WO2008138422A1 - Système d'embrayage - Google Patents

Système d'embrayage Download PDF

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Publication number
WO2008138422A1
WO2008138422A1 PCT/EP2008/002243 EP2008002243W WO2008138422A1 WO 2008138422 A1 WO2008138422 A1 WO 2008138422A1 EP 2008002243 W EP2008002243 W EP 2008002243W WO 2008138422 A1 WO2008138422 A1 WO 2008138422A1
Authority
WO
WIPO (PCT)
Prior art keywords
locking member
clutch assembly
synchronizer ring
locking
assembly according
Prior art date
Application number
PCT/EP2008/002243
Other languages
German (de)
English (en)
Inventor
Jochen Krenkler
Erol Ledetzky
Original Assignee
Hoerbiger Synchron Technik Gmbh & Co. Kg
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Hoerbiger Synchron Technik Gmbh & Co. Kg filed Critical Hoerbiger Synchron Technik Gmbh & Co. Kg
Publication of WO2008138422A1 publication Critical patent/WO2008138422A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D23/00—Details of mechanically-actuated clutches not specific for one distinct type
    • F16D23/02—Arrangements for synchronisation, also for power-operated clutches
    • F16D23/04—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch
    • F16D23/06—Arrangements for synchronisation, also for power-operated clutches with an additional friction clutch and a blocking mechanism preventing the engagement of the main clutch prior to synchronisation
    • F16D2023/0618—Details of blocking mechanism comprising a helical spring loaded element, e.g. ball

Definitions

  • the present invention relates to a clutch assembly for the rotationally fixed connection of a shaft with a rotary member mounted thereon, with a sliding sleeve which is rotatably connected to the shaft, axially displaceably mounted with respect to the shaft and provided with a first toothing, with a coupling body with the rotary member is rotatably connected and provided with a second toothing, which is brought to the rotationally fixed connection of the shaft and rotary member with the first toothing in engagement, and with a Sperr-Synchronmaschinesein- direction, which has a synchronizer ring with a friction surface, by means of the rotational speeds the shaft and the rotary member are synchronized before the first and the second teeth are brought into engagement, wherein the locking synchronizing comprises a locking member which is movably mounted relative to the shift sleeve between a neutral position and a locking position, which is coupled to the synchronizer ring in the circumferential direction and which has a wedge surface which forms a wedge surface pairing in the locked
  • Such a clutch assembly is, for example, from the document DE 10 2005025569 Al known.
  • Clutch assemblies of the generic type are used in countershaft transmissions for motor vehicles.
  • the countershaft transmissions are designed as a stepped transmission with a plurality of gear ratios.
  • Each gear is assigned to a wheelset having a fixed gear and a loose wheel.
  • the loose wheels are each rotatably mounted on one of the shafts of the transmission and connectable by means of a clutch to the shaft (to shift the gear ratio), and detachable from this (to interpret the gear ratio).
  • the clutches are nowadays usually designed as synchronous clutches in which the rotational speeds of shaft and rotary member are synchronized with each other before a positive engagement is established therebetween.
  • the synchronous couplings are nowadays usually designed as locking synchronizer clutches, in which a locking mechanism ensures that the engagement of the teeth of the sliding sleeve and coupling body is only possible when the rotational speeds of shaft and rotary member are synchronized with each other.
  • the most common locking mechanism today has a locking toothing on the outer circumference of the synchronizer ring.
  • the synchronizer ring is mounted on the shaft (or a guide sleeve fixed thereto, which is also referred to as a synchronizer body) movable limited.
  • the sliding sleeve teeth can be passed through the locking teeth of the synchronizer ring to make the positive connection with the coupling body.
  • the lock Position the synchronizer ring is rotated, in such a way that the shift sleeve is prevented from being moved in the axial direction on the coupling body.
  • the locking position of the synchronizer ring is achieved in that the synchronizer ring due to the applied axial switching force frictionally engages with the associated coupling body (or other associated friction surface), whereby the synchronizer ring is taken in the direction of rotation and thereby taken in the locked position (flips). Only when the speeds are synchronized, the frictional force is reduced so much that a turning back of the synchronizer ring due to the shift force is possible, so that the shift sleeve can then be pushed through the back in the release position toothing of the synchronizer ring.
  • Such a pressure piece or such a stone is frequently present in synchronous clutch arrangements in order to lock the sliding sleeve into a neutral position. Furthermore, a Vorsynchronkraft can be exercised on the synchronizer ring on such a pressure piece.
  • a plurality of wedge surfaces is provided on the inner circumference of the synchronizer ring, which are associated with corresponding wedge surfaces of the plungers.
  • the shift sleeve of the known locking mechanism When applying a switching force, the shift sleeve of the known locking mechanism tries to move away the thrust piece in the radial direction of the Rastiernut and simultaneously presses the synchronizer ring in the axial direction of a friction surface on (arrival or Vorsynchron approximate). In this case, the synchronizer ring rotates until the wedge surface pairings engage, such that the wedge surfaces a radial Push away pushing away the pressure piece. As a result, the shift sleeve can not be further axially displaced and locked in this manner.
  • the synchronizer ring can be rotated back by means of the axially expended on the shift sleeve switching force due to the then reduced frictional force, so that the pressure piece can be pushed away in the radial direction inwards.
  • the shift sleeve can therefore be further displaced in the axial direction to engage with the coupling body.
  • the above object is achieved in the aforementioned clutch assembly characterized in that the locking member is pivotally mounted about a radially extending pivot axis between the neutral position and the locking position.
  • the locking member may be arranged, for example, instead of a conventional pressure piece (stone) between the shaft (or the guide sleeve) and the shift sleeve.
  • the locking member preferably has a centrally arranged in the axial direction of the hub portion which establishes the pivot axis, around which the locking member is thus pivotable.
  • the hub portion is supported in the circumferential direction preferably on a guide portion. This can be formed on the sliding sleeve or on the shaft (or on an associated guide sleeve).
  • the wedge surfaces of the wedge surface pairing are radially aligned.
  • the locking member is mounted in the axial direction limited movable.
  • the locking member is preferably mounted so as to be limitedly movable in the axial direction between opposing synchronizer rings of a clutch pack.
  • the pivot axis is "moved" in axial movements of the locking member.
  • This preferred embodiment also makes it possible that the locking member also works as a pressure piece, thus exerting a pressing force on the synchronizer ring via the locking member.
  • Vorsynchronstoff are formed, by means of which the locking member in the axial direction of the shift sleeve is entrained.
  • the Vorsynchronstoff couple the locking member with the shift sleeve in the axial direction, so that the locking member is entrained for the purpose of pressing the synchronizer ring in the axial direction.
  • the Vorsynchronstoff are also designed to release the coupling between the locking member and the shift sleeve as soon as the synchronization is achieved and the shift sleeve is to be brought into positive engagement with the coupling body.
  • the Vorsynchronstoff preferably have a Vorsynchronglied which is mounted radially movable in a recess of the locking member.
  • the Vorsynchronglied may be or a ball, but it may also be a wedge element or the like.
  • the Vorsynchronglied attacks usually on a driving wedge surface of the shift sleeve. It is understood that the Vorsynchronstoff can also be used to lock the shift sleeve in the axial direction in a neutral position.
  • the Vorsynchronstoff a spring for biasing the Vorsynchrongliedes in the radial direction towards the shift sleeve.
  • the recess of the locking member is formed continuously in the radial direction and when the spring extends into the recess in order to bias the Vorsynchronglied through the recess therethrough.
  • the spring can be supported on the shaft or the associated guide sleeve.
  • the bias of the Vorsynchrongliedes thus does not influence the pivotability of the locking member.
  • the locking member has a nose extending in the axial direction, which engages in an axial recess of the synchronizer ring for coupling with the synchronizer ring.
  • the locking member (50 ') has an axially extending fork portion (66'") into which for coupling with the synchronizer ring (44 '") an axial projection (64'") of the synchronizer ring (44 '. ") attacks.
  • Such a locking member is inexpensive to manufacture.
  • the locking member has a pressure surface, via which an axial force can be transmitted to the synchronizer ring.
  • the locking member serves as a pressure body or pressure piece at the same time.
  • the pressure surface is formed independently of a circumferential direction coupling between synchronizer ring and locking member.
  • the pressure surface is an axial end surface of the nose or an axial bottom of the fork portion.
  • the pressure surface is arranged in the axial direction in a region between the pivot axis and the circumferential direction coupling of the locking member with the synchronizer ring.
  • the distance between the pressure surface and the pivot axis can be reduced.
  • the loads of the locking member can be reduced.
  • the locking member can be made smaller overall.
  • the pressure surface is crowned.
  • the wedge surface of the locking member is arranged in the axial direction in the region between the pivot axis and the circumferential direction coupling with the synchronizer ring.
  • the wedge surface is arranged on the same side of the pivot axis, seen in the axial direction.
  • This embodiment makes it possible to configure the engagement of the wedge surface pairing in such a way that substantially no self-locking can occur.
  • the wedge surface of the locking member in the axial direction on the other side of the pivot axis as the circumferential direction coupling with the synchronizer ring.
  • the wedge surface of the locking member is offset in the Urnfangscardi arranged opposite to a line which intersects the pivot axis in the axial direction.
  • these embodiments are also particularly suitable for switching packages in which clutch assemblies are integrated into a package, with a single shift sleeve, a single guide sleeve and a single locking member. Furthermore, it is generally advantageous if the synchronizer ring has no locking teeth.
  • the synchronizer ring can be produced in a simple manner.
  • the locking teeth on the synchronizer ring can be omitted
  • the costs of the synchronizer ring can be reduced, the same applies to the manufacturability of the synchronizer ring,
  • the pre-synchronizing means are coupled to the blocking mechanism or the blocking-synchronizing device, there is an improvement in the guide sleeve strength, since no Arretiernutkontur is necessary, as before,
  • the wear reserve can be increased, alternatively, a space reduction can be achieved
  • FIG. 1 is a schematic longitudinal sectional view through a clutch assembly according to the invention
  • FIG. 2 is a cross-sectional view of the clutch assembly of FIG. 1;
  • Fig. 3 is a view similar to Figure 2 of the clutch assembly in a phase of Vorsynchron matterss.
  • Figure 4 is a view similar to Figure 2 of the clutch assembly in a phase between Vorsynchron include and locks.
  • Fig. 5 is a view similar to Figure 2 of the clutch assembly in a phase of main synchronization.
  • FIG. 6 shows a view similar to FIG. 2 of the clutch assembly in a phase of unlocking or a free-flying phase
  • FIG. 7 shows a view comparable to FIG. 2 in a phase of the meshing or the positive connection
  • FIG. 8 shows a view similar to FIG. 2 of an alternative embodiment of a clutch assembly according to the invention of a neutral position
  • FIG. 9 is a view similar to FIG. 8 of the clutch assembly in a phase of presynchronization
  • FIG. 10 is a view similar to FIG. 8 of the clutch assembly in a phase shortly before a blocking position
  • FIG. 11 is a view similar to FIG. 8 of the clutch assembly in a phase of main synchronization (when locked);
  • FIG. Fig. 12 is a view similar to Figure 8 of the clutch assembly in a phase of unlocking and the beginning of a free-flying phase.
  • FIG. 13 shows a schematic illustration of a further embodiment of a clutch assembly according to the invention in a form comparable to that of FIG. 2;
  • Fig. 14 is a schematic longitudinal sectional view through the clutch assembly of Fig. 13;
  • FIG. 15 is a view similar to FIG. 8 of a further embodiment of a clutch assembly according to the invention.
  • FIG. 16 is a cross-sectional view of the clutch assembly of FIG. 15.
  • FIG. 16 is a cross-sectional view of the clutch assembly of FIG. 15.
  • Fig. 1 is a transmission for a motor vehicle generally designated 10.
  • the transmission 10 has an input shaft 12, which is connected via a constant gear set 14 with a countershaft 16 parallel thereto.
  • An output shaft 24 is disposed coaxially with the input shaft 12.
  • a plurality of gear sets 18 is disposed on the countershaft and the output shaft 24, respectively. In Fig. 1, for reasons of clarity, only one set of gears 18 is shown having a fixed wheel 20 which is rotatably connected to the output shaft 24.
  • the gear set 18 further includes a loose wheel 22 which is rotatably mounted on the countershaft 16.
  • a first amongst a clutch assembly according to the invention is generally designated 30 in Figures 1 and 2
  • the clutch assembly 30 serves to connect the idler gear 22 (or a loose wheel, not shown in the axial direction on the other side) to the countershaft 16.
  • the clutch assembly 30 is thus formed as a clutch pack with two individual clutches.
  • the clutch assembly 30 includes a guide sleeve (also called synchronous body) 32, which is fixed to the countershaft 16 (eg. By means of a suitable toothing).
  • the guide sleeve 32 also has an external toothing 33 shown in FIG. 2.
  • a shift sleeve 34 is slidably mounted in the axial direction A.
  • the shift sleeve 34 has, in a conventional manner, an outer radial groove 36 for engaging a shift fork or the like. Furthermore, the shift sleeve 34 has on its inner circumference an internal toothing 38, which is in engagement with the external toothing of the guide sleeve 32.
  • the clutch assembly 30 further includes a coupling body 40 which is fixedly connected to the associated idler gear 22, the coupling body 40 has external teeth 42 on which the internal teeth 38 of the shift sleeve 34 can be pushed to D in the rotational direction of a positive connection between the countershaft 16 and the idler gear 22 set up.
  • the clutch assembly 30 further includes a synchronizer ring 44.
  • the synchronizer ring 44 has in known manner a friction surface 46, which cooperates with a Jacobreib configuration 48 of the idler gear 22 (or the coupling body 40 or an intermediate cone ring).
  • the locking synchronization device has a locking member 50 in the form of a pivotable about a radially extending pivot axis 52 around blocking block.
  • the locking member 50 is also part of Vorsynchronstoffn 54 for applying a Vorsynchronkraft on the synchronizer ring 44.
  • the Vorsynchronstoff 54 have a ball 56 and a spring 58 on.
  • the spring 58 is mounted in a spring seat 59 of the guide sleeve 32 and is designed as a compression spring which presses the ball 56 radially outward.
  • the ball 56 is received in a recess 60 of the locking member 50, which is formed continuously in the radial direction.
  • the recess is generally circular, concentric with the pivot axis 52.
  • the locking member 50 is disposed in the radial direction between the guide sleeve 32 and the shift sleeve 34.
  • the shift sleeve 34 On the radial inner side, the shift sleeve 34 has a groove 61.
  • the spring 58 urges the ball 56 (or other shaped asynchronous member such as a wedge-shaped stone) into the groove 61.
  • the locking member 50 is rotatably supported about the pivot axis 52 between the guide sleeve 32 and the shift sleeve 34 to one. Further, the locking member 50 is mounted in the axial direction limited movable, limited by the axially opposite each other synchronizer rings 44 (only one of which is shown in Fig. 1). The locking member 50 also has around the recess 60th around ring sleeves 53 a, which extend in the radial direction R. The locking member 50 is supported in Urnfangscardi D with these ring sleeves 53a on axially extending guide surfaces 53b of the guide sleeve 32 from, as is indicated schematically in Fig. 2. The ring sleeves 53 a form a hub section for the pivot axis 52
  • the locking member 50 is coupled in the circumferential direction D with the synchronizer ring 44, which is indicated by a driving coupling 62.
  • the entrainment coupling 62 includes a fork-shaped projection 65 which is formed on the synchronizer ring 44 and defines an axial recess 64 which faces the locking member 50.
  • the driving coupling 62 includes a nose 66 which is fixedly connected to the locking member 50 The nose 66 extends from a main body of the locking member 50 in the axial direction to the synchronizer ring 44 and is generally in the axial recess 64.
  • the nose is approximately hemispherical in tangential section to achieve a low-friction driving coupling 62 as possible.
  • An axial front surface of the nose 66 is formed as a pressure surface 68, which is adapted to transmit an axial force on the synchronizer ring 44.
  • the clutch assembly 30 distributed in the circumferential direction D has a plurality of locking synchronization means 49, for example.
  • the locking member 50 has a tangential section approximately rectangular base body from which extend in the axial direction of the lugs 66a, 66b.
  • the Suffixes a, b are used in this case to distinguish the two individual clutches of the clutch assembly 30, the suffix a is associated with the clutch, which is assigned to the idler gear 22 shown in FIG.
  • Wedge surfaces 70 are respectively formed at the four corners of the rectangular base body.
  • the wedge surfaces 70a assigned to a shifting clutch a are arranged on a side of the pivoting axle 52 lying opposite the nose 66a (seen in the axial direction).
  • the wedge surfaces 70 are each offset in the circumferential direction D with respect to a line which extends in the axial direction through the pivot axis 52.
  • the locking member 50 is disposed in a region radially within the shift sleeve 34, in which the toothing is interrupted.
  • the circumferentially adjacent teeth of the spur toothing 38 of the sliding sleeve 34 are each formed with peripheral recesses 74, whose axial end surfaces are formed as the wedge surfaces 72.
  • the locking synchronizer 49 has four wedge surfaces 70 and four correspondingly arranged wedge surfaces 72.
  • the teeth of the spur toothing 38 of the sliding sleeve 34 further each have deposits 76 (in a conventional manner) and are formed to the teeth of the coupling body 40 out with a gating 78.
  • the gating 78 can be formed at an acute angle in the present case, so that a slight meshing in the external teeth 42 of the coupling body 40 is possible.
  • Fig. 1 and 2 the lock-Svnchronmaschines Republic 49 is shown in the neutral position N In this neutral position, the locking member 50 is aligned in the axial direction. In this case, the locking member 50 does not engage in the circumferential recesses 74 and thus can be offset in the axial direction A with respect to the shift sleeve 34 become.
  • Fig. 2 is a so-called.
  • Vorsynchronweg 80 is shown, which corresponds to the distance between the pressure surface 68 and a bottom of the axial recess 64.
  • a gap 82 is shown in Fig. 2, which indicates the distance between the synchronizer ring 44 and the coupling body 40.
  • a wedge surface 70 and a wedge surface 72 engage at one of the nose 66 a approximately diagonally opposite corner into engagement and form a wedge surface pairing 96 a.
  • the wedge surface pairing 96 is formed so that an angle ⁇ is established with respect to the axial direction.
  • a restoring force 98 is exerted on the locking member 50, which counteracts the force F b and tries to push the locking member 50 back into the axially aligned position.
  • the equilibrium of forces is also influenced by how great the distance xa between the pivot axis 52 and the location of the driving coupling 62 and how large the distance between the pivot axis 52 and the wedge surface pairing 96, which is designated in Fig. 5 with xb.
  • the dimensions xa, xb correspond to different lever lengths, which are to be considered in the dimensioning of the clutch assembly 30 (in addition to tribological boundary conditions and the selected angles 94 and ⁇ ).
  • the friction torque 92 collapses, so that the force F 3 is smaller.
  • the force Fb also becomes smaller and, as soon as it becomes smaller than the restoring force 98, the locking member 50 is restored. rotates, as shown in Fig. 6.
  • the locking member 50 thereby takes the synchronizer ring 44 in the circumferential direction D, as shown in FIG. 6 at 99. Since the locking member 50 has now emerged from the circumferential recesses 74 and is oriented at least approximately axially, the shift sleeve 34 can be moved in the axial direction on.
  • Fig. 7 the state is shown, in which the toothing 38 of the shift sleeve 34 is meshed with the toothing 42 of the coupling body 40 and consequently the positive connection has been established.
  • the cone angle of the friction surfaces 46, 48 may be in the range between 5 ° and 10 °, preferably in the range between 6.5 ° and 8.5 °.
  • the blocking angle ⁇ can be in the range between 20 ° and 70 °, preferably in the range between 30 ° and 50 °.
  • FIGS. 8 to 12 an alternative embodiment of a clutch assembly according to the invention is designated generally by 30 '.
  • the clutch assembly 30 'corresponds in structure and operation generally the clutch assembly 30 of Figures 1 to 7. The same elements are therefore provided with the same reference numerals. In the following, only differences will be discussed.
  • the locking member 50 'of the clutch assembly 30' has a lug 66 'which has a crowned pressure surface 68' (of course, the circular shape of the lug 66 of the embodiment of Figures 1 to 7 is also “crowned”).
  • a lug 66 ' which has a crowned pressure surface 68' (of course, the circular shape of the lug 66 of the embodiment of Figures 1 to 7 is also “crowned”).
  • the approximately in the axial direction extending sides of the nose 66 ' are referred to as nose flanks 100.
  • the locking member 50 'in the axial region between the lugs 66' and the pivot axis 52 each have two web projections 69, which are aligned obliquely relative to the axial extent A. These web projections 69 each have a wedge surface 70 'on their side facing away from the nose 66' in the axial direction. The lugs 66 'are each between two such web projections 69th
  • the shift sleeve 34 has in the circumferential direction D adjacent to the locking member 50 on radial projections 101 which extend in the radial direction, so that a main body of the locking member 50 is generally received therebetween.
  • the base body 106 is approximately circular, so that it is independent of the respective axial position of the locking member 50 and independently of the respective rotational position of the locking member 50 friction between the circumferentially opposite radial projections 101 in the axial direction movable.
  • the circular base body 106 forms in this embodiment, a hub portion for the pivot axis 52, which is not supported on the guide sleeve but on the shift sleeve 34 in the circumferential direction, in contrast to the embodiment of FIGS. 1-7
  • the radial projections 101 have on their axially opposite sides of the wedge surfaces 72.
  • the mutually associated wedge surfaces 70a ', 72a', which are associated with the one clutch with the nose 66a ', are arranged on the same side of the pivot axis 52 as the nose 66a', in contrast to the previous embodiment.
  • the four web projections 69 of the locking member 50 ' are dimensioned in the circumferential direction D so that the radial projections 101 can be pushed past it, when the locking member 50 * is in the neutral position shown in Fig. 8
  • a state of the clutch assembly 30 ' is shown, in which the Vorsynchronweg 80' is bridged (similar to the representation of FIG. 3 of the first Auserhrungsfo ⁇ n).
  • an angle ⁇ is also shown, indicating the angle of the nose flanks 100 with respect to the axial direction.
  • a state of the clutch assembly 30 ' is shown, which corresponds to the illustration of FIG. 4. Due to the friction torque 92 'beats the synchronizer ring 44 and takes the locking member 50' with it, so that this is rotated, by the angle of rotation 94th
  • the locking member 50' can be turned back again, as shown in FIG. 12 (at 99 ').
  • the radial projections 101 can then be pushed past the web projections 69 of the locking member 50 'and the switching process goes into the free-flight phase shown in FIG. 12 (which corresponds to the representation of FIG. 6).
  • the clutch assembly 30 'shown in Figures 8 to 12 is “reversible” in contrast to the clutch assembly 30 of Figures 1 to 7. This means that self-locking is easier to avoid, and in Figures 13 and 14 is another alternative embodiment a clutch assembly 30 "according to the invention shown.
  • the clutch assembly 30 “corresponds in structure and operation generally the clutch assembly 30 of Figures 1 to 7. The same elements are therefore designated by like reference numerals In the following, only the differences are explained. While in the clutch assembly 30 of Figures 1 to 7, the pressure surface 68 is disposed at the axially outermost end of the nose 66, the pressure surface 68 "is formed in the clutch assembly 30" regardless of the nose 66 ", preferably at an underside of the locking member 50th ". The pressure surface 68 "acts on a ring portion of the syndirone ring 44, on the underside of the friction surface 46" is formed.
  • the distance between the pivot axis 52 "and the pressure surface 68" can be shortened as shown at 91 "in Fig. 13. This enables the locking member 50" to be made more compact overall. Furthermore, the synchronizer ring 44 can be made simpler in the region of the coupling with the locking member 50 ".
  • FIGS. 15 and 16 an alternative embodiment of a clutch assembly according to the invention is designated generally at 30 '".
  • the clutch assembly 30 '' generally corresponds in structure and operation to the clutch assembly 30 'of Figures 8 through 12. The same elements are therefore designated by the same reference numerals.
  • the locking member 50 '" has, instead of the lugs 66', respective fork portions 66 '" which receive between them a single axial projection 64'"of a synchronizer ring 44 '" for realizing the circumferential direction driving coupling 62'""
  • These fork portions 66 '" are integrated with the web projections 69 of the embodiment of Figures 8-12, so that the locking member has an H-shape in the radial plan view, thus making the shape of the locking member 50 "" less filigree overall Consequently, it can be made high-strength and easy to manufacture with low volume.
  • the crowned sections of the main body 106 are formed, which ensure easy rotatability of the locking member 50 / 'with respect to the sliding sleeve 34'. "Further, on the sides of the H-fo ⁇ n, the wedge surfaces 70 formed, which can form the respective locking wedge surface pairings 96 with the corresponding wedge surfaces 72 of the shift sleeve 34.
  • the invention can be applied to clutch assemblies in which the connection of members (shift sleeve, coupling body, guide sleeve) in the circumferential direction is not done via teeth, but via pins or the like. Furthermore, the invention is also applicable to clutches in which the shift sleeve is not moved axially via a shift fork or the like, but via another actuator, for example. Electromotive or electromagnetic type.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

L'invention concerne un système d'embrayage (30) permettant de solidariser en rotation un arbre (16) et un élément rotatif (22) monté sur ce dernier, lequel système d'embrayage comprend un manchon d'accouplement (34) solidaire en rotation de l'arbre (16), monté de façon à pouvoir se déplacer axialement par rapport à l'arbre (16) et muni d'une première denture (38), un corps d'embrayage (40), solidaire en rotation de l'élément rotatif (22) et muni d'une seconde denture (42) mise en prise avec la première denture (38) pour solidariser en rotation l'arbre (16) et l'élément rotatif (22), ainsi qu'un dispositif de blocage et de synchronisation (49), présentant une bague de synchronisation (44) pourvue d'une surface de friction (46), bague au moyen de laquelle les vitesses de rotation de l'arbre (16) et de l'élément rotatif (22) peuvent être synchronisées, avant que les première et seconde dentures (38, 42) soient mises en prise, ledit dispositif de blocage et de synchronisation (49) présentant un élément de blocage (50) monté de façon à pouvoir se déplacer par rapport au manchon d'accouplement (34) entre une position neutre (N) et une position de blocage (S), lequel élément de blocage est accouplé à la bague de synchronisation (44) dans le sens périphérique (D) et présente une surface cunéiforme (70), qui forme, en position de blocage (S), avec une surface cunéiforme (72) du manchon d'accouplement (34) une paire de surfaces cunéiformes (96), pour bloquer un déplacement axial du manchon d'accouplement (34). Selon l'invention, l'élément de blocage (50) est monté de façon à pouvoir pivoter autour d'un axe de pivotement (52), s'étendant dans le sens radial, entre la position neutre (N) et la position de blocage (S).
PCT/EP2008/002243 2007-05-09 2008-03-20 Système d'embrayage WO2008138422A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022544.1 2007-05-09
DE200710022544 DE102007022544B4 (de) 2007-05-09 2007-05-09 Schaltkupplungsanordnung

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Publication Number Publication Date
WO2008138422A1 true WO2008138422A1 (fr) 2008-11-20

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010016715A1 (de) 2009-06-05 2010-12-09 Miba Sinter Austria Gmbh Getriebe-Synchronisationsvorrichtung
EP2829761A3 (fr) * 2013-07-24 2016-03-16 Kyowa Metal Works Co., Ltd Dispositif de décalage avec synchroniseur

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008049347B4 (de) * 2008-09-29 2011-01-27 Hofer Forschungs- Und Entwicklungs Gmbh Doppelkupplungsgetriebe
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