed change gear, and at this moment, and 22 on axle sleeve exists second grade of speed change gear 14 of speed discrepancy to enter synchronizing process owing to keeping in touch with synchronizing ring 40.When second grade of speed change gear 14 begins to enter synchronizing process because of rubbing contact, synchronizing ring 40 can be with respect to lever 50-1,50-2 rotates (under original state shown in Figure 2, lever 50-1,50-2 and prominent shape fulcrum 44-1, have gap 45-1 between 44-2,45-2) and prominent shape fulcrum 44-1,44-2 can pressurized.In this state, by the fulcrum O on the lever (lever 50-1 as shown in Figure 4), supporting plane P and point of application of force Q three can set up the relation with leverage.The pressurized effect that synchronizing ring 40 is also embodied because of above-mentioned formula (2) is subjected to the effect of big pressure.Simultaneously, the reaction force (moment) that produces because of synchronizing ring 40 rubbing contact has overcome the radial centripetal pressure of sleeve 28 pressure to lever 50-1, and like this, prominent shape fulcrum 44-1 just can not be moved.Therefore, the pressure of sleeve 28 passes to synchronizing ring 40 after initial value is amplified.Because of pressurization pressurized and its rotating speed and second grade of speed change gear 14 when consistent, because friction torque disappears, lever 50-1,50-2 no longer are subjected to by synchronizing ring 40 prominent shape fulcrum 44-1, pressure that 44-2 transmits and restoring force in synchronizing ring 40.Therefore, the inclined-plane 36 of sleeve 28 will overcome the counter-force of spring 60 and with lever 50-1,50-2 forces compressing to the inside, so reposefully with engagement sleeve 16 engagements.36 couples of lever 50-1 of inner edge spline 30 scarves, the inside contention effect of the pressure of 50-2 can make synchronizing ring rotate to its initial position (with the gap 45-1 under the original state shown in Figure 2,45-2 represents), therefore, after variable speed operation was finished, synchronizing ring 40 can be got back to its original state once more.
Fig. 6 be about advance five grades/fall another embodiment of the present invention of one grade of speed change gear, it comprises the 5th grade of speed change gear synchronizer and reverse gear synchronous mechanism being furnished with booster body, when the reverse gear speed change gear carries out variable speed operation (this moment sleeve movement direction deviate from the 5th grade of speed change gear), reverse gear synchronous mechanism can make sleeve and the 5th grade of speed change gear synchronous.
In Fig. 6, the 5th grade of speed change gear 14-1 is installed in by bearing 12 and drives on the pivot 102.The synchronizer axle sleeve 22 that joins with the 5th grade of speed change gear 14-1 meshes and is fixed tightly on the splined shaft 102-1 by spline 20, and axle sleeve 22 provides thrust by clasp 24.Engine power is given live axle 102 by clutch transmits, and the 5th grade of speed change gear 14-1 meshes with the 5th grade of actuation gear (being contained in a certain not adding on the illustrated output shaft).In addition, a reverse drive gear does not add illustrated output shaft and links to each other with above-mentioned, is provided with a certain reverse idler gear (being moved and locking by the reverse gear operation) between this reverse drive gear and its driven gear.When the reverse gear variable speed operation carried out against the 5th grade of operation, reverse idler gear was sent between reverse drive gear and the reverse gear driven gear the two is meshing with each other, thereby return motion just is delivered to output shaft.For example, the F50A type speed change gear that Nissan Motor Co produces has just adopted said method, i.e. reverse gear operation is reverse with the 5th grade of operation.
The lazy-tongs of the 5th grade of speed change gear 14-1 and embodiment illustrated in fig. 2 in the basic machine of situation with.That is retainer shaft is to sliding gomphosis between the inner edge spline 36 of sleeve 28 (being furnished with fork groove 38) and the outer rim spline 26 of axle sleeve 22.Engagement sleeve 16 forms on the 5th grade of speed change gear body and is adjacent with a certain outer rim conical surface 18.Synchronizing ring 40 with inner edge conical surface 42 is relative with the above-mentioned outer rim conical surface 18.A pair of horse shoe shaped lever 50-1 between synchronizing ring 40 and axle sleeve 22,50-2 because of the effect of its inboard spring 60 at pressurized radially and expand.Lever 50-1, the center portion of 50-2 outer rim has overhanging lever head 54-12,54-22.With lever head 54-12 is example, its towards and the both sides that deviate from the 5th grade of speed change gear 14-1 the second and first chamfered edge 54-12,54-11 are arranged respectively.Have and chamfered edge 54-11 on the sleeve 28 inner edge splines 36, the corresponding hypotenuse rectangle of 54-12 carriage form, its scarf 36-11 is corresponding to chamfered edge 54-11, scarf 36-12 is corresponding to chamfered edge 54-12, and the lever head 52-2 of downside lever 50-2 has the structure identical with the lever head 52-1 of above-mentioned lever 50-1 among the figure.
Fig. 7 is the sectional view of being done along VII-VII line among Fig. 6 that does not contain sleeve 28.See easily that by Fig. 7 semicircle lever 50-1,50-2 are contained in the annular groove between axle sleeve 22 hub portions and the outer rim spline 26.From the prominent shape fulcrum 44-1 that synchronizing ring 40 end faces stretch out, 44-2 is positioned at two lever 50-1, between the end of 50-2, because spring 60 makes lever in radially pressurized and expansion, has formed certain clearance 45-1 between the end of two levers, 45-2.
Fig. 8 is the profile stretch-out view of being done along VIII-VIII line among Fig. 6, and this figure has disclosed the relation between sleeve 28 inner edge splines 30 and the lever 50-1 lever head 52-1.That is, because cut corresponding to the part of the overhanging lever head 52-1 of lever 50-1 on the sleeve 28 inner edge splines 30, thus just formed respectively in the right side of lever head 52-1, right both sides with the corresponding first scarf 36-11 of the first chamfered edge 54-11 and with the corresponding second scarf 36-12 of the second chamfered edge 54-12.
Fig. 9 is with respect to the sleeve 28 of synchronizing ring 40 external view and axle sleeve 22 partial sectional views.With lever 50-1 is example, leans against first bearing surface that the first chamfered edge 54-11 on the sleeve 28 inner edge splines 36 scarf 36-11 has constituted the 5th grade of speed change gear synchronizer booster body.When starting synchronizing process, it is the position of first fulcrum that lever 50-1 goes up a certain end that leans against on the prominent shape fulcrum 44-1 because of rubbing contact.In addition, be positioned at lever 50-1 and constituted point of application of force near a certain bump body 58-1 on the synchronizing ring 40 1 routine end faces.Because downside lever 50-2 has said structure equally, first supporting plane of therefore oppressing sleeve 28 scarf 36-11 is that the first chamfered edge 54-2 by lever head 52-2 right side constitutes, and first fulcrum is positioned at the shape fulcrum 44-2 that dashes forward and (is positioned at the relative opposite side with prominent shape fulcrum 44-1, referring to Fig. 6) a certain end of lever leaned on mutually, in addition, first point of application of force is positioned at a certain bump body 58-2 place of leaning on mutually with synchronizing ring 40 end faces.Position first fulcrum of this supposition lever 50-1, supporting plane, point of application of force three is represented by O1, P1, Q1 respectively, then can obtain being similar to the following pressurization representation of above-mentioned relation formula (2)
F
out1＝F
in1×(L
1/L
2) (3)
Be presented in the reverse gear synchronous mechanism that is adopted when the speed change gear operation is carried out against the 5th grade of speed change gear 14-1 direction below in conjunction with Fig. 6.The booster body of reverse gear synchronous mechanism and the 5th grade of speed change gear 14-1 synchronizer is an one.Be example at first with lever 50-1, its reverse gear synchronous effect is as follows: when carrying out variable speed operation against the direction of the 5th grade of speed change gear 14-1, by making live axle 10 and the 5th grade of speed change gear 14-1 make live axle 10 stalls synchronously, for this reason, the side that lever head 52-1 goes up near the 5th grade of speed change gear is provided with the second chamfered edge 54-12, and sleeve 28 is provided with the scarf 36-12 relative with the second chamfered edge 54-12 simultaneously.Therefore, when sleeve 28 moves against the 5th grade of speed change gear 14-1 direction, the second chamfered edge 54-12 of lever head 52-1 can be subjected to the pressure of scarf 36-12, and lever 50-1 makes this pressure that deviates from the 5th grade of speed change gear 14-1 be converted to towards the 5th grade of speed change gear 14-1 and makes it to act on synchronizing ring 40.As pressure reversal mechanism is the set extension 64-1 of lever 50-1, and 64-2 is that stretch out the position that combines with axle from axle sleeve 22 end faces, and lever 50-2 also correspondingly is provided with extension 64-3,64-4, as shown in Figure 7.See easily that by axle sleeve 22 sectional views shown in Figure 9 extension 64-1 to 64-4 leans against lever 50-1 substantially, the mid point of 50-2, its edge section has constituted lever 50-1, the fulcrum O2 of 50-2.In addition, the second chamfered edge 54-12 of lever head 52-1 has constituted the second point of application of force P2 with respect to the second fulcrum O2.In addition, the lever 50-1 end side that is positioned at fulcrum O2 downside has constituted the second point of application of force Q2 to synchronizing ring 40.The second fulcrum Q2 is the trapezoidal extension 46-1 that forms in the overhanging prominent shape fulcrum 44-1 of synchronizing ring 40 end faces both sides, 46-2.
The pressure representative to lever 50-1 second chamfered edge that is produced when sleeve is moved against the 5th grade of speed change gear 14-1 is F
In2, the backpressure that acts on synchronizing ring 40 trapezoidal extension 46-1 point of application of force Q2 is expressed as F
Out2, use L
4Expression fulcrum O2 uses L to the distance of the second supporting plane P2
3Expression fulcrum O2 then can obtain following relation to the distance of the second point of application of force Q2
Therefore, act on backpressure F on the synchronizing ring 40
Out2 can be expressed from the next
Make L
3With L
4About equally, then act on backpressure F on the synchronizing ring 40
OutThe 2 pressure F that will be produced with sleeve 28 motion
In2 equate.When synchronizing ring 40 is subjected to above-mentioned backpressure, its inner rim conical surface 42 will be pressed on the outer rim conical surface 18 of the 5th grade of speed change gear 14-1 and realize rubbing contact with it.Therefore, when clutch is thrown off in the reverse gear operation, live axle 10 was rotated because of inertia, it still can be because of synchronizing ring 40 and static the 5th grade of speed change gear 14-1 maintenance rubbing contact stall, like this, reversing idle pulley not shown in the figures can imbed under the situation that does not produce noise between reversing actuation gear and the reversing driven gear.
Below introduce Fig. 6 to operation conditions embodiment illustrated in fig. 9.At first, the 5th grade of variable speed operation of variable speed operation and forward gears shown in Figure 1 to the 5th grade of speed change gear 14-1 of forward gears shown in Figure 5 is identical with tool embodiment illustrated in fig. 1, that is when the 5th grade of speed change gear of speed change lever tuning, sleeve 28 moves to left not adding under the illustrated shifting fork effect.Therefore, lever 50-1,50-2 lever head 52-1, the first chamfered edge 54-11 on 52-2 right side, 54-21 just are subjected to the axial pressure of sleeve 28 inner edge splines 36 chamfered portion 36-11, like this, because of being pressed in the rubbing contact that causes on the 5th grade of speed change gear 14-1 outer rim conical surface 18, the synchronizing ring 40 inner edge conical surfaces 42 just facilitated synchronizing process, when synchronizing process finishes, the spline 36 of sleeve 28 will mesh with engagement sleeve 16, and then finish variable speed operation.
When below introducing reverse gear against the variable speed operation of the 5th grade of speed change gear 14-1 direction.General advance five grades/fall in one grade of speed change gear, the driver is to the operator scheme of speed change lever as shown in figure 10.The 5th grade of gear 90 is usually located at same row with reverse gear gear 92 and separates from middle gear both sides.In addition, stop but under the condition that motor is still worked at vehicle, if carry out the shift operation of throw-out-of clutch, though the speed change gear output shaft stall of so close live axle one side, but still can together rotate because of inertia and clutch disk near the live axle of sending out machine machine one side.Therefore, if the not stall when shift of input end live axle, the so-called gear noiose phenomenon that occurs when the speed change gear gear shift will cause uncomfortable gear tooth noise so.Generally speaking, advance grade speed change gear and all be furnished with synchronizer, and the reverse gear speed change gear does not have.Therefore, carry out making the vehicle backward in the gear shift of reverse gear, the possibility that produces gear noiose is sizable, the reverse gear method of gearless noise is generally as follows: carry out the reverse gear operation by holdback clutch before, do the shift operation towards advancing five grades of speed change gears earlier, thereafter, because the stall under the effect of advancing five grades of speed change gear synchronizers of input end live axle, so the reverse gear operation just can be finished under the condition of throw-out-of clutch.That is to say, if in the reverse gear operation, manage to realize the stall of input end live axle, just the reverse gear operation can not cause gear noiose so with the action of advancing grade speed change gear synchronizer.To the embodiment shown in Figure 9, is that the 5th grade of synchronizer that speed change gear 14-1 establishes can be used in the reverse gear operation and play the effect of gear noiose when preventing reverse gear at Fig. 6.
In Fig. 6, when speed change lever when middle gear 94 shown in Figure 10 is transformed into the reverse gear gear, the shifting fork of being furnished with gear shift mechanism can make sleeve 28 deviate from the 5th grade of speed change gear 14-1 and move.The athletic meeting of sleeve 28 makes the scarf 36-12 of inner edge spline 30, and 36-22 oppresses lever 50-1 vertically, the second chamfered edge 54-12 of 50-2 (being positioned at the axle sleeve side), 54-22.Lever with one side of 50-1 among Fig. 9 is an example, that is to say, moves axial pressure F along with sleeve 28 deviates from the 5th grade of speed change gear 14-1
InOn the 2 second point of application of force P2 that can act on as the lever head 52-1 left side second chamfered edge 36-12, like this, lever 50-1 can be that axis clockwise rotates with the edge (as the second fulcrum O2) of axle sleeve 22 end face extension 64-1 just.Therefore, the trapezoidal extension 46-1 of synchronizing ring 40 can be at lever merogenesis end point of application of force Q2 pressure F
OutBe moved to the left under 2 the effect.Equally, downside lever 50-2 also oppresses synchronizing ring 40 to the left.Like this, synchronizing ring 40 just is pressed towards the 5th grade of speed change gear 14-1 one side, and its inner rim conical surface 42 is crushed on the outer rim conical surface 18 of gear, thereby forms rubbing contact shown in Figure 5.If still because of inertia and clutch disk together rotate, the rubbing contact between the synchronizing ring 40 and static the 5th grade of speed change gear 14-1 outer rim conical surface will make live axle 10 stalls to live axle 10 so when throw-out-of clutch.When sleeve 28 is continued to press to the 5th grade of speed change gear 14-1 one side, lever 50-1,50-2 will overcome the counter-force of spring 60 and be forced to press to its inboard axle direction, therefore, not add illustrated reverse idler gear and can imbed reposefully between reverse drive gear and the reverse gear driven gear.
Figure 11 is another embodiment who is used for the booster body of speed change gear shown in Figure 2 as described herein.Figure 11 has represented the booster body and the synchronizing ring 40 of synchronizer, and booster body has wherein partly replaced the lever 50-1 among Fig. 2,50-2.At first, be provided with the prominent shape fulcrum 48-1 of triangle along three circumferential positions at the face of synchronizing ring 40,48-2 and 48-3, the top of each prominent shape fulcrum is towards the outer rim direction.Along the lever 50-11 to 50-13 that circumferentially is divided into three sections corresponding respectively corresponding prominent shape fulcrum 48-1 to 48-3.Be equipped with tri-angle-holed 66-1 on each lever 50-11 to 50-13,66-2,66-3, these tri-angle-holed both sides corresponding respectively on the synchronizing ring 40 the prominent shape fulcrum 48-1 to 48-3 of corresponding triangle two drift angle limits and keep certain spacing with it.Corresponding prominent shape fulcrum 48-1 to 48-3 tabling on these holes 66-1 to 66-3 and the synchronizing ring 40.In addition, lever 50-11 to 50-13 be subjected to a local excision annular spring effect and at pressurized radially and expand, like this, under lever original state shown in Figure 11, just formed certain spacing between the two drift angle limits of prominent shape fulcrum 48-1 to 48-3 and hole 66-1 to 66-3.In addition, each lever 50-11 to 50-13 has the lever head 52-11 that stretches out from its outer rim center portion, 52-12,52-13.These lever heads 52-11 to 52-13 and lever 50-1 shown in Figure 1, the lever head 52-1 of 50-2,52-2 is identical, the chamfered edge 54-11 that they are contained, 54-12,54-13 can bear the pressure from inner edge spline 30 scarves 36.
If with synchronizing ring 40 and the lever 50-1 to 50-2 among synchronizing ring shown in Figure 11 40 and lever 50-11 to 50-13 replacement Fig. 2, gear shifting operation will be with embodiment illustrated in fig. 2 identical so, that is: along with sleeve 28 to the moving of second grade of speed change gear, the pressure that acts on the chamfered edge 52-11 to 52-13 will be increased and pass to synchronizing ring 40.In addition, with middle lever 50-1 embodiment illustrated in fig. 6, the lever head 52-1 of 50-2,52-2 is similar, the both sides of lever 50-11 to 50-13 upper lever head 52-11 to 52-13 shown in Figure 11 also all are provided with chamfered edge, therefore, pressurization when the 5th grade of speed change gear 14-1 makes gear shift and the reverse gear synchronous effect when reverse gear 70 is made gear shift all can realize equally.
Figure 12 is another embodiment of synchronizer of the present invention.In Figure 12, lever 50-11,50-21 are positioned at the left groove of spoke between axle sleeve 22 wheel hubs (axle sleeve is installed on the output shaft therefrom) and the outer rim spline 26, and lever 50-12,50-22 is positioned at right groove.Though lever 50-11,50-12 and lever 50-21, the lever 50-1 among 50-22 and Fig. 3,50-2 is the same as being horse shoe shaped in circumferential segmentation, the chamfered edge 54-1 among Fig. 3,54-2 is by the voussoir 80-1 among Figure 12, and 80-2 replaces.Be that example is introduced voussoir 80-1 and 80-2 with voussoir 80-1 below, voussoir 80-1 contains the chamfered edge 36-11 with sleeve 28 inner edge splines 36, the corresponding chamfered edge 82-11 of 36-12,82-12.Equally, with downside lever 50-21, the voussoir 80-2 that 50-22 matches also has and sleeve 28 inner edge splines 36 scarf 36-21, the corresponding chamfered edge 82-21 of 36-22,82-22.With embodiment illustrated in fig. 3 similar, lever 50-11,50-12; 50-21; the assembly relation of 50-22 and synchronizing ring 40 is as follows: lever is positioned at prominent shape fulcrum 44-1, the both sides of 44-2 and because of being subjected to due to the spring 60 effect of radial pressure to prop up point protection certain spacing 45-1,45-2 with prominent shape.In addition, similar with the convex point of application of force 58-1 among Fig. 5, lever 50-11,50-12,50-21,50-22 is provided with the bump body (not representing its position among the figure) as point of application of force Q near the end face of speed change gear one side (that is with corresponding speed change gear one side synchronizing ring opposing end faces).In above-mentioned synchronizer with the 6th kind of structure shown in Figure 12, no matter sleeve 28 is shifted to still right side speed change gear of left side, because of speed change lever motion increased pressure all can act on the synchronizing ring of synchronizer, has so just strengthened net synchronization capability.
Figure 13 is the synchronizer in another embodiment of the present invention, it is characterized in that having adopted the bicone structure.In bicone structure shown in Figure 13, a certain cone 84 is at the synchronizing ring place adjacent with second grade of speed change gear, 14 clutches 16 and between outer synchronizing ring 40-1 and inter-sync ring 40-2.Cone 84 left sides are provided with circumferentially overhanging claw bar 85 of a plurality of edges, the hole 88-1 of they and engagement sleeve 16 end faces, 88-2 tabling.Therefore, cone 84 can move axially, and its rotation motion is subjected to the restriction of speed change gear 14.
Figure 14 is the sectional view of being done along XIV-XIV line among Figure 13 that does not comprise sleeve 28.Position radially respect to one another is provided with prominent shape fulcrum 44-11 on inter-sync ring 40-2 end face, 44-12, and inter-sync ring 40-2 is positioned at cone 84 inboards as shown in phantom in FIG..Be provided with prominent shape fulcrum 44-21 on the outer synchronizing ring 40-1 too, 44-22.There is certain clearance in inboard spring action between lever end and the prominent shape fulcrum, semicircle lever 50-1 under the condition of radially pressurized and expansion because of it at lever, 50-2 just is assemblied in prominent shape fulcrum 44-11 by this gap, 44-12,44-21 is on the 44-22.Lever 50-1 and 50-2 have a lever head 52-1 as embodiment illustrated in fig. 3,52-2, and be provided with chamfered edge 54-1,54-2 with position that sleeve 28 inner edge splines lean on mutually at it.
Introduce operational circumstances embodiment illustrated in fig. 13 below, when gear-change operation makes sleeve 28 to second grade of speed change gear one side shifting, lever 50-1, the chamfered edge 54-1 of 50-2,54-2 can be subjected to the axial pressure of inner edge spline 30 scarves 36.This pressure increases because of the amplification of lever 50-1, and therefore outer synchronizing ring 40-1 is pressed towards the left side.Like this, the inner edge conical surface of outer synchronizing ring 40-1 just contacts with the outer rim conical surface of cone 84 because of pressurized, thereby produces frictional force, and the inner edge conical surface of cone 84 can be pressed on the outer rim conical surface of synchronizing ring 40-2 thereupon and produce moment because of rubbing contact.In these actions, second grade of speed change gear 14 can rotate around the rotation of output shaft 10 along with axle sleeve 22, and when their rotation was consistent each other, sleeve 28 can be with lever 50-1, and 50-2 is to lower compression and be meshed with engagement sleeve 16 reposefully.
It may be noted that the booster body as synchronizer, the scarf of sleeve 28 inner edge splines and the chamfered edge at lever top are set as flat scarf in the above-described embodiments temporarily, but they can also be the curved surfaces with certain curvature radius.Be two or three by tentative in the above-described embodiments though be used for the lever number of booster body and reverse gear synchronous mechanism, this number also can suitably be revised as required.In addition, also may under the prerequisite of not damaging its performance, make suitable improvement to booster body of the present invention and reverse gear synchronous mechanism.For example, for increasing the friction torque of synchronizer, can screw thread and oil groove be set on the relevant conical surface, in addition, spring 60 can adopt other shape except that annular, also desirable other form in its mounting point.
Claims (4)
1. be used for the synchronizer of speed change gear, it comprises:
The output shaft (10) that is used for outputting rotary power;
Be fixed tightly in the axle sleeve (22) on the above-mentioned output shaft (10), be provided with spline (26) at the outer edge surface of described axle sleeve (22);
Have the sleeve (28) of a spline (30), described spline (30) is formed on the inner edge surface of described axle sleeve, and described sleeve can slide in the outer edge surface spline (26) that described sleeve spline (30) is inserted described axle sleeve the time in the axial direction;
Be pivotally mounted on the speed change gear (14) on the described output shaft (10), it has the outer rim conical surface (18) and and all-in-one-piece engagement sleeve (16) adjacent with this outer rim conical surface on axle sleeve one side, this engagement sleeve forms from described outer rim conical surface extension, and it can be meshed with the inner edge spline (30) of this sleeve (28) by moving axially of described sleeve;
Synchronizing ring (40) between the outer rim conical surface (18) of described sleeve (28) and described speed change gear (14), described synchronizing ring (40) have the inner edge conical surface (42) relative with the outer rim conical surface (18) of described speed change gear (14);
Booster body between described axle sleeve (22) and described synchronizing ring (40), it is arranged to bear because of described sleeve (28) and moves the pressure that produces and with this pressure increase and pass to described synchronizing ring (40) to described speed change gear (14), described booster body comprises: a pair of at the lever (50-1 that upwards is divided at least two joints week, 50-2), from the overhanging lever head that forms of the core of described each lever outer rim, by described paired lever (50-1,50-2) and the point of contact between the described synchronizing ring (40) provide as the part (58-1 of point of application of force, 58-2), described part provides a point of application of force (Q), is exaggerated and acts on a precalculated position on described synchronizing ring (40) end face at this point of application of force axial thrust load;
It is characterized in that described booster body also comprises:
A pair of bump body as fulcrum (44-1,44-2), overhanging forming on its at least two symmetrical positions from described synchronizing ring (40) end face of described axle sleeve one side,
By form described lever as the balance pivot of point of application of force (50-1,50-2) and a plurality of fulcrum parts of providing of the point of contact between described axle sleeve (22) end face,
Described paired lever (50-1, two parts 50-2) are arranged on the described paired bump body (44-1 of described synchronizing ring (40), both sides 44-2) also upwards have certain clearance (45-1 in week, 45-2), described lever (50-1,50-2) utilize described synchronizing ring (40) relatively rotate with described bump body (44-1, side 44-2) contacts, motion at described sleeve (28) causes that speed change gear (14) makes described lever be pushed and be broadened diametrically when producing rubbing contact
Described a plurality of lever head (50-1,50-2) has a chamfered edge (36), form a force application location (P) and be used to bear axial pressure, axial pressure produces by receiving the direct friction that is associated with described sleeve (28) motion, and described pressure is resolved into the radial component and the axial thrust load at sensing center
Chamfered edge (36) on the inner edge spline (30) that is located at described sleeve (28) be pressed against described lever head (52-1, described chamfered edge 52-2) (54-1 produces described axial thrust load when 54-2) going up,
Wherein, the distance L from described fulcrum (O) to described point of application of force (Q)
2Set for less than distance L from described fulcrum (O) to described point of application of force (P) position
1,
Described chamfered edge (54-1, angular setting 54-2) becomes, when the inner edge conical surface (42) of described synchronizing ring (40) is realized rubbing contact with the described outer rim conical surface (18) of described speed change gear (14), affact described each lever head (52-1 by described bump body, 52-2) reaction force on the end face must overcome because of compressing and is provided with described lever (50-1, above-mentioned lever head (52-1 50-2), chamfered edge (54-1 52-2), radial component 54-2), after finishing synchronously, described each lever pressure diametrically descends and is suppressed, and the motion of described sleeve (28) gets clogged.
2. according to the synchronizer of claim 1, it is characterized in that,
Replace described paired bump body be provided with a plurality of the isolated triangle bump body of described synchronizing ring (40) end face equal intervals (48-1,48-2 ...), each described triangle bump body (48-1,48-2 ...) have a top shape bump body that periphery makes progress on described axle sleeve
Replace described a pair of lever be provided with a plurality of the lever that upwards is divided into a plurality of parts week (50-11,50-12 ...), each lever (50-11,50-12 ...) have tri-angle-holed (66-1, the 66-2 that are provided with by certain interval,), described tri-angle-holed (66-1,66-2 ...) with respect to described a plurality of triangle bump body (48-1,48-2 ...) and be provided with.
3. synchronizer according to claim 1 and 2 is characterized in that,
Described synchronizing ring (40) has the bicone structure, and one of them cone (84) is inserted between outer synchronizing ring (40-2) and the inter-sync ring (40-1),
A plurality of bump body (44-12,44-22) extend to the inter-sync ring (40-1) of the end face of each synchronizing ring (40-2) and described axle sleeve side and at least two symmetrical positions of point of application of force part (58), described bump body produces a point of application of force, and axial thrust load described herein is exaggerated and is sent to a precalculated position of described outer synchronizing ring (40-2) end face.
4. according to each described synchronizer in the claim 1 to 3, it is characterized in that,
Also comprise a reverse gear synchronous mechanism, the synchronous effect that utilizes following mode to realize stops described axle (10; 102) rotation is promptly worked as described booster body and is subjected to deviating from described speed change gear (14 by described sleeve (28); 14-1) the kinetic pressure of a side, described reverse gear synchronous mechanism is with described pressure reversal and be transported to described synchronizing ring (40),
Described reverse gear synchronous mechanism comprises:
Described lever head (52-1 in described speed change gear one side, second chamfered edge (the 54-11 that 52-2) forms on the edge, 54-22), and form second force application location that is used to bear pressure, described pressure be by bear with described sleeve (28) to described speed change gear (14; 14-1) the direct contact that a relative lateral movement is relevant causes,
Go up the fulcrum bump body (46-1,46-2, the 64-1 that are used to produce second fulcrum that forms at described axle sleeve (22) ...), described second axial pressure of naming a person for a particular job oppositely also will be applied to described second chamfered edge (54-12,54-22; 54-12,54-22 ...) second apply the axial pressure of position from described lever (50-1,50-2; 50-11,50-12 ...) second force application location of end affacts described synchronizing ring (40).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP07972396A JP3699775B2 (en) | 1995-07-20 | 1996-04-02 | Gearbox synchronizer |
| JP079723/96 | 1996-04-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1161419A CN1161419A (en) | 1997-10-08 |
| CN1089149C true CN1089149C (en) | 2002-08-14 |
Family
ID=13698128
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN96111837A Expired - Lifetime CN1089149C (en) | 1996-04-02 | 1996-08-15 | Synchronizing apparatus for transmission |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN1089149C (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8474345B2 (en) * | 2010-08-26 | 2013-07-02 | GM Global Technology Operations LLC | Transmission with reverse gear brake |
| CN103925357A (en) * | 2013-01-16 | 2014-07-16 | 上海索达传动机械有限公司 | Automobile, speed changer and gear reversing and shifting structure |
| WO2015188312A1 (en) * | 2014-06-10 | 2015-12-17 | 孙振台 | Traction drive isochronism speed governor and multi-drive shaft gearbox having speed governor |
| DE102015108991A1 (en) * | 2015-06-08 | 2016-12-08 | Hoerbiger Antriebstechnik Holding Gmbh | Hub, sliding sleeve and synchronization device and method for producing a hub and method for producing a sliding sleeve |
| CN109538736A (en) * | 2018-12-08 | 2019-03-29 | 哈尔滨东安汽车动力股份有限公司 | A kind of bearing arrangement for supporting that reverse gear is synchronous |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2085984A (en) * | 1980-10-17 | 1982-05-06 | Zahnradfabrik Friedrichshafen | Synchronizing gear systems |
| US4526052A (en) * | 1982-02-05 | 1985-07-02 | Nissan Motor Company, Ltd. | Synchromesh mechanism for transmission |
| US4823631A (en) * | 1986-05-26 | 1989-04-25 | Mazda Motor Corp. | Transmission synchronizer |
-
1996
- 1996-08-15 CN CN96111837A patent/CN1089149C/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB2085984A (en) * | 1980-10-17 | 1982-05-06 | Zahnradfabrik Friedrichshafen | Synchronizing gear systems |
| US4526052A (en) * | 1982-02-05 | 1985-07-02 | Nissan Motor Company, Ltd. | Synchromesh mechanism for transmission |
| US4823631A (en) * | 1986-05-26 | 1989-04-25 | Mazda Motor Corp. | Transmission synchronizer |
Also Published As
| Publication number | Publication date |
|---|---|
| CN1161419A (en) | 1997-10-08 |
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