• 专利附录
  • 专利说明
  • 权利要求
  • 类似技术
  • 同族专利
  • 引用文献
  • 法律状态
  • 优先权
    • 专利摘要:
    The present invention relates to a synchronizing device for a gearbox. The synchronizing device comprises an annular coupling element (5, 14), a locking cone (6, 9) and a coupling cone (7, 10). The coupling element (5, 14) is slidably arranged in an axial direction between a first end position in which the coupling element (5, 14) is freely rotatable relative to the coupling cone, (7, 10) and a second end position in which the coupling element teeth (Sa, 14a) are in the engagement coupling cone teeth (7a, 10a). The synchronizing device comprises a gap-shaped space between a radially outer guide surface (Se, 14c) of the coupling element (5, 14) and a radially inner guide surface (6c, 9c) of the locking cone (6,9), and a locking element (8, 11) which is arranged in said space. Said guide surfaces (60,9e) are designed so that the locking element (S, 11) establishes a connection between the coupling element (S, 14) and the locking cone (6, 9) in a connecting position which is located at a distance from the first end position so that the coupling element (5 , 14) during a continued movement towards the first end position, moves the locking cone (6, 9) to a position in which the conically shaped friction surface (6a, 9a) of the locking cone is located at a distance from the conically shaped friction surface of the disengagement cone (Ya, 10a). (sig. see)
    公开号:SE1351046A1
    申请号:SE1351046
    申请日:2013-09-11
    公开日:2015-03-12
    发明作者:Jonas Lundin
    申请人:Scania Cv Ab；
    IPC主号:
    专利说明:

    10152D253035relatively small, which results in the conical friction surface of the track cone often becominglocated at a very small distance from the friction surface of the clutch cone when the ring gear is inthis state of mind. In this end position, the conical friction surfaces rotate relative toeach other. This creates a braking moment in the oil-filled space betweenfriction surfaces of the locking cone and the coupling cone. The magnitude of this slowing momentdepends on several factors such as the viscosity of the gearbox oil, the temperature of the oil, the distancebetween the conical surfaces and the relative velocity between the conical surfaces. Thisburning moment of the rotational movement of the shaft can be described as a towing loss asleads to a reduced efficiency of the gearbox and an increased fuel consumptionof an internal combustion engine connected to the gearbox.
    Synchronization devices are also used to synchronize the speed of gearsand shafts in gearboxes in connection with the loading of gears. A displaceably arrangedcoupling sleeve can in this case be releasably connected to two alternative gearson a shaft in the gearbox. The coupling sleeve is slidably arranged in axial directionsto engage the respective gears with the aid of a ratchet cone having oneconically shaped friction surface and a coupling coira having a correspondingly shapedconical friction surface. Here, too, trailer losses occur when the coupling sleeve is in oneend position in which the locking cone and the coupling cone rotate relative to each other.
    SUMMARY OF THE INVENTIONThe object of the present invention is to provide a synchronizing devicewhich comprises an axially displaceable coupling element, a locking cone with a conicalfriction surface and a coupling lcona with a conical friction surface where the trailer losses in itthe oil-filled space between said friction surfaces can essentially always be kept at a lowlevel when the coupling element has been displaced to an end face in which it is out of engagement withclutch cone.
    This object is achieved with the synchronizing device of the initially mentionedwhich is characterized by the features set forth in the characterizing part of claim 1part. The locking element thus establishes a connection between the coupling element andthe ratchet cone in a connecting position which the coupling element passes before it reachesthe end position in which the coupling element is out of engagement with the coupling cone. Thusthe locking cone will be displaced a distance from the coupling cone which correspondsthe distance that the switching element is moved between the connection position and the end position.101520253035With a suitable dimensioning of the constituent components canthe coupling element now. the connecting position at a relatively large distance from the end edge.
    Thus, the locking cone can be displaced a relatively long distance from the coupling cone so thatthe oil-filled space between the conical friction surface of the locking cone and the coupling coneconical friction surface becomes relatively large. Thus, relatively small trailer losses are obtained, whichresults in the gearbox being able to obtain a high efficiency and an internal combustion enginewhich is connected to the gearbox a reduced fuel consumption.
    According to an embodiment of the present invention, the locking member is substantiallyring-shaped and mounted in a prestressed condition in said space so that it strivesafter expanding radially outwards or radially inwards. A locking element that strives toexpand radially outward obtains a radial position defined by the radialexternal guide surface. As a rule, the radially outer guide surface is defined bythe clutch owner. Alternatively, a locking element can be used which strives tocompressed radially inwards. The annular locking member may comprise an elongate memberbody having a substantially circular curvature between two free ends. One suchlocking elements can be easily applied in a prestressed state in said radial space.
    The locking element may consist of a metal material with suitable resilient properties.
    According to an embodiment of the present invention, the coupling element comprisesguide surface a first stop surface which restricts the movement of the locking element in an axial direction andthat the guide surface of the locking cone comprises a first stop surface which delimits the locking elementmovement in an opposite axial direction and that said connection is established bysaid stop surfaces receive contact with opposite sides of the locking element inconnection mode. During the displacement pipe travel of the coupling element in one directionin the first end position, the stop surface of the coupling element first comes into contact withthe locking element. The coupling element thus initially carries the locking element with it. Thenthe locking element comes into contact with the stop surface of the locking cone in connection position canthe coupling element bring with it both the locking element and the locking cone fromclutch cone. When the coupling element reaches the first end position comes the locking coneto be at a predetermined axial distance from the coupling cone.
    According to an embodiment of the present invention, the coupling element comprisesguide a second stop surface which restricts the movement of the locking element in an axial direction andthat the guide surface of the locking cone comprises a second stop surface which delimits the locking elementmovement in an opposite axial direction and that said other stop surfaces obtain contact with101520253035opposite sides of the locking element when the coupling element reaches a second breathing position. Thenthe coupling element is rotated in an axial direction towards the second end position of the initial withthe locking element. When the locking element is in contact with the second stop surface of the locking coneit carries with it both the locking element and the locking cone. Spårrkonan's conical friction surfacethen comes into contact with the conical friction surface of the coupling cone. Sincethe clutch cone is not displaceable, it stops the displacement movement of the locking coneand the locking element. The coupling element is essentially stationary while the track cone andthe speed of the coupling cone is synchronized by those in contact with each other conicalthe friction surfaces. When the ratchet cone and clutch cone have reached the same speed,the coupling element is displaced one last distance in which it engagesclutch cone teeth. The movement of the coupling element can be stopped in the second end positionby the coupling element and the coupling cone interfering.
    According to an embodiment of the present invention, the coupling element is arrangedaround a central axis and that the guide surface of the coupling element has a breaking point as yearlocated between said stop surfaces which is located on the smallest radial surface of the guide surfacedistance from the central axis. A locking element that strives to be displaced radiallyoutwards is directed here towards one of the respective stop surfaces depending on which side ofthe breaking point as it is in contact with the contact surface. The part of the guide surface that is locatedbetween the breaking point and the second stop surface, the locking element pushes radially inwards thenthe switching element reaches a dry synchronization mode. In the pre-synchronization mode, one is pressedoil m lm between the conical surfaces away after which the conical surfaces are applied to each other.
    According to an embodiment of the present invention, the locking cone is radially outwarddirected portions a surface which forms the first stop surface of the guide surface of the locking cone. Thushave these radially outwardly directed portions, in addition to the function of creating a torsionally stableconnection between the coupling element and the track cone, also the task of creating onestop surface which guarantees that the groove cone is separated from the coupling cone at times whenthe coupling element is moved towards the first end position.
    According to an embodiment of the present invention, the groove cone has radially outwarddirected portions a surface which forms the second stop surface of the guide surface of the locking cone. Thushave these radially outwardly directed portions, in addition to the function of creating a torsionally stableconnection between the coupling element and the track cone, also the function to definea stop position for the locking element at times when the coupling element is pushed towards the otherend position.'Uh1520253035According to an embodiment of the present invention, the clutch element is a ring gear ina planetary gear which is a gear in the gearbox. A range gear can give eachprimary gear in the gearbox a low and a low gear respectively. The ring wheel is connected toa stationary clutch cone in the low gear position and with a rotating oneclutch cone in the high 'gear position The speed of the ring wheel must thussynchronized before it can be engaged with the respective coupling cones. In itlow gear position, the ring gear is displaced to an axial end position in which it engageswith the stationary clutch cone. In the high gear position, the ring gear is shifted toan opposite end position in which it engages the rotating coupling cone.
    According to an embodiment of the present invention, the coupling element is acoupling sleeve which is arranged around a shaft in the gearbox, the coupling sleeve beingslidably disposed between a second end position in which it engages onegears that define a gear in the gearbox and a first end position in which it canrotate freely relative to the gear. The coupling sleeve is arranged in betweentwo gears so that it can alternatively be connected to one of the gears at the same time asit can rotate freely relative to the other gear.
    BRIEF DESCRIPTION OF THE DRAWINGSIn the following, by way of example, preferred embodiments of the invention are describedwith reference to the accompanying drawings, in which:Pig. 1 shows an exploded view of a range gear comprisingsynchronizing devices according to the present invention,Pig. 2 shows the gear unit in an assembled condition,Figs. 3a-d show one of the synchronizing devices in Fig. 2 when the ring gear is in fourdifferent modes andFig. 4 shows synchronizing devices for connecting gears in a gearbox.
    DETAILED DESCRIPTION OF PREFERRED EMBODIMENTS OFTHE INVENTIONFig. 1 shows an exploded view of the components of a gear unit. Range switches are arranged ingearboxes in vehicles to give each primary gear in the gearbox a high and a low, respectively101520253035exchange. The range gear is connected to a main shaft 1 in the gearbox. The main shaft lcomprises a portion provided with splines 1a. The range includes a sun gear 2with an inner portion provided with splines Za of a corresponding shape asshaft 1. The sun gear 2 is thus rotatably connected to the main shaft 1. The sun wheel 2 rotatesthus with the same speed as the main shaft 1. The sun gear 2 has an outer portion whichis provided with teeth 2b. A planet wheel holder 4 which is provided with a numberplanet gears 3 are arranged radially outside the sun gear 2. Planet gears 3 are designedwith teeth 3a which rotate in engagement with the teeth of the sun gear Zb. Planet wheel holder 4comprises a shaft 1b which constitutes the output shaft of the gearbox. A ring wheel 5 is mountedradially outside the planet gear holder 4. The ring wheel 5 comprises an inner portionwith teeth Sa which is engaged with the teeth of the planet gears 3a. The ring gear 5 includesan outer peripheral recess Sb for receiving an inner member which may bea pressure air controlled control cylinder which displaces the ring wheel 5 in an axial direction.
    The range switch comprises a first locking cone 6 as arranged at a first side ofthe ring gear 5. The first locking cone 6 is formed with a radially inwardly directed conicalshaped friction surface 6a. The first locking cone 6 comprises first radially outwardly projectingportions 6b and other radially outwardly projecting portions 6d which are engaged with the ring gear5 inside ga teeth Sa. The first locking cone 6 is thus rotatably connected tothe ring gear 5 so that they rotate at the same speed. Because the ring gear teeth Sa andthe projecting portions 6b, 6d of the ratchet cone have an axial extension, the ratchet cone 6 candisplaced in an axial direction relative to the ring gear 5. The first ratchet cone 6comprises a radially outer surface 6c having an axial distance between themprotruding portions 6b, 6d. The first locking cone 6 also comprises teeth 6e which areadapted to engage the geared portion Sa of the ring gear 5. A firstcoupling cone 7 is arranged in connection with the first locking cone 6. The firstthe coupling cone 7 is arranged stationary and it can, for example, be attached to onewall elements of the gearbox. The first coupling cone 7 comprises a radially outwarddirected conically shaped friction surface 7a which is adapted to come into contact withconically shaped friction surface 6a of the ratchet cone. The first coupling cone 7 comprisesradially outwardly directed teeth 7b adapted to engage the ring gear 5invändí ga cogs 5a. A first ring-shaped locking element 8 is adapted to be mounted in onegap-shaped space between the ring gear 5 and the first ratchet cone 6. Detannular first locking element 8 does not have a complete circular in front but it isprovided with two free end portions Sa which are arranged at a distance from each other. The101520253035the first locking element 8 can thus be easily compressed and mounted in a prestressed position inwhich it tends to expand in a radially outward direction.
    The gear unit comprises, at an opposite side of the ring gear S, a second ratchet cone 9. Thethe second locking cone 9 is formed with a radially inwardly directed comically shaped friction surface9a. The second locking cone 9 comprises first radially outwardly projecting portions 9b andother radially projecting portions 9d which engage the gears Sa of the ring gear S.
    The second locking cone 9 is thus rotatably connected to the ring housing 5 so that they rotatewith the same speed. Because the ring gear's teeth Sa and the other ratchetprojecting portions 9b, 9d have an axial extension, the second locking cone 9displaced in an axial direction relative to the ring gear S. The second ratchet cone 9comprises a radially outer surface 9c located between the projecting portions9b, 9d. The second locking cone 9 also comprises teeth 9e which are adapted to go inengagement with the geared portion Sa of the ring gear 5. A second coupling cone 10 isarranged connection to the second locking cone 9. The second coupling cone 10comprises a radially outwardly directed conically shaped friction surface 10a adapted tocome into contact with the comically shaped friction surface 9a of the second ratchet cone 9. Thethe second coupling cone 10 comprises radially outwardly directed teeth 10b which are adaptedto engage the ring gear teeth Sa. The second coupling cone 10 comprises oneradially inner portion provided with splines l0c so that the coupling cone is torsionally stableconnected to the portion of the main shaft comprising splines 1a. The other onethe clutch 10 thus rotates at the same speed as the main shaft 1. The otherthe coupling cone 10 is mounted on the shaft 1 in a non-displaceable condition. A secondring-shaped locking element 1 1 is arranged a slit-shaped space between the ring wheel S andthe second locking cone 9. The second annular locking element ll does not have a fi independentcircular shape but it comprises two free end portions 11a arranged on onedistance from each other. The second locking element 11 can thus be easily compressed andmounted in a biased position in which it tends to expand in a radially outward direction.
    A central shaft 12 extends through the main shaft 1.
    Pig. 2 shows the gear unit components in a mounted position. To provide oneshifting the gearshift, the ring gear S is displaced by an actuator (not shown) in an axial positiondirection between two end positions. The ring gear S is shown here in an end position in which it is inengagement with the first clutch cone 7. The movement of the main shaft is transmitted in this case,via the sun gear 2, the planet gears 3 and the planet holder 4, to the output shaft 1b of the gearbox.
    The speed of the main shaft 1 is in this case transmitted to the output shaft 1b by one101520253035downshift. Range gear in this case provides a low gear ratio. Then the ring gear 5displaced in an opposite axial direction to an opposite spirit position, the ring gear lugs are connected5a with the teeth of the second coupling cone lÛb. The movement of the main shaft 1 is transmitted in thiscase, via the second clutch cone 10, the ring gear 5, the planet gears 3 and the planet holder 4,to the output shaft lb of the gearbox. The entire planetary gear including the ring gear 5 rotates hairas a unit so that the speed of the main shaft 1 is transmitted unchanged to the output shaftlb. The range gear in this case provides a high gear ratio.
    The primary gears in a gearbox can thus provide a low gear ratio or ahigh gear ratio. Using a range gear provides a gearboxtwice as many gears. Since the ring gear 5 in the low gear position is connected tothe first clutch cone 7 which is stationary and in the high gear position is connectedwith the second clutch cone 10 rotating at the speed of the main shaft 1, one mustrnoment interruptions are made during a gear process in the range gear to synchronizethe speed of the ring gear 5 with the speed of the respective clutch cones 7, 11]. A firstsynchronizing device is used to synchronize the speed of the ring gear 5 with itthe first coupling cone 7 and a second synchronizing device are used tosynchronize the speed of the ring gear 5 with the second clutch cone 10.
    Figs. Fig-d show one right side of the ring wheel 5 in four different axial positions during onedisplacement movement between the two spirit flames. This right side of the ring gear 5includes the first synchronizing device. The firstthe synchronizing device comprises the ring gear 5, the first track cone 6, the firstthe coupling cone 7 and the first locking element S. The first locking element 8 is arranged ina slit-shaped space defined by an inner radial guide surface 5e ofthe coupling sleeve 5 and an outer radial guide surface 6c of the first groove cone 6.the first locking element 8 is mounted in a biased state in said space so that itstrives to expand radially outwards. The ring surface 5c of the ring wheel has a distance betweena first stop surface See; which defines a spirit position of the locking element 8 relative tothe ring gear 5 and a second stop surface 502 defining a second breathing position forthe locking element 8 in relation to the ring wheel 5. The ring surface So of the ring wheel has an inclination sothat the radial distance to the central axis 12 decreases from the first stop surface5c1 to a breakpoint 5c3. In the same way, it reduces the steering distance's See distance fromthe second stop surface See; to the breaking point 503. The ring surface 50 of the ring wheel is connected tothe second stop surface 52 located at a greater radial distance from the central axis 12101520253035than control surface See adjacent to the first stop surface Ser. The first locking cone 6 has oneguide surface 60 with a first stop surface 601 defining a first end positionfor the reading element 8 in relation to the locking cone 6 and a second stop surface 602 whichdefines a second end position of the locking element 8 in relation to the latch cone 6.
    Pig. 3a shows the ring wheel 5 in an end position in which the teeth Sa of the ring wheel engage withthe teeth of the first clutch cone 7b. Since the first coupling cone 7 isstationary, the ring gear 5 is stationary. The movement of the main shaft 1 is transmitted in this case, viathe sun gear 2, the planet gears 3 and the planet holder 4, to the output shaft 1b of the gearbox.
    The speed of the main shaft 1 is transmitted here, via the gear shift, to the output shaft 1b witha downshift. The first locking element 8 is arranged between the first stop surface of the ring wheelSee 1 and the locking cone's first stop surface 601.
    At times when the range is to be shifted to the end position with a high gearthe actuator (not shown) is activated which provides a displacement movement ofring wheel 5 in an axial direction to the left. Because the first locking element 8 strivesafter expanding radially outwards, it is in continuous contact with the ring wheel's steering surface Se.
    Since the guide surface Sc has a slope in the contact area with the locking element 8 pullsthe guide surface Initially carry the locking element 8 with you until the locking cone 6 is stopped offplanet gears 3. When the ratchet cone 6 is stopped, it can resist so that the firstthe reading element 8 is pushed radially inwards by the guide surface 5e. The first reading element 8 can thuspass the local minimum point Seg; at the guide surface 5c. After the firstthe locking element 8 passed the minirni point Se; it can again expand radially outwards incontact with the guide surface See until it comes into contact with the second stop surface 502 of the guide surfacewhich is shown in Fig. 3b. During the continued displacement movement of the ring wheel 5 for itwith it the first locking element 8 via the second stop surface Seg. This movement continuesuntil the locking element 8 comes into contact with the second stop surface 6c2 of the first locking cone,which is shown in Fig. 3e. Second stop surface of the coupling element See; limits the firstthe movement of the locking element 8 in an axial direction and the second stop surface of the first locking cone602 restricts the movement of the reading element 8 in an opposite axial direction. The ring wheel 5 now hasa connection position with the locking cone 6.
    During a final part of the displacement movement of the ring wheel 5, the first entrainsthe locking element 8 and the first locking cone 6 by means of the second stop surfaces 502, 6c2.
    Thus, the reading element 8 and the first locking cone 6 are displaced as a unitthe ring gear 5. The displacement movement ceases when the ring wheel 5 reaches the end position shown in Figs.101520253035103d. The ring gear 5 can now rotate freely relative to the first clutch cone 7.
    The ring gear teeth 5a on the opposite left part not shown have now been connected tothe second coupling cone 9 teeth 9b. The ring gear 5 and the second ratchet cone 9rotates therein at the same speed as the second clutch cone 10. The main shaft l.motion is transmitted in this case, via the second clutch cone 10, the ring gear 5, the planet gears3 and the planet carrier 4, to the output shaft 1b. The range provides in thiscase a high gear ratio.
    In that the first locking cone 6 is carried by the ring wheel 5 during the closingthe part of the displacement movement to the end position, in which the ring gear can rotate freely inrelative to the coupling cone 7, the first locking cone 6 assumes a position of onedistance from the first coupling cone 7. Since the first locking cone 6 rotateswith the speed of the ring wheel, it performs a rotational movement relative to the stationary onethe first clutch cone 7 in the disengaged position. This inevitably creates onebraking torque in the oil-filled space between the conical of the first ratchet conefriction surface 6a and the conical friction surface 7a of the first clutch cable. The size ofthis moment is related to the distance between the conical surfaces 6a, Ta. It depends, thoughon several factors such as the viscosity of the gearbox oil, the temperature of the oil, and the relativethe velocity between the conical surfaces. In this case, however, one is guaranteed to be createdsufficient distance between the conical friction surfaces 6a, 7a so that the brakingthe torque becomes relatively small. Thus, only small trailer losses are obtained in the gearbox, whichresults in a reduced fuel consumption of an internal combustion engine that isconnected to the gearbox.
    At times when the ring gear 5 is displaced to the end position with a high gear ratio is providedcorresponding relative movements of the second locking cone 9, the second coupling conelÛ and the second locking element ll as in the first locking cone 6, the firstthe coupling line 7 and the first locking element 8 when the ring gear 5 is displaced to the end positionwith the low gear. The second synchronizing device comprises onegap-shaped space between a guide surface 5c of the ring wheel 5 and a guide surface 9c of itthe second locking cone 9. The second locking element 11 is arranged in said slot-shapedspace. The second locking element 11 is inonterati a biased state in saidspace where it strives to expand radially outwards. During the last part ofthe displacement movement to the end position of the ring wheel 5 carries with it the second locking element 11and the second ratchet cone 9. Thus, the second ratchet cone 9 is displaced in one. axialdirection from the second coupling cone 10. l and with it a distance is guaranteed to be created10152025303511between the conical friction surface 9a of the second locking cone and the second coupling coneconical friction surface l0a when the ring gear 5 reaches the end position. The second clutch conecomic friction surface l.0a thus rotates guaranteed on a relatively large predetermineddistance from the stationary conical friction surface 9a of the second locking cone. Even in thiscase, it becomes the burning moment in the oil-filled space between comicthe friction surfaces 9a, l0a relatively small.
    When the ring gear 5 has been displaced in an axial direction to one of the two end positions, it moves inengagement with a coupling cone at the same time as it can rotate freely relative to itsecond clutch cone. The movement of the ring gear 5 from the end position as it can rotate freely inrelation to the first coupling cone to the end position in which it engagesthe first coupling cone 7 is made in the following manner. The displacement movement starts withthe ring gear 5 in the position shown in Fig. 3d. When the actuator displaces the ring sleeve 5 in oneaxial direction to the right of the ring sleeve 5 with the first locking element 8 via itthe inclined portion of the guide surface Sc extending between the second stop surface 502 and thelocal rninirnipunkten 5c3. This movement continues until the first reading element 8 arrivesin contact with the first stop surface of the first locking cone 6ci_ In the continued movement ofthe ring wheel 5 carries with it both the first reading element 8 and the first ratchet cone 6until the conically shaped friction surface 6a of the ratchet cone comes into contact with the firstcoupling cone 7 conically shaped friction surface 7a. This position is shown in Fig. 3b and canreferred to as a synchronization mode. In this position, oil that is located is pressedbetween the comic surfaces away. In the case of the continued displacement movement of the ring gear 5tends the inclined guide surface 5c between the second stop surface Se; and the localthe minimum point 503 to push the locking element radially inwards. The actuator displaces the ring gear5 with a force so that the reading element 8 is pushed radially inwards until it passes the local oneminimipunlrten Seg. The movement of the ring wheel 5 ceases when it reaches a stop surface adjacent to itclutch cone teeth 7b. The locking element 8 simultaneously receives contact with the firstthe stop surface Sci as shown in Fig. 3a. During this movement, the first locking cone is pressedconically shaped friction surface 6a against the conically shaped coupling cone of the first coupling conefriction surface 7a. The speed of the ring gear 5 is thus quickly slowed down until it is obtainedthe same speed as the first clutch cone 7, which in this case is zero because itthe first coupling cone 7 is a stationary component. The 5 speed of the ring sleeve is now zeroand it can thus be displaced a final distance up to the end position in which the ring sleeveteeth Sa engages the coupling cone teeth 7b.10152025303512Pig. 4 shows a main shaft 1 in a gearbox. The main shaft 1 comprises a portion withsplines la. A motion transmitting component in the form of a guide sleeve 13 is providedaround the shaft 1. The guide sleeve 13 comprises an inner portion with corresponding shapessplines 13a so that the guide sleeve 13 is rotatably mounted on the shaft 1. The guide sleeve 13 rotatesdänned with the same speed as the shaft 1. The guide sleeve 13 comprises radially outwardly directedteeth 13b which in engagement with internal teeth 14a of a ring foirnatcoupling element in front of a coupling sleeve 14. The coupling sleeve 14 comprises aradial recess l4b which is in contact with an offset actuator (not shown)the coupling sleeve 14 in an axial direction between two end layers. Then the coupling sleeve 14displaced to an end position, the teeth 14a of the coupling sleeve are connected to teeth 7b of afirst clutch cone. The first coupling cone 7 comprises internal teeth 7cto which it is connected to teeth 15a of a first gear 15. The firstthe clutch tone 7 and the first gear 15 thus rotate at the same speedshaft 1 via a needle bearing 17a. The coupling sleeve is 14 years old here in an end position in which it isengagement with the first clutch cone 7. The shaft 1 in this case obtains a movement whichtransmitted from a gear on a side shaft (not shown) to the gear 15 via the firstthe coupling cone 7, the coupling sleeve 14 and the guide sleeve 13. The shaft 1 obtains a speeddefined by the number of teeth of the first gear 15 and the gear onsicloaxeln.
    When the coupling sleeve 14 is displaced in an axial direction to an opposite end positionthe teeth 144 of the coupling sleeve engage the tooth elements of the other coupling cone10b. The second clutch cone 10b includes internal teeth 10c with which it isconnected to teeth 16a of a second gear 16. The second clutch cone 10and the first gear 15 thereby rotates at the same speed about the axis 1 via oneneedle bearing 17b. The coupling sleeve is 14 years old here in a state of mind in which it is engagedthe second clutch cone 10. The shaft 1 in this case receives a movement which is transmitted from onegear on a side shaft (not shown) of the gear 16 via the second clutch cone 7,the coupling sleeve 14 and the guide sleeve 13. The shaft 1 obtains a speed defined bythe number of teeth of the second gear 15 and the gear on the side axle.
    A first synchronizing device is used to synchronize the coupling sleeve 14speed with the first clutch cone 7 and a second synchronizing deviceis used to synchronize the speed of the coupling sleeve 14 with the otherthe coupling cone 10. The coupling sleeve 14 comprises guide surfaces 14c which cooperate withguide surfaces oc, 9c of the respective ratchet economy 6, 9 so that gap-shaped spaces are formed101513in which a respective locking element 8, 11 is arranged. Synchronization devicesfunction and design correspond to the function of the synchronizing devices in the one abovedescribed first execution form. We therefore do not make any further review ofthe function of the synchronizing devices. However, it can be stated that the locking element 8,ll in the same way as in the first form of drying establish a connection betweenthe coupling sleeve 14 and the respective locking cones 6, 9 when the coupling sleeve 14 is in aconnection position located at a distance from an end position in which the coupling sleevecan rotate freely relative to one of the coupling cones 7, 10. The coupling loop 14 forthen carry the respective locking cones 6, 9 from the connecting position to that end positionso that the conical friction surfaces 6a, 9a of the locking cones 6, 9 are also in this case actively moved to aposition at a distance from the conical of the respective coupling cones 7, 10friction surfaces 7a, i0a.
    The thawing is in no way limited to the embodiments shown in the drawingsbut can be varied freely within the scope of the claims.
    权利要求:
    Claims (10)
    [1]
    A gearbox synchronizing device, the synchronizing device comprising - an annular coupling element (S, 14) comprising radially inwardly directed teeth (Sa, 14a) having an axial extension, - a locking cone (6, 9) comprising radially outwardly directed portions (6b, d, 9b, d) having an axial stretch which are intended to engage with the teeth (5a, 14a) of the coupling element and a conically shaped friction surface (6a, 9a), and - a coupling cone (7, 10) which comprises a conically shaped friction surface (7a, 10a) which is adapted to come into contact with the conically shaped friction surface (6a, 9a) of the locking cone and radially outwardly directed teeth (7b, 10b), the coupling element (5, 14) being slidably arranged in a axial direction between a first end position in which the coupling element (S, 14) is freely rotatable relative to the coupling cone (7, 10) and a second end position in which the toothed element (Sa, 14a) of the coupling sleeve engages the coupling cone bushes (719, 10b), know The synchronizing device comprises - a gap-shaped space between a radially outer guide surface (Se, 14c) of the coupling element (5, 14) and a radially inner guide surface (6c, 9c) of the locking cone (6, 9) and - a locking element (8, 11) arranged in said space, said guide surfaces (Se, 6c, 9c, 100) being designed so that the locking element (8, 11) establishes a connection between the coupling element (5, 14) and the locking cone (6, 9) in a connecting position which is located at a distance from the first end position so that the coupling element (5, 14) during a continued movement towards the first end position carries the locking cone (6, 9) to a position in which the conically forged friction surface (6a, 9a) of the locking cone is located at a distance from the conically shaped friction surface (7a, 10a) of the coupling cone.
    [2]
    Synchronizing device according to claim 1, characterized in that the locking element (S, 11) is substantially annular and mounted in a prestressed condition in said space so that it strives to expand radially outwards.
    [3]
    Synchronizing device according to claim 2, characterized in that the annular locking element (8, 11) comprises an elongate body having a substantially circular curvature between two free ends (Sa, 11a). 10 15 20 25 30 35 15
    [4]
    Synchronizing device according to one of the preceding claims, characterized in that the guide surface (Se, 14e) of the coupling element comprises a first stop surface (Sei) which limits the movement of the locking element (8, 11) in an axial direction and that the guide surface (6e, 9e) of the locking cone comprises a first stop surface (6c1) which restricts the movement of the locking element (8, 1 1) in an opposite axial direction and that said connection is established by said stop surfaces (Se1, 6e1) obtaining contact with opposite sides of the locking element (8, 11) in the connecting position.
    [5]
    Synchronizing device according to claim 4, characterized in that the guide surface (Se, 14e) of the coupling element comprises a second stop surface (Seg) which restricts the movement of the locking element (8, 11) in an axial direction and that the guide surface (6e, 90) of the locking cone comprises a second stop surface. (6e2) which restricts the movement of the locking element (S, 11) in an opposite axial direction and that said second stop surfaces (Seg, 602) obtain contact with inserted sides of the locking element (8, 11) when the coupling element (5, 14) reaches the second end position.
    [6]
    Synchronizing device according to any one of the preceding claims, characterized in that the coupling element (S, 14) is arranged around a central axis (12) and that the guide surface (Se, 140) of the coupling element has a breaking point (Seg) located between said stop surfaces (Ser , Seg) which is arranged at the smallest radial distance of the guide surface (Se, 14e) from the central axis (12).
    [7]
    Synchronizing device according to one of Claims 4 to 6, characterized in that the radially outwardly directed portions (6d, 9d) of the ratchet cone have a surface which forms the first stop surface (6e1) of the guide surface (6e, 90) of the ratchet cone.
    [8]
    Synchronizing device according to one of Claims 5 to 7, characterized in that the radially outwardly directed portions (6b, 9b) of the ratchet cone have a surface forming the second stop surface (602) of the guide surface (6e, 9e) of the ratchet cone.
    [9]
    Synchronizing device according to one of the preceding claims, characterized in that the clutch element is a ring gear (S) in a planetary gear which constitutes a range gear in the gearbox.
    [10]
    Synchronizing device according to any one of the preceding claims, characterized in that the coupling element is a coupling sleeve (14) arranged around an axis (1) in the 16 gearbox, the coupling sleeve (14) being displaceably arranged between an end position in which it engages a gear (15, 16) in which they gear a gear in the gearbox and an opposite end position in which it can rotate freely relative to the gear (15, 16).
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    同族专利:
    公开号 | 公开日
    WO2015038053A1|2015-03-19|
    SE537524C2|2015-06-02|
    引用文献:
    公开号 | 申请日 | 公开日 | 申请人 | 专利标题
    JP3161244B2|1994-08-26|2001-04-25|トヨタ自動車株式会社|Transmission synchronization device|
    SE514231C2|2000-01-28|2001-01-29|Scania Cv Ab|Synchronization device at a planetary gear|
    JP2005133840A|2003-10-30|2005-05-26|Aisin Ai Co Ltd|Synchro device of manual transmission|
    JP2007292151A|2006-04-24|2007-11-08|Honda Motor Co Ltd|Transmission synchronous mesh mechanism|
    JP5020903B2|2008-07-30|2012-09-05|アイシン・エーアイ株式会社|Power transmission device|SE539358C2|2015-11-19|2017-08-01|Scania Cv Ab|A latch cone ring for a synchronizing arrangement, a synchronizing arrangement, a gearbox and a vehicle|
    法律状态:
    2017-05-02| NUG| Patent has lapsed|
    优先权:
    申请号 | 申请日 | 专利标题
    SE1351046A|SE537524C2|2013-09-11|2013-09-11|Synchronization device in a gearbox|SE1351046A| SE537524C2|2013-09-11|2013-09-11|Synchronization device in a gearbox|
    PCT/SE2014/051039| WO2015038053A1|2013-09-11|2014-09-10|Synchromesh unit in a gearbox|
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