CN104373591A - Dog clutch for vehicle transmission - Google Patents

Dog clutch for vehicle transmission Download PDF

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Publication number
CN104373591A
CN104373591A CN201410395257.1A CN201410395257A CN104373591A CN 104373591 A CN104373591 A CN 104373591A CN 201410395257 A CN201410395257 A CN 201410395257A CN 104373591 A CN104373591 A CN 104373591A
Authority
CN
China
Prior art keywords
tooth
wheel hub
cone
shifting element
hub
Prior art date
Legal status (The legal status 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 status listed.)
Pending
Application number
CN201410395257.1A
Other languages
Chinese (zh)
Inventor
尤尔根·宾德尔
安德列亚斯·登普夫勒
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hoerbiger Antriebstechnik Holding GmbH
Original Assignee
Hoerbiger Antriebstechnik Holding GmbH
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 Antriebstechnik Holding GmbH filed Critical Hoerbiger Antriebstechnik Holding GmbH
Publication of CN104373591A publication Critical patent/CN104373591A/en
Pending legal-status Critical Current

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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
    • 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
    • F16D2023/0631—Sliding sleeves; Details thereof
    • 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
    • F16D2023/0637—Details relating to the hub member on which the sliding is arranged
    • 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
    • F16D2023/0656—Details of the tooth structure; Arrangements of teeth
    • 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
    • F16H—GEARING
    • F16H63/00—Control outputs from the control unit to change-speed- or reversing-gearings for conveying rotary motion or to other devices than the final output mechanism
    • F16H63/02—Final output mechanisms therefor; Actuating means for the final output mechanisms
    • F16H63/30—Constructional features of the final output mechanisms
    • F16H2063/3093—Final output elements, i.e. the final elements to establish gear ratio, e.g. dog clutches or other means establishing coupling to shaft

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Mechanical Operated Clutches (AREA)
  • Arrangement And Mounting Of Devices That Control Transmission Of Motive Force (AREA)

Abstract

The invention relates to a dog clutch (16) for a vehicle transmission (10). The dog clutch comprises at least one coupling body (18) fixed to a gear wheel (14) of the vehicle transmission (10) and on one of a transmission axis (A) rotatable transmission shaft ( 12) mounted rotatably and axially non-displaceable substantially, a hub (20) on the around the transmission axis (A) rotatable transmission shaft (12) rotationally fixed substantially, and is axially displaceably mounted, and an axially displaceable switching element (22) in the axial direction (24) is connected to the hub (20) and clamped axially and in the circumferential direction (26) with the hub (20) forms a frictional connection, wherein the switching element (22) and the hub (20) relative to the coupling body (18) axially between a neutral position, a synchronization position and a switching position can be adjusted, wherein the coupling body (18) is substantially rotated freely in the neutral position both relative to the switching element (22) and relative to the hub (20), in which synchronization position is positively connected to the switching element (22) in the circumferential direction (26) and coupled via the frictional engagement with the hub (20), and in the switching position, both the switching element (22) and with the hub (20) in the circumferential direction (26 ) is positively connected.

Description

Embedding tooth for automotive transmission engages
Technical field
The present invention relates to a kind of embedding tooth for automotive transmission and engage (Klauennschaltung).
Background technique
The embedding tooth generally becoming known for automotive transmission in the prior art engages, and it is characterized in that its structure simply and thus low-cost building mode.But especially when treating the high speed discrepancy of coupling access component and/or high moment of inertia, embedding tooth joint has low shifting comfort and noise high undesirably generates and part-load.
Summary of the invention
The object of the invention is to, provide a kind of embedding tooth for automotive transmission to engage, it can make the low noise when high shifting comfort and low operation of abrasively shifting gears.
According to the present invention, this object realizes by engaging for the embedding tooth of automotive transmission, it has: at least one shaft joint body, and it is fixed on the follower of automotive transmission, and rotationally and substantial axial be not bearing in movably can around transmission axis rotate transmission shaft on, wheel hub, its substantially torsionally and be axially movably bearing in can around transmission axis rotate transmission shaft on, and the shifting element moved axially, it is connected with wheel hub and axial nervous (verspant) in the axial direction, and form frictional connection with wheel hub in tangential direction, wherein, shifting element and hub relative axially can in neutral positions in shaft joint body, regulate between sync bit and drive range, wherein, shaft joint body not only can substantially freely have been rotated relative to shifting element but also relative to wheel hub on neutral position, on sync bit with shifting element in tangential direction shape be connected ordinatedly, and coupled by frictional connection and wheel hub, and on drive range not only with shifting element but also with wheel hub in tangential direction shape be connected ordinatedly.By which, transmission shaft can in tangential direction first shape be connected with shifting element ordinatedly, shifting element has little moment of inertia.On the contrary, after the part between transmission shaft and follower or basic synchronization completely, just realize transmission shaft and the shape be fixed between the follower in shaft joint body is connected, it has large moment of inertia respectively.This causes the shifting comfort significantly improved, and the reduction noise that engages of embedding tooth and the operation of wearing and tearing.
At this, shifting comfort close to (interlocking-) shifting comfort with step gear shifting, wherein, the embedding tooth with friction vibration damping engages and structurally more easily builds, need little axial arrangement space, and produce little drag torque, produce extra high efficiency thus.
In the mode of execution that embedding tooth engages, provide tension part, it axially acts on shifting element and wheel hub relative to one another.Screw or rivet are such as applicable to as tension part, be used in especially to take turns with anxiety or compression spring connection in.Compared to (such as according to Bouguer Warner (Borg-Warner)) tradition (interlocking) same to step gear shifting, less for the necessary gear shifting force of shifting vehicle gearbox, because due to the prestressing force applied by tension part, and simultaneous force need not be applied between shifting element and wheel hub.
Preferably, shaft joint body has axially outstanding tooth, and shifting element has mark of mouth groove, or vice versa, and wherein, tooth is engaged in mark of mouth groove, is connected with the shape formed between shaft joint body and shifting element.Axially outstanding tooth and corresponding groove are molded on shaft joint body or shifting element by low manufacturing technology cost, and are connected for solid and reliable shape.
In addition preferably, wheel hub has axially outstanding tooth, and shaft joint body has mark of mouth groove, or vice versa, and wherein, tooth is engaged in mark of mouth groove, is connected with the shape formed between shaft joint body and wheel hub.Again effectively, axially outstanding tooth and corresponding groove are molded in wheel hub or shaft joint body by low construction cost, and formed in addition solid and reliably shape be connected.Especially, the size of tooth and mark of mouth groove is determined in tangential direction mutually, and wheel hub is torsionally connected by means of shape is connected substantially with shaft joint body.
Tooth and/or mark of mouth groove can be provided with the coating for impact damping.Especially, tooth and/or the live part of mark of mouth groove in tangential direction as stop surface coated, thus, in embedding tooth engages and runs, produce low part-load and noise.Alternative, in coating stop surface, also on purpose can change surface characteristic or the surface elasticity of tooth and/or mark of mouth groove, thus realize impact damping.
Particularly advantageously, wheel hub is built into two-part, and wherein, first wheel part and the second hub portion are axially mutually nervous, and are supported on respectively on shifting element.
In the mode of execution that embedding tooth engages, shifting element is annular, level conveyor dish, and it has rubbing surface at least one axial end.Such conveyer dish is such as fabricated stamping part in blocks, and the qurer manufacture by low manufacturing technology cost.
In this embodiment, preferably, conveyer dish is axially arranged between two hub portions, and respectively there is rubbing surface on the axial end of its opposition, wherein, each hub portion comprises wheel hub rubbing surface, and its plane earth is close on the contiguous rubbing surface of conveyer dish.By which, apply and arrange desired friction torque simply by the frictional connection between shifting element and wheel hub, such as, by means of the prestressing force of tension part.
Optionally, shifting element or hub portion are coated with wearing piece facings, and wherein, two hub portions are supported on shifting element respectively by wearing piece facings.Wearing piece facings is conducive to frictional connection on working life of engaging at embedding tooth between shifting element and wheel hub friction torque constant as far as possible.In addition, when relatively low axial prestress, usually by wearing piece facings, the desired friction torque of frictional connection is realized.
In another mode of execution that embedding tooth engages, shifting element is the gearshift cone of annular, and its radially inner side attenuates from axial edge to axial centre cone-shape, and builds two cone faces, and wherein, gearshift cone has rubbing surface at least one cone face.The prestressing force such as applied by tension part is strengthened by tilt angle.Thus, realize higher friction torque when lower-prestressed on the one hand, and on the other hand, realize the low degree impact of elastic force when the non-constant camber of spring curve of tension part.The tension part with little elastic force has the camber of spring curve of plane usually, and in working zone, have the little difference between maximum and minimum elastic force thus.
In this embodiment, gearshift cone can surround two hub portions, and has rubbing surface respectively on its cone face, and wherein, each hub portion has wheel hub rubbing surface on radial outside, and its plane earth is close on the contiguous rubbing surface of gearshift cone.
In preferably one special modification, gearshift cone is built into two-part, wherein, first annular cone element and the second axially contiguous annular cone element alternately have axial protuberance and recess respectively in tangential direction on the end face that it is mutually opposing, wherein, protuberance and the recess of two cone element engage each other, and cone element couples in tangential direction.
In this mode of execution modification that embedding tooth engages, preferably, see in tangential direction, protuberance is connected by the flank of tooth with recess, and wherein, at least some of the flank of tooth forms power and strengthens face, and be inclined to, also mutually move in the axial direction when two cone element are relatively rotated in tangential direction.Described power strengthens on sync bit that face engages at embedding tooth due to the axial introversion of cone element and causes frictional force to strengthen, and therefore causes the impacting force between friction cone (Reibkonen) to improve by the extra anxiety of tension part.Thus, on neutral position, obviously can reduce the axial prestress between shifting element and wheel hub.By the friction torque improved because power strengthens effect, the speed discrepancy between wheel hub and shaft joint body reduces first fast.Then, as long as shifting element and wheel hub are not adjusted to drive range, then power enhancing effect is reduced by axial shifting power, and the speed discrepancy of the reservation between wheel hub and shaft joint body more slowly reduces thus.Finally, this makes can shape to be connected between wheel hub and shaft joint body, and therefore makes the gearshift of jaw clutch more reliable.
In addition, see in tangential direction, protuberance is connected by the flank of tooth with recess, and wherein, at least some of the flank of tooth forms stop surface, and restriction cone element relatively rotates.Also the axial introversion of cone element be can be limited by this stop surface, the axial pressing force between shifting element and wheel hub or friction torque again limited thus.This protection rubbing surface can not transship.In addition, friction torque is determined in each power train by little cost thus, thus avoids less desirable vibration in power train, and this vibration is such as caused by too high friction torque.
Accompanying drawing explanation
In hereinafter with reference accompanying drawing description related to the preferred embodiment, provide other features and advantages of the present invention.In accompanying drawing:
Fig. 1 illustrates the sectional arrangement drawing by automotive transmission local (Ausschnitt), has and engages according to the embedding tooth according to the present invention of the first mode of execution on neutral position, sync bit and drive range;
Fig. 2 illustrates the perspective exploded view of automotive transmission local, and the embedding tooth had second embodiment of the invention engages;
Fig. 3 illustrates the sectional arrangement drawing by the automotive transmission local according to Fig. 2;
Fig. 4 illustrates another sectional arrangement drawing by the automotive transmission local according to Fig. 2;
What Fig. 5 illustrated that the embedding tooth according to Fig. 2 engages can the perspective exploded view of friction element of pre-installation;
Fig. 6 illustrates the sectional arrangement drawing by the friction element according to Fig. 5;
Fig. 7 illustrates the gearshift unit perspective exploded view of the embedding tooth joint for the 3rd mode of execution according to the present invention;
Fig. 8 illustrates the perspective view of the shifting element according to Fig. 7; And
Fig. 9 illustrates the side view of the shifting element according to Fig. 8.
Embodiment
Fig. 1 to Fig. 9 relates to automotive transmission 10, particularly double clutch gearbox or automatic transmission, have: the transmission shaft 12 that can rotate around transmission axis A, two can on transmission shaft 12 rotationally and (except by conditions of manufacture restriction and for follower Safety function desired by bearing play outer) follower 14 that axially do not support movably, and embedding tooth joint 16.At this, the follower 14 of automotive transmission 10 engages 16 respectively shaft joint body 18 with embedding tooth is fixedly connected with, and builds all-in-one-piece or welding especially.According to Fig. 2 to Fig. 4, engage 16 on (left side) side of less follower 14 at embedding tooth, provide clutch driven plate 19 that belong to shaft joint body 18, that separate, it utilizes follower 14 to be pressed into regularly.
Embedding tooth for automotive transmission 10 engages 16 and comprises: two shaft joint body 18, and it is separately fixed on one of the follower 14 of automotive transmission 10, and thus rotationally and be not axially bearing in movably on transmission shaft 12; Wheel hub 20, it is substantially torsionally and be axially movably bearing on transmission shaft 12; And the shifting element 22 moved axially, it is substantially fixedly connected with hub 20 and axial anxiety on axial direction 24, and builds frictional connection with wheel hub 20 in tangent direction 26.Shifting element 22 and wheel hub 20 axially at neutral position (the left figure of Fig. 1), can regulate between sync bit (middle graph of Fig. 1) and drive range (the right figure of Fig. 1) relative to shaft joint body 18.At this, shaft joint body 18 is on neutral position, not only substantially free to rotate relative to wheel hub 20 relative to shifting element 22, on sync bit, in tangent direction 26, shape is connected ordinatedly with shifting element 22, and coupled by frictional connection and wheel hub 20, and be not only connected ordinatedly with shifting element 22 but also with wheel hub 20 shape in tangent direction 26 on drive range.
The wheel hub 20 of embedding tooth joint 16 is built into manifold, particularly two-part in an illustrated embodiment, wherein, and first wheel part 28 and the second prestressing force F of hub portion 30 by arranging vaxially mutually nervous, and be supported on (especially see Fig. 1, Fig. 4 and Fig. 6) on shifting element 22 respectively.
For tension wheel hub 20, provide tension part 32, it axially acts on shifting element 22 and hub portion 28,30 relative to one another.Suitable tension part 32 is such as screw, particularly stretching screw 34, as shown in Figure 1, or rivet 36, there is nervous wheel or compression spring 38 especially, as shown in Fig. 2, Fig. 4, Fig. 5 and Fig. 6.By tension part 32, axial prestress F is set v, it axially reciprocally acts on two hub portions 28,30 towards with shifting element 22 ground dorsad.
As shown in the details local in Fig. 1 and Fig. 5, shifting element 22 and hub portion 28,30 can be coated with wearing piece facings 39, and wherein, two hub portions 28,30 are supported on shifting element 22 respectively by wearing piece facings 39.At this, wearing piece facings 39 for shifting element 22 and wheel hub 20 or hub portion 28, between 30 arrange and engage 16 at embedding tooth working life in constant as far as possible friction torque.
Fig. 1 illustrates three schematic longitudinal sectional by automotive transmission 10 local on neutral position, on sync bit and on drive range, has and engages 16 according to the embedding tooth of the first mode of execution.
Engage in first mode of execution of 16 at embedding tooth, each shaft joint body 18 has axially outstanding tooth 40, and shifting element 22 has mark of mouth groove 42, wherein, tooth 40 was not only engaged in mark of mouth groove 42 on the sync bit that embedding tooth engages 16 on drive range, thus shape connects shaft joint body 18 and shifting element 22 ordinatedly.
In addition, wheel hub 20, particularly each hub portion 28,30 have axially outstanding tooth 44, and each shaft joint body 18 has mark of mouth groove 46, wherein, tooth 44 engages on the drive range of 16 at embedding tooth and is engaged in mark of mouth groove 46, thus shape connects shaft joint body 18 and wheel hub 20 or the hub portion belonging to it 28,30 ordinatedly.At this, preferably, the size of tooth 44 and mark of mouth groove 46 is determined mutually in tangent direction 26, wheel hub 20 and shaft joint body 18 is connected by shape on drive range (the right figure of Fig. 1) and is substantially torsionally connected.
According to Fig. 1, the shifting element 22 that embedding tooth engages 16 have annular, level conveyor dish, it has rubbing surface 50 at least one axial end 48.Have in embodiment shown in two-part wheel hub 20, conveyer dish is axially arranged in two hub portions 28, between 30, and on the axial end 48 of its opposition, there is rubbing surface 50 respectively, wherein, each hub portion 28,30 comprises wheel hub rubbing surface 52, and its plane earth is close to the contiguous rubbing surface 50 of conveyer dish.
Fig. 2 to Fig. 6 illustrates that the embedding tooth for automotive transmission 10 engages 16 second mode of executions, and it is implemented as double clutch gearbox or automatic transmission especially.
According to Fig. 2 to Fig. 6, the shifting element 22 of embedding tooth joint 16 is gearshift cones of annular, and its radially inner side is that cone-shape attenuates from axial edge to axial median surface E, and builds two cone faces 54, wherein, cone of shifting gears has rubbing surface 50 at least one cone face 54.Have in embodiment shown in two-part wheel hub 20, gearshift cone surrounds two hub portions 28,30, and on two cone faces 54, there is rubbing surface 50 respectively, wherein, each hub portion 28,30 has cone hub rubbing surface 52 on its radial outside, and its plane earth is close to the contiguous rubbing surface 50 of gearshift cone.Be different from the wheel hub rubbing surface 52 of the side according to Fig. 1, plane, the wheel hub rubbing surface 52 engaged at embedding tooth in second mode of execution of 16 is built into the side of the truncated cone, wherein, the tilt angle of wheel hub rubbing surface 52 and the tilt angle in cone face 54 are mated mutually, special or even identical.
Completely as according in first mode of execution of Fig. 1, wheel hub 20 or each hub portion 28,30 have axially outstanding tooth 44, and shaft joint body 18 has mark of mouth groove 46, wherein, tooth 44 engages on the drive range of 16 at embedding tooth and is engaged in mark of mouth groove 46, thus shape connects shaft joint body 18 and wheel hub 20 or the hub portion belonging to it 228,30 ordinatedly.Again less preferably, tooth 44 and mark of mouth groove 46 are implemented on precise match ground as far as possible, wheel hub 20 and shaft joint body 18 are connected by shape on drive range and are substantially torsionally interconnected.
First mode of execution of 16 is engaged on the contrary with according to the embedding tooth of Fig. 1, according in second mode of execution of Fig. 2 to Fig. 6, shifting element 22 has axially outstanding tooth 56, and each shaft joint body 18 has mark of mouth groove 58, wherein, tooth 56 was not only engaged in mark of mouth groove 58 on the sync bit that embedding tooth engages 16 on drive range, thus shape connects shaft joint body 18 and shifting element 22 ordinatedly.At this, this structural difference between two mode of executions is substantially owing to the reason of manufacturing technology.
Fig. 5 and Fig. 6 illustrates perspective exploded view, and by engage according to the embedding tooth of the second mode of execution 16 can the sectional arrangement drawing of friction element 76 of pre-installation.
At this especially, seeing well according in the section of Fig. 6, the tooth 56 of shifting element 22 is axially given prominence to further relative to axial median surface E, as the tooth 44 of wheel hub 20 or hub portion 28,30.
Engage the hereafter functional description of 16 or automotive transmission 10 according to embedding tooth, the meaning of tooth 56,44 outstanding in various degree becomes clear.
If particularly as automatic transmission automotive transmission 10 should by gearshift in another gear time, then the shifting element 22 engaging 16 at embedding tooth applies axial shifting power F s(the left figure see Fig. 1 and Fig. 3).Correspondingly, shifting element 22 moves towards follower 14 to be shifted gears on axial direction 24.At this, by tooth 40,56 and mark of mouth groove 42,58 shape be formed between shaft joint body 18 and shifting element 22 be connected.In other words, this represents, shifting element 22 and wheel hub 20 axially move to sync bit (middle graph of Fig. 1) from neutral position (the left figure of Fig. 1) relative to shaft joint body 18, on neutral position, shaft joint body 18 is not only substantially free to rotate relative to wheel hub 20 relative to shifting element 22, on sync bit, shaft joint body 18 and shifting element 22 shape in tangent direction 25 is connected ordinatedly, and is coupled by frictional connection and wheel hub 20.
Because for the tooth 40 that shape between shifting element 22 and shaft joint body 18 is connected, 56 is axially outstanding further, as the tooth 44 be connected for shape between wheel hub 20 and shaft joint body 18, although occurred on sync bit that the shape between shaft joint body 18 and shifting element 22 is connected, but between shaft joint body 18 and wheel hub 20, also do not occur that shape is connected.
Be connected by the shape between shaft joint body 18 and shifting element 22, due to the speed discrepancy between wheel hub 20 and follower 14, produce between shifting element 22 and wheel hub 20 and relatively rotate.Due to axial tightening (prestressing force F v) and the rubbing surface 50,52 be mutually close to, under this in relative rotation situation, occur friction torque, it compensates the rotating speed of transmission shaft 12 and follower 14 mutually.As long as speed discrepancy is lower than boundary value and/or fill up predetermined lock in time, then gear shifting force F sagain be applied to (middle graph see Fig. 1) on shifting element 22, shifting element 22 and wheel hub 20 are axially moved, further until occur that shape is connected between shaft joint body 18 and wheel hub 20 on the direction to follower 14 to be shifted gears thus.In other words, shifting element 22 and wheel hub 20 are adjusted to drive range (the right figure of Fig. 1) from sync bit (middle graph of Fig. 1) on axial direction 24, on sync bit, shaft joint body 18 and shifting element 22 shape in tangent direction 26 is connected ordinatedly, and coupled by frictional connection and wheel hub 20, on drive range, shaft joint body 18 had not only been connected ordinatedly with shifting element 22 but also with wheel hub 20 shape in tangent direction 26.Thus, desired gear is shifted gears.
Thus by shaft joint body 18, first follower 14 is connected with shifting element 22, and it has little moment of inertia.After part or basic synchronization completely, realize being connected with the shape of transmission shaft 12 by wheel hub 20, it has relatively large moment of inertia.Engage relative to traditional embedding tooth, produce low material requirements, and the shifting comfort significantly improved in less desirable noise and vibration.
Synchronous relative to interlocking well known in the prior art, such as, according to Bouguer Warner, the low and axial consolidation more of structure complexity.In addition, synchronous relative to interlocking, axial shifting power F sdiminish, because simultaneous force need not be applied again due to pre-nervous rubbing surface.
At this, waiting time on sync bit and such as can cross wearing piece facings 39 and/or prestressing force F between shifting element 22 and wheel hub 20 vthe wiping moment of torsion arranged must be determined mutually, makes, when shifting element 22 and wheel hub 20 are adjusted to drive range from sync bit, to have little speed discrepancy, thus reliably guarantees the conversion entering drive range.As long as the engagement immediately that the tooth 44 of wheel hub 20 enters in the mark of mouth groove 46 of shaft joint body 18 is impossible, then tooth 44 slides along it in shaft joint body 18 due to the speed discrepancy retained, until it arrives mark of mouth groove 46, and due to gear shifting force F sand be axially engaged to wherein.
For the situation of carrying out complete rotating speed unification, before tooth 44 is engaged in mark of mouth groove 46, driving torque is imported in embedding tooth joint 16 by the cut-off clutch of automotive transmission 10.This moment affects necessarily relatively rotating between wheel hub 20 and shaft joint body 18, and tooth 44 is reliably engaged in mark of mouth groove 46, and guarantees that entering drive range reliably shifts gears.
As shown in fig. 5 and fig., tooth 40,44,56 and/or mark of mouth groove 42,46,58 be provided with coating 60 for impact damping, wherein, coating 60 is provided in tangent direction 26 especially as on the face of stop surface.Alternative, in coating 60, also can propose the change of surface characteristic or surface elasticity in this region.
Fig. 7 to Fig. 9 illustrates the view for engaging the shifting element 22 of 16 according to the embedding tooth of the 3rd mode of execution.
3rd mode of execution of embedding tooth joint 16 is only different from the second mode of execution in following, that is, replaced by cone of shifting gears according to two-part of Fig. 7 to Fig. 9 according to the single-piece shifting element 22 of Fig. 2 to Fig. 6.
At this, in the general structure engaging 16 at embedding tooth and working principle, reference pin to the foregoing description of other mode of executions, and hereinafter only relative to the second mode of execution description scheme and difference functionally.
According to Fig. 7 to Fig. 9, gearshift cone is built into two-part, wherein, first annular cone element 62 alternately has axial protuberance 66 and recess 68 respectively with the second axially contiguous annular cone element 64 on the end face that it is mutually relative in tangent direction 26, wherein, the protuberance 66 of two cone element 62,64 and recess 68 engage each other, and cone element 62,64 mutually couples in tangent direction 26.
In tangent direction 26, protuberance 66 is connected by the flank of tooth with recess 68, wherein, the at least some of the flank of tooth forms power and strengthens face 70 and tilt, make two cone element 62,64 in situation in relative rotation in tangent direction 26 adjacent near-earth slide together, it is also mutually being moved on axial direction 24.At this, power strengthens face 70 in a plane, and it extends in radial directions and with tending to axial direction.
In addition, at least some of the flank of tooth forms stop surface 72, and limits relatively rotating of cone element 62,64 thus.At this, stop surface 72 is in a plane, and it had not only extended in radial directions but also in the axial direction.
If gear should be inserted for the automotive transmission 10 had according to the embedding tooth joint 16 of the 3rd mode of execution, be then similar to two aforesaid mode of executions, axial shifting power F sbeing applied to embedding tooth engages on the shifting element 22 of 16, such as, by means of the reverse shift fork according to Fig. 9.Shifting element 22 and wheel hub 20 are moved into sync bit from neutral position thus.
On sync bit, cone element 62, the tooth 56 of 64 is engaged in the mark of mouth groove 58 of affiliated shaft joint body 18, makes this cone element 62,64 turn to relative to other cone element 64,62 stopper formed by stop surface 72.Alternative or extra in stop surface 72, for limiting cone element 62, this stopper in relative rotation between 64 also realizes by the axial dimension of the exact matching of reverse shift fork 74.
By cone element 62,64 relatively rotate, cone element 62,64 strengthen face 70 axially by introversion by power, rubbing surface 50 thus, and the axial force on 52 improves, and the friction torque thus between shifting element 22 and wheel hub 20 improves.Strengthen by power the speed discrepancy that this friction torque that effect improves is used for reducing fast between wheel hub 20 and shaft joint body 18, wherein, power strengthens rotating speed unification that effect increases together and reduces.
As long as speed discrepancy lower than boundary value and or cover predetermined lock in time, then two-part shifting element 22 and two-part wheel hub 20 axially move to follower 14 to be shifted gears further.If the tooth 44 of wheel hub 20 encounters the mark of mouth groove 46 of the vicinity of shaft joint body 18, then shifting element 22 and wheel hub 20 can axially be adjusted on its drive range.Therefore, desired gear is shifted gears.
If the tooth 44 of wheel hub 20 encounters the mark of mouth groove 46 of shaft joint body 18, then cone element 62,64 again reverse and are axially moved to together, that is, axially mutually move.Friction torque is reduced to minimum value thus.Due to little friction torque, the speed discrepancy between wheel hub 20 and shaft joint body 18 is than more slowly reducing in full friction torque situation.This slower synchronization is guaranteed at the end of shift process, and each tooth 44 of wheel hub 20 slides together at least for a long time in shaft joint body 18, until it arrives mark of mouth groove 46, and is engaged to wherein.Therefore, desired gear is shifted gears.
The advantage engaged at embedding tooth in the 3rd mode of execution situation of 16 is, friction torque can be affected in an advantageous manner by axial prestress, otherwise friction torque engages the prestressing force F by being applied on neutral position in other mode of executions of 16 at embedding tooth vand scheduled, and substantially keep constant.By the friction torque reduced at the end of shift process, embedding tooth engages 16 and can be transformed on drive range especially simply and reliably.
Certainly, for the shortcoming significantly improving manufacture cost of two-part shifting element 22, corresponding embedding tooth engages this advantage of the 3rd mode of execution of 16.

Claims (14)

1. one kind engages for the embedding tooth of automotive transmission (10), has:
At least one shaft joint body (18), it is fixed on the follower (14) of automotive transmission (10), and rotationally and be not axially bearing on the transmission shaft (12) that can rotate around transmission axis (A) movably;
Wheel hub (20), it is substantially torsionally and substantial axial is bearing on the transmission shaft (12) that can rotate around transmission axis (A) movably; And
The shifting element (22) moved axially, it to be connected with wheel hub (20) and axial anxiety axial direction (24) is upper, and to go up and wheel hub (20) forms frictional connection in tangent direction (26),
Wherein, shifting element (22) and wheel hub (20) axially can in neutral position, regulate between sync bit and drive range relative to shaft joint body (18),
Wherein, shaft joint body (18) not only can substantially freely have been rotated relative to shifting element (22) but also relative to wheel hub (20) on neutral position, and be connected ordinatedly the upper shape of tangent direction (26) with shifting element (22) on sync bit, and coupled by frictional connection and wheel hub (20), and be not only connected ordinatedly with shifting element (22) but also with wheel hub (20) the upper shape of tangent direction (26) on drive range.
2. embedding tooth according to claim 1 engages, and it is characterized in that, provides tension part (32), and it axially acts on shifting element (22) and wheel hub (20) relative to one another.
3. engage according to embedding tooth in any one of the preceding claims wherein, it is characterized in that, shaft joint body (18) has axially outstanding tooth (40) and shifting element (22) has mark of mouth groove (42), or vice versa, wherein, tooth (40) is engaged in mark of mouth groove (42), and the shape formed between shaft joint body (18) and shifting element (22) is connected.
4. engage according to embedding tooth in any one of the preceding claims wherein, it is characterized in that, wheel hub (20) has axially outstanding tooth (44) and shaft joint body (18) has mark of mouth groove (46), or vice versa, wherein, tooth (44) is engaged in mark of mouth groove (46), and the shape formed between shaft joint body (18) and wheel hub (20) is connected.
5. the embedding tooth according to claim 3 or 4 engages, and it is characterized in that, tooth (40,44,56) and/or mark of mouth groove (42,46,58) are provided with the coating (60) for impact damping.
6. engage according to embedding tooth in any one of the preceding claims wherein, it is characterized in that, wheel hub (20) is built into two-part, wherein, first wheel part (28) and the second hub portion (30) are axially mutually nervous, and are supported on respectively on shifting element (22).
7. engage according to embedding tooth in any one of the preceding claims wherein, it is characterized in that, shifting element (22) is annular, level conveyor dish, and it has rubbing surface (50) at least one axial end (48).
8. the embedding tooth according to claim 6 and 7 engages, it is characterized in that, conveyer dish is axially disposed in two hub portions (28,30) between, and on the axial end (48) of its opposition, there is rubbing surface (50) respectively, and wherein, each hub portion (28,30) comprise wheel hub rubbing surface (52), its plane earth is close on the contiguous rubbing surface (50) of conveyer dish.
9. the embedding tooth according to claim 6 or 8 engages, it is characterized in that, shifting element (22) or hub portion (28,30) wearing piece facings (39) is coated with, wherein, two hub portions (28,30) are supported on shifting element (22) respectively by wearing piece facings (39).
10. embedding tooth according to any one of claim 1 to 6 engages, it is characterized in that, shifting element (22) is the gearshift cone of annular, its radially inner side attenuates from axial edge to axial centre cone-shape, and build two cone faces (54), wherein, cone of shifting gears has rubbing surface (50) at least one cone face (54).
11. embedding teeth according to claim 6 and 10 engage, it is characterized in that, gearshift cone surrounds two hub portions (28,30), and on its cone face (54), there is rubbing surface (50) respectively, and wherein, each hub portion (28,30) on radial outside, have wheel hub rubbing surface (52), its plane earth is close on the contiguous rubbing surface (50) of gearshift cone.
12. embedding teeth according to claim 10 or 11 engage, it is characterized in that, gearshift cone is built into two-part ground, wherein, first annular cone element (62) and the second axially contiguous annular cone element (64) alternately have axial protuberance (66) and recess (68) respectively on the end face that it is mutually opposing in tangent direction (26), wherein, two cone element (62,64) protuberance (66) and recess (68) engage each other, and cone element (62,64) couples in tangent direction (26).
13. embedding teeth according to claim 12 engage, it is characterized in that, in tangent direction (26), protuberance (66) is connected by the flank of tooth with recess (68), wherein, at least some of the flank of tooth forms power and strengthens face (70), and is inclined to, also in the upper motion mutually of axial direction (24) when making two cone element (62,64) relatively rotate in tangent direction (26).
14. embedding teeth as requested described in 12 or 13 engage, it is characterized in that, in tangent direction (26), protuberance (66) is connected by the flank of tooth with recess (68), wherein, the at least some of the flank of tooth forms stop surface (72), and restriction cone element (62,64) relatively rotates.
CN201410395257.1A 2013-08-12 2014-08-12 Dog clutch for vehicle transmission Pending CN104373591A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013108736.1 2013-08-12
DE102013108736.1A DE102013108736A1 (en) 2013-08-12 2013-08-12 Claw connection for a vehicle transmission

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CN104373591A true CN104373591A (en) 2015-02-25

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CN201410395257.1A Pending CN104373591A (en) 2013-08-12 2014-08-12 Dog clutch for vehicle transmission

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DE (1) DE102013108736A1 (en)
FR (1) FR3009598A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016203707B4 (en) * 2016-03-08 2017-12-21 Magna powertrain gmbh & co kg Actuator arrangement for a drive train of a motor vehicle
DE102017216322A1 (en) 2017-09-14 2019-03-14 Zf Friedrichshafen Ag Switching device for a transmission
EP3457001B1 (en) * 2017-09-14 2020-12-09 ZF Friedrichshafen AG Switching device for gearbox

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE647456C (en) * 1933-02-09 1937-07-05 Daimler Benz Akt Ges Claw coupling
GB654701A (en) * 1947-05-31 1951-06-27 Ganz And Company Ltd Synchronising claw coupling device
DE925927C (en) * 1953-03-22 1955-03-31 Egon Dr-Ing Martyrer Synchronous switching device for gear change transmission with dog gear
DE1030692B (en) * 1955-03-17 1958-05-22 Egon Martyrer Dr Ing Synchronization device for heavy, high performance gear change transmissions, especially for road and rail vehicles
DE19903115C2 (en) * 1999-01-27 2003-09-04 Getrag Getriebe Zahnrad Transmission for a motor vehicle

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CB03 Change of inventor or designer information

Inventor after: Binder Juergen

Inventor after: JUERGEN BINDER

Inventor after: Andreas Och

Inventor after: Wolfgang Volker

Inventor before: Binder Juergen

Inventor before: JUERGEN BINDER

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Free format text: CORRECT: INVENTOR; FROM: JUERGEN BINDER ANDREAS DEMPFLE? TO: JUERGEN BINDER ANDREAS DEMPFLE? ANDREAS OCH WOLFGANG VOLCKER

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Application publication date: 20150225

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