DE102005056827A1 - Synchronizing ring for synchronous clutch, has annular base body and spring element is fixed to synchronizing ring whereby spring element is designed to transmit axial pre-synchronizing force - Google Patents

Abstract

Synchronizing ring (24A,24B) has an annular base body and spring element (26A,26B) is fixed to the synchronizing ring .The spring element is designed to transmit an axial pre-synchronizing force. The base body is provided means for mounting the synchronizing ring so as to be moveable to a limited extent in the peripheral direction relative to an associated guide sleeve (18). An independent claim is also included for the synchronous clutch.

Description

The The present invention relates to a synchronizer ring for a synchronizer clutch, with an annular Body, on the outer circumference of a Locking teeth formed and provided on which a friction lining is, being on the main body further means are provided to the synchronizer ring in the circumferential direction limited movable with respect to an associated guide sleeve to store.

Further the present invention relates to a synchronizer clutch for a spur gear, with a guide sleeve (Synchronous body), which is connectable to a shaft and has a guide sleeve toothing, with a sliding sleeve, which engages with the guide sleeve toothing standing sliding sleeve teeth and with respect to the guide sleeve axially displaceable, with a coupling body attached to a gear can be fixed and has a coupling body toothing, in the sliding sleeve teeth can be inserted to the guide sleeve and the coupling body rotatably connect to each other, and with a synchronizer ring of type described above.

Blocking synchronous couplings for helical gear, especially for Motor vehicle transmissions are generally known (cf., for example, Zooman, Gear transmission, 3rd edition, 1996).

to Initiation of a synchronization process is the sliding sleeve moved axially. It is about a spring / pressure piece system (ball stone spring or ring spring) a so-called. Vorsynchronkraft on the synchronizer ring exercised. This centered on the counter friction surface and is due to the differential speed twisted into a defined blocking position (relative to the sliding sleeve). The sliding sleeve teeth can not in this position the teeth of the synchronizer ring are pushed through. The on the sliding sleeve exerted Axial force is then transmitted directly to the synchronizer ring, its friction engagement on a counter friction surface of the coupling body for speed matching leads.

As soon as the synchronization has taken place, the synchronizing ring can be turned back be, the teeth of the sliding sleeve is characterized by the teeth of the Synchronring pushed through and inserted into the toothing of the coupling body to to make the non-rotatable connection between shaft and gear.

From the document EP 0 717 212 B1 is a synchronizer clutch with a synchronizer ring is known, which is formed as a deep-drawn sheet metal part. On the outer circumference locking teeth are formed and on the inner circumference driving cams that engage in recesses of the synchronizer body. To transmit the Vorsynchronkraft either a system of bolt, spring and sliding ring is provided, or an annular spring. The annular spring has an inwardly drawn edge which acts on the synchronizer ring.

Another synchronizer ring is from the DE 35 19 811 C2 known. The synchronizer ring is made of a carrier, are bent at the cold-forming tabs that serve as a stop cam.

The publication DE 202 16 782 U1 discloses different spring systems (plungers) for transmitting the Vorsynchronkraft. In one embodiment, the pressure piece is made of folded spring steel sheet.

The described spring systems (plungers) are in the art each integrated into a clutch pack having two synchronizer clutches. Depending on the direction of displacement of the sliding sleeve, the spring system transmits the presynchronizing force on the synchronizer ring of one or the other synchronizer clutch.

It The object of the present invention is an improved synchronizer ring and to provide an improved synchronizer clutch.

The above task is solved by a synchronizer ring, as mentioned at the beginning, wherein on the synchronizer ring at least one spring element is fixed, which is adapted is to transmit an axial Vorsynchronkraft.

The The above object is further by a synchronous coupling of the above mentioned type solved with such a synchronizer ring.

By the measure, to define a spring element on the synchronizer ring, which is designed to to transmit an axial Vorsynchronkraft can Synchronous couplings without a separate spring / pressure piece system getting produced.

It results in a lower number of parts and a lower installation costs. Furthermore, the risk of confusion during assembly is reduced since the separate spring elements of the prior art often with different types of springs are formed.

The Task is thus completely solved.

From It is particularly advantageous if the spring element extends from the outer circumference of the synchronizer ring approximately parallel or slightly oblique to an axis of the synchronizer ring extends.

A Such a configuration is structurally feasible low, further is due to the arrangement on the outer circumference an immediate assignment of the spring element to the sliding sleeve possible.

According to one another preferred embodiment is the spring element in the circumferential direction up to 10 mm wide.

With the embodiment the spring element is designed in the manner of a leaf spring, for example, along the manner of a cantilever about along the axis of the synchronizer ring extends.

According to one another preferred embodiment the spring element is radially elastic.

There Although the spring element designed to accommodate the Vorsynchronkraft is, but not usually for transmitting the synchronous force during the actual synchronization process, the spring element must dodge in the further synchronization process. This is true Generally also possible in the circumferential direction. However, it is preferred when the spring element evades in the radial direction. For some Applications (ASG) is also a transmission the synchronous force conceivable.

According to one preferred embodiment the spring element cohesively with the main body connected.

For example the spring element can be welded to the main body.

at an alternative preferred embodiment is the spring element one piece with the main body educated.

In In this case, the synchronizer ring, for example, from a forming steel be prepared.

at the synchronous coupling according to the invention It is particularly advantageous if the sliding sleeve has a circumferential groove section has, which cooperates with the spring element and against a axial center of the sliding sleeve is arranged offset.

By the staggered arrangement can the spring element of the synchronizer ring a separate Umfangsnutabschnitt be assigned to the sliding sleeve.

There the spring system for transmitting the Vorsynchronkraft is now assigned to a synchronizer ring, and not the shift sleeve or the associated synchronizer clutch package Overall, it is also appropriate to Spring element (or the spring elements) of the synchronizer ring a assign own circumferential groove section.

moreover it is in this embodiment of particular advantage that the Umfangsnutabschnitt also unbalanced may be formed so that opposing flank sections fulfill different functions can.

So It is particularly advantageous if a first contact section of the Spring element in a neutral position on a first edge portion of the Umfangsnutabschnittes rests, the Vorsynchronkraft of the first flank portion in the first contact portion of the spring element and thus can be introduced into the synchronizer ring.

Of the first contact section and the first flank section thus serve for transmission the Vorsynchronkraft from the sliding sleeve to the synchronizer ring.

According to one another preferred embodiment is a second contact portion of the spring element of a second Flank portion of the Umfangsnutabschnittes pressed into a neutral position to the friction lining of the synchronizer ring in the neutral position of a appropriate Gegenreibbelag withdraw.

hereby can be achieved that the friction lining of the synchronizer ring in the Neutral position of the associated Gegenreibbelag completely or but at least something is lifted. At least the frictional contact Relieved between these elements.

hereby can Drag torques are reduced, the efficiency is increased, the Reduced wear.

at this embodiment the circumferential groove section can accordingly have two flank sections, of which one flank section for the transmission of the Vorsynchronkraft is optimized, and of which the other flank section to the provision of the synchronizer ring is designed in a neutral position.

A such reset function becomes conventional Spring / pressure piece systems not realized in the prior art.

Furthermore, it is thereby possible to move the synchronizer ring with respect to the shift sleeve in a defined position. Therefore, it is also possible to realize the actual Vorsynchronvorgang with greater reliability; ideally the pre-synchronization is ensured with each switching operation.

It Consequently, there is also an improvement in shifting comfort.

at a further preferred embodiment serves an outside circumference Radial recess of the guide sleeve for receiving the spring element, wherein the bottom of the radial recess a larger diameter has as the inner diameter of the synchronizer ring.

There the spring element of the synchronizer ring in the radial direction very compact can be formed, for example according to the type of cantilever, it is also possible the component strength of the guide sleeve to enlarge. Because on the guide sleeve no need far radially inwardly reaching recesses for receiving a Spring / pressure piece system be provided.

There also the guide sleeve preferably no contribution in the transmission of Vorsynchronkraft makes, as in the prior art, the case by the spring / pressure piece systems on the guide sleeve support, can on the guide sleeve also a tolerance refinement done. In other words, can the guide sleeve with larger tolerances and thus cheaper getting produced.

Advantageous it is also when the sliding sleeve operates two synchronizer clutches and two circumferential grooves, each with a spring element interact and oppose the Sides of an axial center of the sliding sleeve are arranged.

at this embodiment the sliding sleeve is part of a synchronous package with two synchronizer clutches. The synchronizer rings of the two synchronizer clutches each have their own circumferential groove or their own Umfangsnutabschnitt on. These circumferential groove sections can each opposite Have flank sections that are asymmetrical with respect to a axial center of the respective circumferential groove are formed and consequently can perform different functions in both axial directions.

Although in the present context generally of a spring element respectively associated circumferential groove or Umfangsnutabschnitt spoken It goes without saying that, in any case, when a plurality of Springs distributed over the circumference is arranged, each spring element has its own Umfangsnutabschnitt assigned. These Umfangsnutabschnitte can exclusively in Be formed portion of their respective spring element. It could, however also be that the Umfangsnutabschnitte part of a circumferential Are circumferential groove.

at a further preferred embodiment the Umfangsnutabschnitte are arranged so that a spring element a switched synchronizer clutch in the other spring element associated Umfangsnutabschnitt engages, so that when inserted the sliding sleeve teeth in the coupling body toothing a drag torque is reduced.

With In other words, the fact that two in the axial direction staggered circumferential groove sections for the two synchronizer clutches are provided, exploited to that the spring element when switching its associated synchronizer clutch also uses the other Umfangsnutabschnitt functional.

For example the spring element can then, if the sliding sleeve teeth in the coupling body toothing is inserted, the spring element radially outward in the Dodge the circumferential groove of the other synchronizer clutch, so that the Contact pressure on the synchronizer ring is reduced. This will, however also the breakaway torque due to a frictional engagement between the friction lining of the synchronizer ring and the Gegenreibbelag reduced.

• – Reduktion der Bauteilanzahl durch Entfall eines separaten Federsystems;
• – Integration des Federelementes in den Synchronring;
• – Zentrierung des Synchronringes zur Schaltmuffe;
• – Abheben des Synchronrings in Neutralstellung, zur Reduzierung des Schleppmomentes;
• – Abheben des Synchronringes beim Einspuren in den Kupplungskörper, so dass das Losbrechmoment reduziert wird;
• – Abheben des Synchronringes führt jeweils auch zu einer Reduktion der Wärmeerzeugung und des Verschleißes;
• – der Schaltkomfort wird verbessert;
• – es ergibt sich eine Montageerleichterung durch Entfall des separaten Federsystems;
• – es ergibt sich eine Festigkeitserhöhung der Führungsmuffe durch eine breitere Stegbreite, durch eine geringere Aussparungstiefe im Bereich des Federelementes und/oder durch eine geringere Aussparungsbreite für die Umschlagwinkelbegrenzung;
• – es ergibt sich eine Toleranzentfeinerung an der Führungsmuffe durch Entfall des separaten Federelementes;
• – das Vorsynchronisieren ist vorzugsweise bei jedem Schaltvorgang gewährleistet;
• – es ergibt sich eine Reduzierung des Verwechslungsrisikos durch Entfall des separaten Federelementes mit unterschiedlichen Federarten.

Overall, at least one of the following advantages is realized with the synchronizer ring according to the invention or the synchronizer clutch according to the invention:

• - Reduction of the number of components by omission of a separate spring system;
• - Integration of the spring element in the synchronizer ring;
• - Centering of the synchronizer ring to the shift sleeve;
• - Lifting the synchronizer ring in neutral position, to reduce the drag torque;
• - Lifting the synchronizer ring when meshing in the coupling body, so that the breakaway torque is reduced;
• - Lifting the synchronizer ring also leads to a reduction of heat generation and wear;
• - the shifting comfort is improved;
• - It results in a simplification of assembly by omission of the separate spring system;
• - There is an increase in strength of the guide sleeve by a wider web width, by a smaller recess depth in the region of the spring element and / or by a smaller recess width for the Umschlagwinkelbegrenzung;
• - It results in a tolerance refinement of the Guide sleeve by omission of the separate spring element;
• - The Vorsynchronisieren is preferably guaranteed at each switching operation;
• - There is a reduction of the risk of confusion by omission of the separate spring element with different types of springs.

The Means for circumferentially movable storage can by the spring elements themselves be formed, which then also forces in the circumferential direction take up. It can but also separate means for the formation of stop cams or the like formed on the synchronizer ring and / or the associated components be.

Further The idea is that a spring system is provided, which is the synchronizer ring actively presses in the neutral position and thus lifts the synchronizer ring from the associated Gegenreibbelag, as considered independent invention, regardless of the training of a Spring element such that it is fixed to the synchronizer ring. In other words, could at conventional Synchronous couplings elastic return means also be formed by a separate spring system.

It it is understood that the above and the following yet to be explained features not only in the specified combination, but also in other combinations or alone, without to leave the scope of the present invention.

embodiments The invention are illustrated in the drawings and in the following description explained. Show it:

1 a schematic longitudinal sectional view through a clutch pack with two synchronizer clutches according to an embodiment of the present invention;

2 a view of a detail II of the 1 ;

3 a view of a detail III of the 1 ;

4 one of the 1 corresponding representation, in a position during a Vorsynchronisierung;

5 one of the 1 corresponding representation, in a position during a synchronization;

6 one of the 1 corresponding representation, in a position with back twisted synchronizer ring;

7 one of the 1 corresponding representation, in a position when meshing in the coupling body;

8th one of the 1 corresponding representation, in a position when switching through;

9 a side view of a synchronizer ring according to an embodiment of the present invention;

10 a partial perspective view of the synchronizer ring of 9 ;

11 a perspective view of a sliding sleeve of a synchronizer clutch according to the invention; and

12 a detail XII the 11 ,

In 1 is a clutch pack for a spur gear, in particular for a spur gear for motor vehicles, generally with 10 designated.

The clutch pack 10 is suitable for spur gear of any kind, especially for manual transmission, for automated manual transmission, for dual-clutch transmission, etc. Generally, the clutch pack 10 but also suitable for other types of spur gears.

The clutch pack 10 has in a conventional manner two adjacent synchronizer clutches 12A . 12B on, on a wave 14 are stored. The wave 14 is along an axis 15 aligned.

At the wave 14 are two gears (loose wheels) 16A . 16B rotatably mounted.

The synchronous couplings 12A . 12B serve either the gear 16A or the gear 16B rotatably with the shaft 14 connect to.

The clutch pack 10 has a guide sleeve (synchronizer body) 18 on, the rotation with the shaft 14 connected is. The guide sleeve 18 has an in 1 not shown outer teeth per se conventional design.

Furthermore, includes the clutch pack 10 a sliding sleeve 20 , which has an internal toothing (not shown in Figure), which is in engagement with the guide sleeve toothing. Accordingly, the sliding sleeve 20 in the axial direction parallel to the axis 15 movable back and forth. In 1 the sliding sleeve is shown in a neutral position.

The clutch pack 10 also has two coupling bodies 22A . 22B on, with the Zahnrä countries 16A respectively. 16B are rotatably connected. The coupling body 22A . 22B each have an outer toothing 23A respectively. 23B on.

The synchronous clutch 12A has a synchronizer ring 24A on. In a corresponding way, the synchronizer clutch 12B a synchronizer ring 24B on. The synchronizer rings 24A . 24B each have outer circumference a locking teeth 25A . 25B ,

The clutch pack 10 corresponds in its general construction, as described above, conventional clutch packs, as are known in the art. On a detailed description of the details and the exact operation is therefore omitted here.

The synchronizer rings 24A . 24B each have according to the invention spring elements 26A . 26B on.

In the illustrated embodiment, the spring elements 26 each as a kind of Kragarmes from the outer circumference of the synchronizer ring 24A . 24B formed in the axial direction protruding leaf springs.

An axial center of the sliding sleeve 20 is in 1 at 28 shown. The sliding sleeve 20 also has an outer circumferential circumferential groove 30 on, the manner known per se is designed to engage a shift fork or the like.

The guide sleeve 18 has a radially outwardly extending central web 32 on. In the area of its outer periphery, the guide sleeve 18 for the two spring elements shown 26A . 26B a radial recess 34 on. Their bottom has a larger diameter than the inner diameter of the synchronizer rings 24A . 24B ,

At the synchronizer rings 24A . 24B is, as will be explained below, a plurality of, for example, three spring elements 26 arranged distributed over the circumference.

It is understood that radial recesses 34 on the guide sleeve 18 are formed in a corresponding number.

Furthermore, on the inner circumference of the sliding sleeve 20 Umfangsnutabschnitte 36A . 36B formed in a corresponding number.

The circumferential groove sections 36A . 36B are opposite the axial center 28 staggered and lie on opposite sides of the axial center 28 , The spring elements 26A . 26B consequently, each have their own "own circumferential groove section 36A . 36B on.

The circumferential groove sections 36A . 36B can each be part of a circumferential circumferential groove. Preferably, the circumferential groove sections 36A . 36B each formed only on a relatively short peripheral portion, for example on a tooth of the internal toothing of the sliding sleeve 20 ,

The spring elements 26A . 26B are each integral with a main body of their synchronizer rings 24A . 24B connected. The main body may be made of formed steel, for example.

Alternatively, it is also possible to provide a spring element, which is manufactured separately from a base body and then connected to this, for example by means of a material connection, as shown in FIG 1 schematically at 38 is shown.

2 shows a detail II of 1 ,

In the following, the invention will continue essentially on the basis of the synchronizer clutch 12A explained. It is understood, however, that the description in a corresponding manner to the synchronizer clutch 12B is applicable.

The spring element 26A has a from the outer circumference of the synchronizer ring 24A slightly obliquely upwardly extending web section 40 and an end portion formed at the free end 42 on. The end section 42 is formed in the illustrated embodiment rolled up in the manner of a hook.

The bridge section 40 extends with respect to the axis 15 at an angle 44 in the range of 1 ° to 30 °, in particular from 2 ° to 20 °, and starting from the outer periphery of the synchronizer ring obliquely upward toward the axial center of the clutch pack 10 ,

The spring element 26A has a first contact section 46 in the area of the transition from the bridge section 40 to the end section 42 is trained. The first investment section 46 lies in the representation of 2 on a first flank section 48 the Umfangsnutabschnittes 36A at.

The top of the bridge section 40 forms a second contact section 50 that at a second flank section 52 the Umfangsnutabschnittes 36A in the neutral position.

The flank sections 48 . 52 are both inclined to the axis 15 aligned, in opposite directions. Here is the first flank section 48 steeper, so that between the axis and the first edge portion 48 an angle is set which is greater than that angle 44 , The size of this angle (in 2 unspecified) may for example be in the range of 30 ° to 80 °, preferably in the range of 40 ° to 70 °.

The length of the spring elements 26A . 26B is chosen so that these are in the range of their end sections 42 opposite but preferably not touching.

In the in 1 shown neutral position of the shift sleeve 20 are the two spring elements 26A . 26B each in their Umfangsnutabschnitten 36A . 36B , The spring elements are each preferably slightly deflected radially inwardly, so that they under a certain bias in the Umfangsnutabschnitten 36A . 36B issue.

If now the shift sleeve 20 for initiating a switching operation ie for connecting, for example, the gear 16A with the guide sleeve 18 , is moved to the right, practices the shift sleeve 20 over her first flank section 48 an axial force on the spring element 26A out. This axial force causes the spring element 26A is moved to the right and in this case transmits a so-called Vorsynchronkraft, as in 2 at 54 is shown.

The Vorsynchronkraft serves to synchronizer ring 24A with respect to the coupling body 22A to center and bring in a defini te blocking position. This will be explained in detail below.

If the shift sleeve 20 is in its neutral position, exerts the bias of the spring element 26A radially outward a small restoring force 56 towards the axial center 28 on the spring element 26A from how it is in 2 and 3 at 56 is shown.

By this restoring force (centering force) is the spring element 26A and hence the synchronizer ring 24A from the coupling body 22A lifted. In other words, between a friction lining 60 of the synchronizer ring 24A and a friction lining 62 of the coupling body 22A a small distance s set up as it is in 3 is shown.

at However, multiple cone syncing raises this distance between the coupling body and the intermediate ring or the intermediate ring package.

Although preferably a certain distance is set up, it is also possible according to the invention to make the restoring force so small that the over the friction surfaces 60 . 62 transmitted friction force is very low, in any case, significantly lower than in cases where the synchronizer ring is loosely centered on the coupling body, as is generally the case with synchronizer clutches of the prior art.

Due to the fact that the synchronizer ring 24A preferably from the coupling body 22A is lifted, drag torques are reduced or even completely avoided.

In the 4 to 8th a switching operation is shown in which the shift sleeve 20 from the in 1 shown neutral position is shifted to a position in which the synchronizer clutch 12A is closed, ie the teeth of the sliding sleeve 20 in the coupling body toothing 23A is inserted.

In 4 a state is shown in which a Vorsynchronisierung is done. The sliding sleeve has 20 a very small first way 66 put back, and this was on the shift sleeve 20 a force 68 transfer.

It is due to the interaction of the first investment section 46 and first flank section 48 an axial force, the so-called presynchronizing force, 54 on the synchronizer ring 24A Have been transferred. This is the friction lining 60 with a force 70 to the Gegenreibbelag 62 created. Due to the differential speed is the shift sleeve 24A turned into a locked position, as in 69 shown.

As a means for limiting the turning over or for defining a blocking position and a release position of the synchronizer ring 24A can the spring elements 26 be used. Alternatively, separate means, such as separate stop cams or the like may be provided.

Upon further exercise of a force 68 on the shift sleeve 20 the actual synchronization ( 5 ). Here is the shift sleeve 20 for a distance 72 moved towards the neutral position. The sharpening of the toothing of the sliding sleeve is due to the sharpening of the toothing of the synchronizer ring 24A at. Therefore, a force is transmitted through these gears, namely the actual synchronization force 74 so that the friction linings engage so as to realize the synchronization, ie the speed adjustment.

Here is the spring element 26A deflected by the first abutment section 46 in the manner of a ramp to the first flank section 48 has been guided along. In the actual synchronization process, little or no force in the axial direction of the Umfangsnutabschnitt 30A on the spring element 26A transfer.

In 6 a state is shown in which the speed has been adjusted. Consequently, over the contact of the friction surfaces 60 . 62 essentially no more frictional torque generated. The on the sliding sleeve 20 applied axial force 68 causes the synchronizer ring 24A is turned back, as shown schematically in 6 at 76 is shown.

In 7 is shown as the sliding sleeve by means of force 68 is moved axially further. In this case, the toothing of the sliding sleeve reaches the region of the coupling body toothing 23A and twist them (as with 78 is shown), so that the teeth can be moved into each other.

Here comes the transition region between web and end section 40 . 42 of the spring element 26A in the region of the Umfangsnutabschnittes 36B , which is actually the other synchronous clutch 12B assigned. Here, the spring element 26A thus relieved in the radial direction to the outside, so that the synchronizer ring 24A from the coupling body 22A can take off. This in turn reduces the drag torque.

8th finally shows the state in which the teeth of the sliding sleeve 20 in the coupling body toothing 23A is inserted. This engaged state is in 8th at 80 shown. Again, this is the spring element 26A due to entering the circumferential groove portion 36B relieved. Drag torques can consequently also be in the switched state of the synchronizer clutch 12A be reduced.

The 9 and 10 show an embodiment of a synchronizer ring according to the invention 24 ,

The synchronizer ring 24 has an annular body 90 on, on the outer circumference of the locking teeth 25 is trained. A single tooth is in 9 at 92 shown.

Further, on the body 90 three spring elements 26 fixed, in the present case in one piece with the main body 90 connected.

The spring elements 26 each extending from the region of the locking teeth 25 approximately in the axial direction, over the portion of the body 90 away, the friction lining on its inner circumference 60 forms.

at 9 are also stop recesses 94 shown, for example, the establishment of a limited circumferentially movable mounting of the synchronizer ring 24 can be used.

In the 11 and 12 is a sliding sleeve 20 a synchronizer clutch according to the invention shown.

It can be seen that the shift sleeve 20 on the inner circumference a sliding sleeve toothing 100 having. Their teeth are distributed over the circumference differently formed and have different functions. Some teeth are straight and serve mainly for axial guidance of a corresponding toothing of the guide sleeve 18 ,

Other Teeth are formed with deposits and serve, in appropriate Deposits of the coupling body toothing to grab when the switched state is established. hereby can be prevented that the switched state at low Moments or load changes are accidentally released.

Furthermore, in the 11 and 12 shown that three teeth 102 each of the three spring elements 26 the assigned synchronizer ring 24 are assigned.

On the teeth 102 is respectively on the surface facing radially inward, the Umfangsnutabschnitt 36A and the circumferential groove portion 36B educated. The corresponding flank sections 48A . 48B and 52A . 52B are in 12 also shown.

Although the invention with reference to an embodiment have been described, modifications thereof are conceivable. So can the Synchronous clutches, for example, constructed as multiple cone clutches be.

Claims (14)

Synchronizer ring ( 24 ) for a synchronous coupling ( 12 ), with an annular base body ( 90 ), on whose outer circumference a locking toothing ( 25 ) and on which a friction lining ( 60 ) is provided, wherein on the base body ( 90 ) further means ( 94 ) are provided to the synchronizer ring ( 24 ) limited in the circumferential direction movable with respect to an associated guide sleeve ( 18 ), characterized in that on the synchronizer ring ( 24 ) at least one spring element ( 26 ) is arranged, which is adapted to an axial Vorsynchronkraft ( 54 ) transferred to. Synchronizer ring according to claim 1, characterized in that the spring element ( 26 ) from the outer periphery of the synchronizer ring ( 24 ) approximately parallel or slightly oblique to an axis ( 15 ) of the synchronizer ring ( 24 ). Synchronizer ring according to claim 1 or 2, as characterized in that the spring element ( 26 ) is circumferentially up to 10 mm wide. Synchronizer ring according to one of claims 1 to 3, characterized in that the spring element ( 26 ) is formed radially elastic. Synchronizer ring according to one of claims 1 to 4, characterized in that the spring element ( 26 ) cohesively ( 38 ) with the basic body ( 90 ) connected is. Synchronizer ring according to one of claims 1 to 4, characterized in that the spring element ( 26 ) in one piece with the main body ( 90 ) is trained. Synchronizer ring according to one of claims 1 to 6, characterized in that on the synchronizer ring ( 24 ) at least two circumferentially distributed spring elements ( 26 ). Synchronous coupling ( 12 ) for a spur gear, with a guide sleeve (synchronous body) ( 18 ) with a wave ( 14 ) is connectable and has a Führungsmuffenverzahnunq, with a sliding sleeve ( 20 ), which has a sliding sleeve toothing (FIG. 100 ) and with respect to the guide sleeve ( 18 ) is axially displaceable, with a coupling body ( 22 ) attached to a gear ( 16 ) and a coupling body toothing ( 23 ), in which the sliding sleeve toothing ( 100 ) is insertable to the guide sleeve ( 18 ) and the coupling body ( 22 ) rotatably connected to each other, and with a synchronizer ring ( 24 ) according to one of claims 1 to 7. Synchronous coupling according to claim 8, characterized in that the sliding sleeve ( 20 ) a circumferential groove portion ( 30 ), which with the spring element ( 26 ) and against an axial center ( 28 ) of the sliding sleeve ( 20 ) is arranged offset. Synchronous coupling according to claim 9, characterized in that a first contact section ( 46 ) of the spring element ( 26 ) in a neutral position on a first flank section ( 48 ) of the circumferential groove portion ( 30 ) is applied, wherein the Vorsynchronkraft ( 54 ) from the first flank section ( 48 ) in the first section of the Annex ( 46 ) of the spring element ( 26 ) and thus into the synchronizer ring ( 24 ) can be initiated. Synchronous coupling according to claim 9 or 10, characterized in that a second contact section ( 50 ) of the spring element ( 26 ) from a second flank section ( 52 ) of the circumferential groove portion ( 30 ) is pressed in a neutral position to the friction lining ( 60 ) of the synchronizer ring ( 24 ) in the neutral position of a corresponding Gegenreibbelag ( 62 ). Synchronous coupling according to one of claims 8 to 11, characterized in that an outer circumferential radial recess ( 34 ) of the guide sleeve ( 18 ) for receiving the spring element ( 26 ), wherein the bottom of the radial recess ( 34 ) has a larger diameter than the inner diameter of the synchronizer ring ( 24 ). Synchronous coupling according to one of claims 8 to 12, characterized in that the sliding sleeve ( 20 ) two synchronous couplings ( 12 ) and two circumferential groove sections ( 36A . 36B ), each with a spring element ( 26 ) and on opposite sides of an axial center ( 28 ) of the sliding sleeve ( 20 ) are arranged. Synchronous coupling according to claim 13, characterized in that the circumferential groove sections ( 36A . 36B ) are arranged so that a spring element ( 26 ) a switched synchronizer clutch ( 12 ) in the other spring element ( 26 ) associated circumferential groove portion engages, so that when inserting the sliding sleeve toothing ( 100 ) in the coupling body toothing ( 23 ) a drag torque is reduced.